View source for RS-12-154, Attachment D to Proto-Power Calculation 97-195, Revision a

{{Adams
| number = ML12269A020
| issue date = 09/17/2012
| title = Attachment D to Proto-Power Calculation 97-195, Revision a
| author name = 
| author affiliation = Exelon Generation Co, LLC
| addressee name = 
| addressee affiliation = NRC/NRR
| docket = 05000373, 05000374
| license number = 
| contact person = 
| case reference number = RS-12-154
| document report number = 97-195, Rev. A
| document type = - No Document Type Applies
| page count = 687
}}

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{{#Wiki_filter:Attachment D to Proto-Power Calculation 97-195 Revision A Proto-Power Caic: 97-195 

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D Revy A Page 1 of 5 LSCS-UFSAR 9.2 WATER SYSTEMS The auxiliary water systems for the LaSalle County Station are as follows: a. CSCS equioment cooling water system, b. station service water system, c. reactor building closed cooling water system, d. demineralized water makeup system, e. potable and sanitary water system, f. ultimate heat sink, g. cycled condensate system and refueling water storage facilities, h. turbine building closed cooling water system (TBCCWS), i. primary containment chilled water system, j. station heat recovery system, k. suppression pool cleanup system, and 1. chemical feed system.9.2.1 CSCS Eauinment Coolina Water  The function of the core standby cooling system-equipment cooling water system (CSCS-ECWS) is to circulate lake water from the ultimate heat sink for cooling of the residual heat removal (RHR) heat exchangers, diesel-generator coolers, CSCS cubicle area cooling coils, RHR pump seal coolers, and low-pressure core spray (LPCS) pump motor cooling coils. This system also provides a source of emergency makeup water for fuel pool cooling and also provides containment flooding water for post-accident recovery.
This CSCS-ECWS system is equivalent in purpose to the essential service water cooling systems at other stations.9.2.1.1 Design Bases 9.2.1.1.1 Safety Design Bases a. The system is sized based on the followinw minimum eciinment cooling water flow requirements:
: 1. RHR heat exchanger 
-7400 gpm 2. diesel-generator cooler (division 1 and 2 only) -800 3. diesel-generator cooler (division 
: 3) -650 gpm gpm Proto-Power Calc: 97-195 

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D Rev: A Page 2 of 5 REV. 12 -MARCH 1998 9.2-1 LSCS-UFSAR 9.5.4.5 Instrumentation and Controls Fuel levels in each day tank and storage tank are indicated locally, and storage tank levels are also indicated at each storage tank filling station. `Ton-roI alarms annunciate high or low levels in each day tank and low level in each storage tank. All day tank level instruments and diesel-generator transfer pump controls are Seismic Category I and Class 1E. A local pressure indicator is connected to the discharge of each transfer pump to monitor pump discharge head.. A local differential pressure indicator is connected across the transfer pump suction strainer to identify a clogged strainer.Each diesel engine gauge panel includes local gauges for monitoring the following diesel-generator skid-mounted system fuel oil parameters:
fuel oil temperature, fuel pump suction strainer inlet and outlet pressure (Divisions I and 2 diesel generators only), fuel pump discharge pressure, fuel filter inlet pressure, and fuel filter outlet pressures (for the Division 3 diesel generators, filter inlet and outlet pressure gauges are mounted on the engine and not on the gauge panel). In addition, pressure switches are installed in the skid-mounted systems to annunciate high fuel filter differential pressure for the Divisions 1 and 2 diesel generators and low fuel pump discharge pressure for the Division 3 diesel generators.
The entire skid-mounted fuel oil system, including instrumentation, is supplied by the engine manufacturer as a part of the diesel engine.Each diesel-generator fuel transfer pump is started and stopped automatically by day tank level control switches.
The diesel fire pump fuel transfer pump is started manually; however, it is automatically shut down by day tank high level. -Elapsed time instrumentation monitors diesel-generator transfer pump running time and, when the diesel engine is operating, pump shutdown time. This instrumentation actuates control room alarm lights if pump running time is excessive or shutdown time is too short to permit remote detection of possible fuel oil leaks at the day tank or diesel generator.
9.5.5 Diesel-Generator Cooling Water System The function of the diesel-generator cooling water system is to transfer the heat rejected from the engine water jacket, the lube oil cooler and the engine air aftercooler to the CSCS equipment cooling water system (CSCS-ECWS).
9.5.5.1 Design Bases n 9.5.5.1.1 Safety Design Bases 0 0 Cooling capacity of this system is based on a diesel-generator output of 2860 kW with an environmental temperature of 1220 F to maximum and a minimum and maximum lake water temperature of 320 F C and 1000 F, respectively.
Total heat transfer by this system is 9.5-34 REV. 0 -APRIL 1984 0 4 LSCS-UFSAR approximately 7.8 x 106 Btu/hr per diesel-generator set at rated engine capacity.
The diesel cooling water heat exchangers are sized based on operation of 110'% of rated load.8High water temperaLure is alarmed at 2000 F and the engine is automatically shut down if the cooling water temperature at the engine outlet exceeds 2080 F in order to prevent engine damage due to overheating.
This shutdown control is in effect only when the engine is started manually and bypassed when the diesel generator is started automatically during an emergency.
Heaters are installed in the cooling water piping below the lube oil cooler to maintain the engine water and lube oil in a warm standby condition while the engine is not operating; thus increasing the starting reliability of the diesel generator.
Natural convection is employed to circulate the warm engine water through the lube oil cooler during standby.Each system is designed based on Seismic Category I requirements and is protected from tornadoes, missiles, and flooding.9.5.5.1.2 Power Generation Desian Bases The diesel-generator cooling water system is not required during power generation.
Consequently, it possesses no power generation design bases.9.5.5.2 System Description Each diesel-generator cooling water system is a separate, independent closed loop system supplied with the diesel generator and located entirely on the diesel-generator skid. It consists of two parallel engine driven centrifugal circulating pumps, a low-pressure expansion tank, an AMOT temperature regulating valve, a lube oil cooler, and the engine cooling water heat exchanger.
The expansion tank is fitted with a 7 psig relief cap which also will relieve vacuum. Engine coolant is demineralized water treated with chromate, borate-nitrite, or silicate-nitrite type corrosion inhibitors in accordance with the engine manufacturer's recommendations.
During operation, cooling water at a flow of 1100 gpm per diesel-generator set is circulated by the engine driven pumps through the diesel engine cooling water passages to the lube oil cooler, through the temperature regulating valve, and then to the engine cooling water heat exchanger.
See Figure 9.5-5 for additional details.'In 'r 0%The engine cooling water heat exchanger is a two-pass shell and o tube type heat exchanger having admiralty tubes with a carbon steel water box and shell. Engine cooling water is circulated through the shell side while strained lake water is pumped U a through the tube side by the CSCS-ECWS (Subsection 9.2.1). CO Design pressure and temperature is 150 psig and 3000 F for both ou 9.5-35 REV. 0 -APRIL 1984 '0, P. -
LSCS-FSAR AMENDMENT 29 JANUARY 1978 QUESTION 040.92"In response to Question 040.16 you have provided in section 9.5.5.1.1 a total diesel generator cooling water heat rate of approximately 6.15 million Btu/hr.This heat is rejected in the heat exchanger interfacing with CSCS equipment cooling W.&#xfd;ater system when the diesel generator is operating at rated capacity.
Also, in section 9.5.5.2 you mention *that the cooling waterflbw rate in the diesel engine is 1,100 gpm. It is not clear whether these heat and flow rates are for the total five diesel generators or for a single diesel generator.
Please provide the heat and flow rates for each of the five diesel generators.
In addition, also provide the design temperature differential((OF) for each diesel engine cooling water when operating at rated capacity." RESPONSE The design conditions for each diesel-generator cooling water system are: Shell side flow 1100 gpm Design shell side inlet temperature 1900 F Shell side outlet temperature 1750 F Tube side design flow 800 gpm.Tube side inlet temperature 1000 F Tube side outlet temperature 1220 F Heat exchanger design heat removal 8.6 x 106 btu/hr Diesel-generator set 6 cooling requirement 7.8 x 10 btu/hr (The value of 6.15 x 106 btu/hr heat removal specified in Subsegtion 9.5.5.1.1 has been corrected to read 7.8 x 10 btu/hr in accordance with the above data).Proto-Power Ca~c: 97-195 Q4 0.92-1 

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D Rev: A Page 5 of 5 Attachment E to Proto-Power Calculation 97-195 Revision A Proto-Power Caic: 97-195 

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E Rev: A Page 1 of 13 12:19:47 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler Vendor Data Sheet -BENCHMARK Shell and Tube Heat Exchanger Input Parameters 06/29/98 1.FliiidQuantity, Total .-i...gpm Inlet Temperature OF Outlet Temperature OF Fouling Factor Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/hr)Design Heat Trans Coeff (BTU/hr-ft Emprical Factor for Outside h Performance Factor (% Reduction)
Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Number of Shells per Unit Shell Minimum Area Shell Velocity (ft/s)Tube Pitch (in)Tube Pitch Type Shell-Side Tube-Side.... .1J,399.45~ 
............ 
.77576-I-190.00 100.00 ,/ENoot-"AT 174.40 122.20 &Iv6r &5t c5 0.00285 0 .000001 ,oorAL o Fresh Water (1 , Fresh Water f " .8,600,000 , .F) 255.20 , o 0.780339000-5 0.00",.,T .TEMA-E I/ A Emc.pv:e)CoJDtIof' S. 0.998169790 1 0.490000000 5.000 0.7500 Triangular Number of Tube Passes 2 U-Tubes No Total Number of Tubes 188 Number of Active Tubes 188 Tube Length (ft) 13.00 Tube Inside Diameter (in) 0.652 Tube Outside Diameter (in) 0.750 Tube Wall Conductivity (BTU/hr-ft&deg;F) 112.00 Ds, Shell Inside Diameter (in) 0.000 Lbc, Central Baffle Spacing (in) 0.000 Lbi, Inlet Baffle Spacing (in) 0.000 Lbo, Outlet Baffle Spacing (in) 0.000 Doti, Tube circle diameter (in) 0.000 Bh, Baffle cut height (in) 0.000 Lsb, Diametral difference between Baffle and Shell (in) 0.000 Ltb, Diametral difference between Tube and Baffle (in) 0.000 Nss, Number Sealing Strips 0.000 Proto-Power Calc: 97-195 

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E Rev: A Page 2 of 13 12:19:47 PROTO-HX 3.02 by Proto-Powver Corporation (SN#PIHX-0000)
Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler Vendor Data Sheet -BENCHMARK 06/29/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Extrapolation Data Data Date Tube Flow (gpm) 775.6 Shell Flow (gpm) Shell Flow (gpm) 1,099.5 Shell Temp In (IF) Tube Inlet Temp (IF) 100.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 190.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (&deg;F)Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hrift 2.&deg;F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2 0-F)Tube-Side hi (BTU/hr'ft 2"&deg;F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2 0-F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr'ft 2.&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (&deg;F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (&deg;F)Bulk Visc (Ibm/ft-hr)
Shell Skin Temp (IF)Skin Visc (lbm/ft'hr)
Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (IF)Cp (BTU/Ibn-&deg;F)
Tav Tube (&deg;F)K (BTU/hr-ft--F)
Tube Skin Temp (IF)Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbmlft-hr)
Density (Ibm/ft 1)Cp (BTU/lbm.&deg;F)
K (BTU/hr-ft.&deg;F) 71.1 Overall Fouling (hr'ft 2.&deg;F/BTU)Shell-Side ho (BTU/hr-ft 2.&deg;F)Tube-Side hi (BTU/hr'ft 2.&deg;F)I/Wall Resis (BTU/hr-ft 2.&deg;F)LMTD Correction Factor 0.002850 2,075.6 2,100.5 25,594.8 0.9886 479.0 Shell-Side Tube-Side 5.15 8.00 8.537E+04 6.589E+04 2.13 4.00 0.82 1.47 0.87 1.33 60.53 61.85 1.00 1.00 0.39 0.37 U Overall (BTU/hr-ft 2-OF) 2 Shell Temp In (OF) 1 Shell Temp Out (OF) I Tav Shell (IF) I Shell Skin Temp (OF) 1 Tube Temp In (OF) 1 Tube Temp Out (OF) I Tav Tube (IF) I Tube Skin Temrn(&deg;F) 1$'roto-Power Cale: 97-195 

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E Rev: A Page 3 of 13 55.2 90.0 74.4 82.2 73.5 00.0 22.2 11.1 21.0** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 12:22:07 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DG01A -DG Jacket Water Cooler Vendor Design Condition 
-Adj. Area 06/29/98 Shell and Tube Heat Exchanger Input Parameters II II Shell-Side Tube-Side F 1idQu-anti,,T-ta-gpT 1t,099-l5 
.77576Y Inlet Temperature OF 190.00 100.00 "/ -Outlet Temperature OF 174.40 122.20 ',7, Fouling Factor 0.00285 [.0.00000 tALU5 Shell Fluid Name Fresh Water Tube Fluid Name Fresh Water Design Heat Transfer (BTU/hr) 8,600,000 Design Heat Trans Coeff(BTU/hr-ft 2"&deg;F) 255.20 Emprical Factor for Outside h 0.780339000 Performance Factor (% Reduction) 0.00 , ....'Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Number of Shells per Unit Shell Minimum Area Shell Velocity (fr/s)Tube Pitch (in)Tube Pitch Type TEMA-E 50r"A 47 1.231 0.981978184 1 0.490000000 5.000 0.7500 Triangular Number of Tube Passes 2 U-Tubes No Total Number of Tubes 188 Number of Active Tubes 188 Tube Length (ft) 13.00 Tube Inside Diameter (in) 0.652 Tube Outside Diameter (in) 0.750 Tube Wall Conductivity (BTU/hr-ft-&deg;F) 112.00 Ds, Shell Inside Diameter (in) 0.000 Lbc, Central Baffle Spacing (in) 0.000 Lbi, Inlet Baffle Spacing (in) 0.000 Lbo, Outlet Baffle Spacing (in) 0.000 Doti, Tube circle diameter (in) 0.000 Bh, Baffle cut height (in) 0.000 Lsb, Diametral difference between Baffle and Shell (in) 0.000 Ltb, Diametral difference between Tube and Baffle (in) 0.000 Nss, Number Sealing Strips 0.000 Proto-Power Calc: 97-195 

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E Rev: A Page 4 of 13 12:22:07 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler Vendor Design Condition 
-Adj. Area 06/29/98 Calculation Specifications II It , Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (&deg;F)Shell Inlet Temp (IF)775.6 1,099.5 100.0 190.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2'.F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2.&deg;F)Tube-Side hi (BTU/hr-ft 2.&deg;F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr ft 2-&deg;F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hrft 2--F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (&deg;F)Reynold's Number Shell Temp Out (&deg;F)Prandtl Number Tav Shell (&deg;F)Bulk Visc (Ibm/ft hr) Shell Skin Temp (&deg;F)Skin Visc (lbm/ft-hr)
Tube Temp In (&deg;F)Density (Ibm/ft-)
Tube Temp Out (&deg;F)Cp (BTU/lbm-&deg;F)
Tav Tube (&deg;F)K (BTU/hr'ft'&deg;F)
Tube Skin Temp (&deg;F)Extrapolation Calculation Results Shell Mass Flow.(lbm/hr)
Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (Wt 2)5.5E+5 3.88E+5 8.48 1E+6 71.3 471.2 Property Shell-Side Tube-Side Velocity (ft/s) 5.15 8.00 Reynold's Number 8.543E+04 6.580E+04 Prandtl Number 2.13 4.00 Bulk Visc (lbm/ft-hr) 0.82 1.47 Skin Visc (lbm/ft-hr) 0.87 1.34 Density (Ibm/ft')
60.52 61.85 Cp (BTU/Ibm.&deg;F) 1.00 1.00 K (BTU/hr-ft.&deg;F) 0.39 0.37** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Overall Fouling (hr-ft 2-&deg;F/BTU) 0.Shell-Side ho (BTU/hr.ft--&deg;F)
Tube-Side hi (BTU/hr-ft 2-&deg;F)I/Wall Resis (BTU/hr.ft 2-&deg;F) 2 LMTD Correction Factor U Overall (BTU/hr.ft 2.0 F)Shell Temp In (&deg;F)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (&deg;F)Tav Tube (IF)Tube Skin Tefpo? -wr Calt: 97-195 

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E Rev: A Page 5 of 13)02850 2,076.0 2,099.0 5,594.8 0.9889 255.2 190.0 174.6 182.3 173.5 100.0 121.9 110.9 120.9 12:26:44 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DG01A -DG Jacket Water Cooler Adj. Area -LSCS Ref. Conditions Shell and Tube Heat Exchanger Input Parameters 06/29/98 I I.I Shell-Side F l iii d-Q u--n-i i~y, ToF-.I gpr m Inlet Temperature OF 190.00 Outlet Temperature OF 174.40 Fouling Factor 0.00285 Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/hr)Design Heat Trans Coeff (BTU/hr-ft 2..F)Emprical Factor for Outside h Performance Factor (% Reduction)
Tube-Side 100.00 122.20 0.00000 Fresh Water Fresh Water 8,600,000 255.20 0.780339000 0.00 Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Number of Shells per Unit Shell Minimum Area Shell Velocity (ft/s)Tube Pitch (in)Tube Pitch Type TEMA-E 471.23 0.981978184 1 0.490000000 5.000 0.7500 Triangular Number of Tube Passes U-Tubes Total Number of Tubes Number of Active Tubes Tube Length (ft)Tube Inside Diameter (in)Tube Outside Diameter (in)Tube Wall Conductivity (BTU/hr-ft-PF)
Ds, Shell Inside Diameter (in)Lbc, Central Baffle Spacing (in)Lbi, Inlet Baffle Spacing (in)Lbo, Outlet Baffle Spacing (in)Dotl, Tube circle diameter (in)Bh, Baffle cut height (in)Lsb, Diametral difference between Baffle and Shell (in)Ltb, Diametral difference between Tube and Baffle (in)Nss, Number Sealing Strips 2 No 188 188 13.00 0.652 0.750 112.00 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-195 

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E Rev: A Page 6 of 13 12:26:44 PROTO-HX 3.02 by Proto-Power Corporation (SN#PMX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler Adj. Area -LSCS Ref. Conditions 06/29/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Extrapolation Data Data Date Tube Flow (gpm) 795.3 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In (IF) Tube Inlet Temp (OF) 100.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 190.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.&deg;F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2-&deg;F)Tube-Side hi (BTU/hr-ft 2-&deg;F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2-&deg;F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2.&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (&deg;F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (&deg;F)Bulk Visc (Ibm/ftrhr)
Shell Skin Temp (&deg;F)Skin Visc (Ibm/ft-hr)
Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (&deg;F)Cp (BTU/Ibm-&deg;F)
Tav Tube (&deg;F)K (BTU/hr-ft.&deg;F)
Tube Skin Temp (IF)Extrapolation Calculation Results Shell Mass Flow (Ibm/hi)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ftW)5.325E+5 LES. rHAZ, 3.978E+5 1?6f. (6D .4 1?(&j Il e 0 8.484E+6 WXJQ&#xfd;M 71.3 Property Shell-Side Velocity (ft/s) 4.99 Reynold's Number 8.257E+04 Prandtl Number 2.14 Bulk Visc (lbm/ft-hr) 0.82 Skin Visc (lbm/ft-hr) 0.88 Density (Ibm/ft 3) 60.53 Cp (BTU/Ibm.&deg;F) 1.00 K (BTU/hr-ft.&deg;F) 0.39 Tube-Side 8.20 6.728E+04 4.01 1.47 1.34 61.85 1.00 0.37 Overall Fouling (hr ft 2.&deg;F/BTU) 0.(Shell-Side ho (BTU/hr-ft 2 0.F) 2 Tube-Side hi (BTU/hr-ft 2-&deg;F)1/Wall Resis (BTU/hrft 2.&deg;F) 25 LMTD Correction Factor U Overall (BTU/hr-ft 2.&deg;F)Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (&deg;F)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (&deg;F)Tube Skin TegCCV)&#xfd;ower Ca0c: 97-195 

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E Rev: A Page 7 of 13)02850 2,034.1 2,138.0 5,594.8 0.9889 255.2 190.0 174.1 182.1 173.1 100.0 121.4 110.7 120.5** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 12:29:43 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIIX-0000)
Commonwealth Edison Calculation Report for DGO I A -DG Jacket Water Cooler Reference Condition 
-Fouling Limit 06/29/98 I Shell and Tube Heat Exchanger Input Parameters 11 I.n ureT 0 To-T-l-Fg, pm Inlet Temperature OF Outlet Temperature OF Fouling Factor Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/hr)Design Heat Trans Coeff (BTU/hr-ft 2.&deg;F)Emprical Factor for Outside h Performance Factor (% Reduction)
Heat Exchanger Type Effective Area (ftA2)Area Factor Area Ratio Number of Shells per Unit Shell Minimum Area Shell Velocity (f'/s)Tube Pitch (in)Tube Pitch Type Shell-Side Tube-Side 7,0~9974-5 
.................
7 5- -190.00 100.00 174.40 122.20 D 0.00285 N 0.00000r O, Fresh Water 0.A) AJlf Fresh Water CA  8,600,000 255.20 0.780339000 0.00 TEMA-E 471.23 0.981978184 1 0.490000000 5.000 0.7500 Triangular Number of Tube Passes U-Tubes Total Number of Tubes Number of Active Tubes Tube Length (ft)Tube Inside Diameter (in)Tube Outside Diameter (in)Tube Wall Conductivity (BTU/hr'ft.&deg;F)
Ds, Shell Inside Diameter (in)Lbc, Central Baffle Spacing (in)Lbi, Inlet Baffle Spacing (in)Lbo, Outlet Baffle Spacing (in)Doti, Tube circle diameter (in)Bh, Baffle cut height (in)Lsb, Diametral difference between Baffle and Shell (in)Ltb, Diametral difference between Tube and Baffle (in)Nss, Number Sealing Strips 2 No 188 188 13.00 0.652 0.750 112.00 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-195 

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E Rev: A Page 8 of 13 12:29:43 P)ROTO-IIX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler Reference Condition 
-Fouling Limit 06/29/98 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions
[Fouling Was Input by User 1 IrhI"Ajiot L)sIN&: Fbtk%..tt,&(UIlL ReFE Cxtj1rotn D ata Extrapolation Data Test Data Data Date Shell Flow (gpm)Shell Temp In (fF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp ("F)Shell Inlet Temp (OF)Input Fouling Factor 795.3 1,064.5 100.0 190.0 0.002782 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr ft 2.&deg;F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-ft 2.-F)Tube-Side hi (BTU/hr.ft 2 F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr'ft 2.&deg;F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-t.&deg;F/BTU)
Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (&deg;F)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (OF)Skin Visc (lbm/ft-hr)
Tube Temp In (&deg;F)Density (Ibm/ft 3) Tube Temp Out (&deg;F)Cp (BTU/Ibm.&deg;F)
Tav Tube (OF)K (BTU/hr-ft-&deg;F)
Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/ft.hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/tl)Cp (BTU/Ibm.&deg;F)
K (BTUihr ft.&deg;F)5.325E+5&#xfd;>'FrgZrAa,..3.978E+5 71.1 471.2 Shell-Side Tube-Side 4.99 8.20 8.25 1E+04 6.738E+04 2.14 4.01 0.82 1.47 0.88 1.34 60.53 61.85 1.00 1.00 0.39 0.37 Overall Fouling (hr.ft2-&deg;F/BTU) 0.002782?Shell-Side ho (BTU/hr.ft 2.OF) 2,033.Tube-Side hi (BTU/hr-ft 2-F) 2,140.0 I/Wall Resis (BTU/hr-f 2.F) clv6,qt,, 25,594.8 LMTD Correction Factor 0.9885 Fou4ir.(6" U Overall (BTU/hr-ft 2.OF) FPC i'VP? 259.7 Shell Temp In (OF) 190.0 Shell Temp Out (OF) 173.9 Tav Shell (&deg;F) 181.9 Shell Skin Temp (OF) 172.9 Tube Temp In (&deg;F) 100.0 Tube Temp Out (OF) 121.6 Tav Tube (OF) 110.8 Tube Skin Calc: 97-195 120.8 

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E Rev: A Page 9 of 13** Reynolds Number Outside Range of Equation Applicability
!I With Minimum Fouling The Test Heat Load Could Not Be Achie 12:31:13 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler**** FINAL MODEL ****06/29/98 Shell and Tube Heat Exchanger Input Parameters II 1i d-Q-inhTi, TT-emperagpmur Inlet Temperature OF Outlet Temperature OF Fouling Factor Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/hr)Design Heat Trans Coeff (BTU/hr-ftl.&deg; Emprical Factor for Outside h Performance Factor (% Reduction)
Shell-Side Tube-Side~17J997.45 
...............
775 .6I ..190.00 -1epl)U,6')
100.00 174.40 122.20 078 1' 0.00000 5 Fresh Water Fresh Water 8,600,000 F) 255.20 0.780339000 0.00 TEMA-E 3cjt 0.981978184 1 0.490000000 5.000 0.7500 Triangular Heat Exchanger Type Effective Area (ftA2)Area Factor Area Ratio Number of Shells per Unit Shell Minimum Area Shell Velocity (ft/s)Tube Pitch (in)Tube Pitch Type Number of Tube Passes U-Tubes Total Number of Tubes Number of Active Tubes Tube Length (fi)Tube Inside Diameter (in)Tube Outside Diameter (in)Tube WMI Conductivity (BTU/hr-ft-.F)
Ds, Shell Inside Diameter (in)Lbc, Central Baffle Spacing (in)Lbi, Inlet Baffle Spacing (in)Lbo, Outlet Baffle Spacing (in)Dotl, Tube circle diameter (in)Bh, Baffle cut height (in)Lsb, Diametral difference between Baffle and Shell (in)Ltb, Diametral difference between Tube and Baffle (in)Nss, Number Sealing Strips 2 No 188 188 13.00 0.652 0.750 112.00 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-195 

==Attachment:==

E Rev: A Page 10 of 13 12:31:13 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler**** FINAL MODEL ****06/29/98.1 Calculation Specitications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions
[Design Fouling Factors Were Used- AtJ"S'E1)
A r TVS&- K'J 0 L.)FoLkiA6-" FAc70To Test Data Extrapolation Data Data Date Shell Flow (gpm)Shell Temp In (&deg;F)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (&deg;F)IN P,~OTo-H)'
Mo~GL Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)795.3 1,064.5 100.0 190.0 I. .1 II Fouling Calculation Results II 1 I.Shell Mass Flow (Ibm/hr)Tube Mass Flow (Ibm/ir)Heat Transferred (BTU/hr)LMTD Effective Area (ft')Property Shell-Side Tube-Side Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/ftl)Cp (BTU/Ibm-&deg;F)
K (BTU/hrIft.&deg;F)
U Overall (BTU/hr-ft 2-IF)Shell-Side ho (BTU/hr-ft-F)
Tube-Side hi (BTU/hr'ft-&deg;F)
I/Wall Resis (BTU/hr-ft 2.&deg;F)LMTD Correction Factor Overall Fouling (hr ft 2.&deg;F/BTU)Shell Temp In (IF)Shell Temp Out (&deg;F)Tav Shell (&deg;F)Shell Skin Temp (&deg;F)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Tav Tube (&deg;F)Tube Skin Temp (IF)Extrapolation Calculation Results I Shell Mass Flow (lbm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 3.978E+5 8.6E+6 71.1 471.2 Overall Fouling (hr'ft 2 0&deg;F/BTI1 Shell-Side ho (BTU/hr'ft 2 F)Tube-Side hi (BTU/hr'ft 2-&deg;F)I/Wall Resis (BTU/hr-ft 2 F)LMTD Correction Factor U Overall (BTU/hr-ft 2 F)) ,0.002782 2,033.3 AW)O5TC')
2,140.0-o dU ,, 6 ,, 25,594.8 0.9885 Property Shell-Side Tube-Side Velocity (ft/s) 4.99 8.20 Reynold's Number 8.25 1E+04 6.738E+04 Prandtl Number 2.14 4.01 Bulk Visc (lbmlft-hr) 0.82 1.47 Skin Visc (lbm/ft-hr) 0.88 1.34 Density (lbm/ft')
60.53 61.85 Cp (BTU/Ibm.&deg;F) 1.00 1.00 K (BTU/hr-ft.&deg;F) 0.39 0.37** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Shell Temp In (OF)Shell Temp Out (IF)Tav Shell (&deg;F)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (fF)Tav Tube (&deg;F)Tube Skin Temp (fF)trn 0'\C-U (-.)0 R0 I.-0 259.7 190.0 173.9 181.9 172.9 100.0 121.6 110.8 120.8 02 12:32:54 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DG0 I A -DG Jacket Water Cooler FINAL MODEL- CLEAN (0 Fouling)06/29/98 Shell and Tube Heat Exchanger Input Parameters
-11 Shell-Side F1-hii-&#xfd;Quantity, Total gpmih -_ 99745-------
Inlet Temperature OF 190.00 Outlet Temperature OF 174.40 Fouling Factor 0.00278 Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/hr)Design Heat Trans Coeff (BTU/hr. ft 2 .F)Emprical Factor for Outside h Performance Factor (% Reduction)
Tube-Side..775.-617-100.00 122.20 0.00000 Fresh Water Fresh Water 8,600,000 255.20 0.780339000 0.00 TEMA-E 471.23 0.981978184 1 0.490000000 5.000 0.7500 Triangular Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Number of Shells per Unit Shell Minimum Area Shell Velocity (ft/s)Tube Pitch (in)Tube Pitch Type Number of Tube Passes U-Tubes Total Number of Tubes Number of Active Tubes Tube Length (ft)Tube Inside Diameter (in)Tube Outside Diameter (in)Tube Wall Conductivity (BTU/hr-fViF)
Ds, Shell Inside Diameter (in)Lbc, Central Baffle Spacing (in)Lbi, Inlet Baffle Spacing (in)Lbo, Outlet Baffle Spacing (in)Dotl, Tube circle diameter (in)Bh, Baffle cut height (in)Lsb, Diametral difference between Baffle and Shell (in)Ltb, Diametral difference between Tube and Baffle (in)Nss, Number Sealing Strips 2 No 188 188 13.00 0.652 0.750 112.00 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-195 

==Attachment:==

E Rev: A Page 12 of 13 12:32:54 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Conunonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler FINAL MODEL- CLEAN (0 Fouling)06/29/98 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions IFouling Was Input by User] t F0t "'CLEAN" Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)Input Fouling Factor 795.3 1,064.5 100.0 190.0 0.000000 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.&deg;F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-fW.&deg;F)
Tube-Side hi (BTU/hr'ft 2 0'F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2-.F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2 0.F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (&deg;F)Skin Visc (Ibm/ft-hr)
Tube Temp In (IF)Density (lbm/ft')
Tube Temp Out (&deg;F)Cp (BTU/Ibm.&deg;F)
Tav Tube (IF)K (BTU/hlr.ft.&deg;F)
Tube Skin Temp (IF)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbrn/ft.hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/fl)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ftl.F) 5.325E+5Al 3.978E+51 1.885E+7]48.3 471.2 Shell-Side Tube-Side 4.97 8.22 7.72 1E+04 7.626E+04 2.29 3.50 0.88 1.30 1.05 1.07 60.74 61.65 1.00 1.00 0.38 0.37 Overall Fouling (hr-ft.&deg;F/BTU) 0.000000 Shell-Side ho (BTU/hr.ft 2-&deg;F) 1,957.5 Tube-Side hi (BTU/hr-fW-0 F) "e.' 2,318.4 I/Wall Resis (BTU/hr-ft 2.&deg;F) 25,594.8 LMTD Correction Factor 0.8656 U Overall (BTU/hr-ft 2.&deg;F)Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (&deg;F)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)ad, 0\0 00.4) C 955.9 190.0 154.6 172.3 148.6 100.0 147.4 123.7 146.8** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Attachment F to Proto-Power Calculation 97-195 Revision A Proto-Power Caic: 97-195 

==Attachment:==

F Rev: A Page 1 of 6 15:49:57 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIX-0000)
Commonwealth Edison Calculation Report for DGO I A -DG Jacket Water Cooler Tube-side Fouling = 0.0000 06/29/98 I.Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User II Test Data Data Date Shell Flow (gpm)Shell Temp In (OF)Shell Temp Out (&deg;F)Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (OF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (&deg;F)Shell Inlet Temp (&deg;F)Input Fouling Factor 795.3 1,064.5 100.0 190.0 0.000500 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2.&deg;F)Tube Mass Flow (Ibmlhr) Shell-Side ho (BTU/hr ft 2 -F)Tube-Side hi (BTUihr-ft 2-&deg;F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2-&deg;F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ftl-&deg;F/BTU)
Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (&deg;F)Reynold's Number Shell Temp Out (&deg;F)Prandtl Number Tav Shell (&deg;F)Bulk Visc (Ibm/ft hr) Shell Skin Temp (OF)Skin Vise (lbm/ft-hr)
Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (&deg;F)Cp (BTU/Ibm'&deg;F)
Tav Tube (&deg;F)K (BTU/hr-ft.&deg;F)
Tube Skin Temp (OF)[17 _ Extrapolation Calculation Results Shell Mass Flow.(lbm/hr)
Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 3.978E+5 1.57E+7 55.4 471.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft')Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-0 F)Shell-Side Tube-Side 4.98 8.22 7.883E+04 7.349E+04 2.24 3.64 0.86 1.35 0.98 1.15 60.68 61.72 1.00 1.00 0.39 0.37 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.0'Shell-Side ho (BTU/hr-ft 2-OF) 1I Tube-Side hi (BTU/hr-ft 2.OF) 2.I/Wall Resis (BTU/hr.ft 2.OF) 25.LMTD Correction Factor C U Overall (BTU/hr-ft 2.&deg;F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (&deg;F)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (OF)Tube Skin TemPttftb-Power Calc: 97-195 

==Attachment:==

F Rev: A Page 2 of 6 00500 ,983.9 ,261.9 ,594.8.9332 644.5 190.0 160.6 175.3 157.2 100.0 139.5 119.8 138.0** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 15:5 1:47 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DG01A -DG Jacket Water Cooler Tube-side Fouling = 0.0005 06/29/98.1 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User II Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (OF)Shell Inlet Temp (OF)Input Fouling Factor 795.3 1,064.5 100.0 190.0 0.001075 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2-0 F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/h~rft 2" 0 F)Tube-Side hi (BTU/hr'ft 2-OF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2 -F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2"&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Vise (lbm/ft'hr)
Shell Skin Temp (IF)Skin Vise (Ibm/ft-hr)
Tube Temp In (IF)Density (Ibm/ft 3) Tube Temp Out (IF)Cp (BTU/Ibm 0'F) Tav Tube (&deg;F)K (BTU/hr'ft'&deg;F)
Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow.(Ibm/hr)
Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ftz)5.325E+5 3.978E+5 1.304E+7 61.3 471.2 Overall Fouling (hr-ft 2-&deg;F/BTU)Shell-Side ho (BTU/hr'fi 2.&deg;F)Tube-Side hi (BTU/hr-ft 2'&deg;F)1/Wall Resis (BTU/hr-ft 2.&deg;F)LMTD Correction Factor 0.001075 2,003.3 2,216.1 25,594.8 0.9633 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/ftihr)
Skin Visc (lbm/ft.hr)
Density (Ibm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft 0'F)Shell-Side Tube-Side 4.98 8.21 8.020E+04 7.118E+04 2.20 3.77 0.85 1.39 0.94 1.21 60.62 61.77 1.00 1.00 0.39 0.37 U Overall (BTU/hr'ft 2"&deg;F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Te~rirtl-Power Caic: 97-195 

==Attachment:==

F Rev: A Page 3 of 6 469.0 190.0 165.6 177.8 163.4 100.0 132.8 116.4 131.4** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 15:53:34 PROTO-HX 3.02 by Proto-Power Corporation (SN#IPHX-0000)
Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler Tube-side Fouling = 0.0010 06/29/98 I. .1 Calculation Specitications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)Input Fouling Factor 795.3 1,064.5 100.0 190.0 0.001650 FE Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2 0.F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr ft 2-OF)Tube-Side hi (BTU/hr-ft 2"&deg;F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft1.
0 F)LMTD LMTD Correction Factor Effective Area (ftW)Overall Fouling (hr-ft 2.0 F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (OF)Skin Visc (lbm/ftrhr)
Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (IF)Cp (BTU/Ibm-0 F) Tav Tube (OF)K (BTU/hr-ft 0.F) Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow.(lbmlhr)
Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 3.978E+5 1.112E+7 65.5 471.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft'hr)
Density (Ibm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr-ft.
0 F)Shell-Side Tube-Side 4.98 8.20 8.120E+04 6.953E+04 2.17 3.87 0.84 1.43 0.91 1.27 60.58 61.80 1.00 1.00 0.39 0.37 Overall Fouling (hr.ft2.&deg;F/BTU)
Shell-Side ho (BTU/hr-ft 2.&deg;F)Tube-Side hi (BTU/hr.ft 2.OF)I/Wall Resis (BTU/hr-ft 2.&deg;F)LMTD Correction Factor U Overall (BTU/hr-ft 2 OF)Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (IF) u Shell Skin Temp (OF) 7a Tube Temp In (OF) 2 Tube Temp Out (OF)Tav Tube (IF) 0 Tube Skin Temp (IF)P0 0.001650 2,016.5 2,183.2 25,594.8 0.9770 0 368.8 190.0 169.2 179.6 167.6 100.0 128.0 114.0 126.7 cd** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 15:54:32 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler Tube-side Fouling = 0.00 15 06/29/98 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (fF)Shell Inlet Temp (OF)Input Fouling Factor 795.3 1,064.5 100.0 190.0 0.002225 FI Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2.&deg;F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr.ft 2"&deg;F)Tube-Side hi (BTU/hr.ft 2-&deg;F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hrtft 2.&deg;F)LMTD LMTD Correction Factor Effective Area (ft')Overall Fouling (hr. ft 2 -F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (&deg;F)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ftbhr)
Shell Skin Temp (OF)Skin Visc (Ibm/ft-hr)
Tube Temp In (&deg;F)Density (Ibm/ft')
Tube Temp Out (OF)Cp (BTU/Ibm-&deg;F)
Tav Tube (&deg;F)K (BTU/hr-ft-&deg;F)
Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow..(lbm/hr)
Tube Mass Flow (lbm/hr)Heat Transferred (BTUihr)LMTD Effective Area (ft 2)Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbmnft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Shell-Side 4.99 8.194E+04 2.15 0.83 0.89 60.55 1.00 0.39 5.325E+5 3.978E+5 9.683E+6 68.7 471.2 Tube-Side 8.20 6.830E+04 3.95 1.45 1.31 61.83 1.00 0.37 Overall Fouling (hr-ft 2-&deg;F/BTU)Shell-Side ho (BTU/hr-ft 2-&deg;F)Tube-Side hi (BTU/hr-ft 2.&deg;F)I/Wall Resis (BTU/hr-ft 2-IF)LMTD Correction Factor U Overall (BTU/hr ft 2.&deg;F)0.002225 2,026.2 2,158.6 25,594.8 0.9842 Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (&deg;F)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (fF)0n 0 0 S.0-4 cg 0 II..co Ce 303.9 190.0 171.9 180.9 170.6 100.0 124.4 112.2 123.3** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 15:55:33 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PIX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler Tube-side Fouling = 0.001984 (LIMIT)06/29/98 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (&deg;F)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (&deg;F)Input Fouling Factor 795.3 1,064.5 100.0 190.0 0.002782 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr ft 2.&deg;F)Tube Mass Flow (lbmlhr) Shell-Side ho (BTU/hr-ft 2-&deg;F)Tube-Side hi (BTU/hr-ft 2-.F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2.&deg;F)LMTD LMTD Correction Factor Effective Area (ft')Overall Fouling (hr-ft 2 0.F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ft-hr)
Shell Skin Temp (IF)Skin Visc (lbm/ft-hr)
Tube Temp In (IF)Density (lbm/fP) Tube Temp Out (IF)Cp (BTU/Ibm-&deg;F)
Tav Tube (IF)K (BTU/hrift.&deg;F)
Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (fi 2)5.325E+5 3.978E+5 8.6E+6 71.1 471.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-0 F)K (BTU/hr-ft.&deg;F)
Shell-Side Tube-Side 4.99 8.20 8.251E E+04 6.738E+04 2.14 4.01 0.82 1.47 0.88 1.34 60.53 61.85 1.00 1.00 0.39 0.37 Overall Fouling (hr-ft 2.&deg;F/BTU)Shell-Side ho (BTU/hr.ft 2.OF)Tube-Side hi (BTU/hr.ft 2.OF)I/Wall Resis (BTU/hr-ft 2.&deg;F)LMTD Correction Factor U Overall (BTU/hr-ft 2-&deg;F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (&deg;F)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (OF)Tube Skin Temp (OF)0.002782 2,033.3 2,140.0 25,594.8 0.9885 W)0 0 0 P-4 0'0 259.7 190.0 173.9 181.9 172.9 100.0 121.6 110.8 120.8** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Attachment G to Proto-Power Calculation 97-195 Revision A Proto-Power Calc: 97-195 

==Attachment:==

G Rev: A Page 1 of 17 09:31:42 PROTO-HX 3.02 by Proto-Power Corporation (SN#IPX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 35 0 F 06/29/98 II Calculation Specifications 11 Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)193.5 1,064.5 35.0 190.0 Fouling Calculation Results Shell Mass Flow (lbmlhr) U Overall (BTU/hrft2.&deg;'F)
Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-ft.'
0 F)Tube-Side hi (BTU/hr ft2.'F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr'ft2"&deg;F)
LMTD LMTD Correction Factor Effective Area (ft')Overall Fouling (hr-ft 2.'F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (&deg;F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (&deg;F)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (IF)Skin Visc (Ibm/ft-hr)
Tube Temp In (IF)Density (lbm/ft')
Tube Temp Out (OF)Cp (BTU/lbm 0'F) Tav Tube (&deg;F)K (BTU/hr'ft-&deg;F)
Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow.(lbm/hr)
Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')5.325E+5 9.68E+4 8.6E+6 98.1 471.2 Overall Fouling (hr-ft2.&deg;F/BTU)
Shell-Side ho (BTU/hr'ft2.&deg;F)
Tube-Side hi (BTU/hr-ft 0.F)1/Wall Resis (BTU/hr-ftz'.F)
LMTD Correction Factor 0.002782 2,032.2 599.1 25,594.8 0.9740 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/fthr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr"ft'&deg;F)
Shell-Side 4.99 8.25 1E+04 2.14 0.82 0.88 60.53 1.00 0.39 Tube-Side 1.98 I. 155E+04 5.90 2.09 1.39 62.22 1.00 0.35 U Overall (BTU/hr-ft2.
0 F) I Shell Temp In (IF) I Shell Temp Out (F) I Tav Shell (IF) I Shell Skin Temp (IF) I Tube Temp In (IF)Tube Temp Out (OF) I Tav Tube ('F)Tube Skin Temp (IF) I Proto-Power Calc: 97-195 

==Attachment:==

G Rev: A Page 2 of 17 91.1 90.0 73.9 81.9 72.3 35.0 23.9 79.4 17.0** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 09:28:13 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 40'F 06/29/98 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Extrapolation Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)204.8 1,064.5 40.0 190.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2.0 F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-ft 2 0.F)Tube-Side hi (BTU/hr-ft 2-OF)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hruft 2.0 F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2.&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (OF)Skin Visc (lbm/ftrhr)
Tube Temp In (&deg;F)Density (Ibm/ftl)
Tube Temp Out (IF)Cp (BTU/Ibm'&deg;F)
Tav Tube (IF)K (BTU/hr-ft-&deg;F)
Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 1.024E+5 8.6E+6 96.0 471.2 Overall Fouling (hr-ft 2.&deg;F/BTU)Shell-Side ho (BTU/hr-ft 2-&deg;F)Tube-Side hi (BTU/hr-ft 2-&deg;F)l/Wall Resis (BTU/hr.ft2-&deg;F)
LMTD Correction Factor U Overall (BTU/hr ft 2-&deg;F)0.002782 2,032.3 634.9 25,594.8 0.9744 195.1 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (lbm/ft)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft.&deg;F)
Shell-Side Tube-Side 4.99 2.10 8.25 1E+04 1.261E+04 2.14 5.70 0.82 2.02 0.88 1.38 60.53 62.20 1.00 1.00 0.39 0.36 Shell Temp In (IF) 190.0 Shell Temp Out (0 F) 173.9 Tav Shell (&deg;F) 181.9 Shell Skin Temp (&deg;F) 172.3 Tube Temp In (&deg;F) 40.0 Tube Temp Out (IF) 124.0 Tav Tube (&deg;F) 82.0 Tube Skin Temp (&deg;F) 117.3 Proto-Power Calc: 97-195 

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G Rev: A Page 3 of 17** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 09:23:51 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DG01A -DG Jacket Water Cooler CSCS = 50OF 06/29/98 I .--I I I -Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used 11 Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)232.2 1,064.5 50.0 190.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2-.F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2 0.F)Tube-Side hi (BTU/hr'ft 2"&deg;F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr'ft 2.F)LMTD LMTD Correction Factor Effective Area (ft')Overall Fouling (hr.-ftF/BTU)
Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (&deg;F)Reynold's Number Shell Temp Out (&deg;F)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ftrhr)
Shell Skin Temp (IF)Skin Vise (Ibm/ft hr) Tube Temp In (&deg;F)Density (Ibm/ftl)
Tube Temp Out (IF)Cp (BTU/Ibm 0'F) Tav Tube (IF)K (BTU/hr'ft'&deg;F)
Tube Skin Temp (&deg;F)Extrapolation Calculation Results Shell Mass Flow (lbma/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 1. 162E+5 8.6E+6 91.9 471.2 Overall Fouling (hr-ft 2 0'F/BTU)Shell-Side ho (BTU/h'ft 2-&deg;F)Tube-Side hi (BTU/hrft 2 0-OF)1/Wall Resis (BTU/hr'ft 2-OF)LMTD Correction Factor 0.002782 2,032.5 719.6 25,594.8 0.9756 Property Shell-Side Tube-Side Velocity (ft/s) 4.99 2.38 Reynold's Number 8.251E+04 1.520E+04 Prandtl Number 2.14 5.33 Bulk Visc (Ibm/ft-hr) 0.82 1.91 ( Skin Visc (lbm/ft-hr) 0.88 1.37 Density (lbm/ft')
60.53 62.15 Cp (BTU/Ibm 0'F) 1.00 1.00 K (BTU/hr'ft 0'F) 0.39 0.36** Reynolds Number Outside Range of Equation Applicability I With Minimum Fouling The Test Heat Load Could Not Be Achie U Overall (BTU/hr-ft 2'-F)Shell Temp In (IF)Shell Temp Out (&deg;F)Tav Shell (&deg;F)Shell Skin Temp (IF)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Tav Tube (IF)Tube Skin Temp (&deg;F)P'roto-Power Calc: 97-195 

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G Rev: A Page 4 of 17 203.6 190.0 173.9 181.9 172.4 50.0 124.1 87.0 117.9 09:11:37 PROTO-HX 3.02 by Proto-Power Corporation (SN#IIPHX-0000)
Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler CSCS = 60'F 06/29/98 I1 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)269.1 1,064.5 60.0 190.0 Fouling Calculation Results Shell Mass Flow (lbmihr) U Overall (BTU/hr ft 2.&deg;F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr.ft 2.0 F)Tube-Side hi (BTU/hr-ft 2.0 F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2.0 F)LMTD LMTD Correction Factor Effective Area (ft')Overall Fouling (hr-ft 2-&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (OF)Bulk Vise (lbm/ft-hr)
Shell Skin Temp (IF)Skin Visc (lbm/ft-hr)
Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (IF)Cp (BTU/lbm.'F)
Tav Tube (IF)K (BTU/hr-ft.&deg;F)
Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)Property Shell-Side Velocity (ft/s) 4.99 Reynold's Number 8.251E+04 Prandtl Number 2.14 Bulk Visc (lbm/ft-hr) 0.82 Skin Visc (lbm/ft-hr) 0.88 Density (Ibm/ft')
60.53 Cp (BTU/lbm.&deg;F) 1.00 K (BTU/hr-ft-&deg;F) 0.39 5.325E+5 1.346E+5 8.6E+6 87.8 471.2 Overall Fouling (hr-ft2-&deg;F/BTU)
Shell-Side ho (BTU/hr-ft 2.&deg;F)Tube-Side hi (BTU/hr-ft 2-OF)l/Wall Resis (BTU/hr-ft 2.F)LMTD Correction Factor U Overall (BTU/hr-ft 2.OF)0.002782 2,032.7 828.7 25,594.8 0.9770 212.7 Tube-Side 2.76 1.865E+04 5.00 1.80 1.37 62.09 1-00 0.36 Shell Temp In (IF) 190.0 Shell Temp Out (IF) 173.9 Tav Shell (IF) 181.9 Shell Skin Temp (IF) 172.5 Tube Temp In (OF) 60.0 Tube Temp Out (IF) 123.9 Tav Tube (IF) 92.0 Tube Skin Temp_(`F) 118.5 Proto-Power Calc: 97-195 

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G Rev: A Page 5 of 17** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 09:06:52 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler CSCS = 70OF 06/29/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Extrapolation Data Data Date Tube Flow (gpm) 321.0 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In (IF) Tube Inlet Temp (IF) 70.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 190.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr~ft 2-'F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hrlft 2.-F)Tube-Side hi (BTU/hr.ft 2.IF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr'ft 2-&deg;F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2.&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (OF)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (OF)Skin Visc (lbm/ft-hr)
Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (OF)Cp (BTU/lbm 0'F) Tav Tube (OF)K (BTU/hr-ft 0'F) Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow. (lbm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 1.606E+5 8.6E+6 83.7 471.2 Overall Fouling (hr-ft 2-FBTU)Shell-Side ho (BTU/hr-ft 2-&deg;F)Tube-Side hi (BTU/hr-ft 2.&deg;F)1/Wall Resis (BTU/hr ft 2-OF)LMTD Correction Factor 0.002782 2,032.8 975.6 25,594.8 0.9790 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft'hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft-0 F)Shell-Side Tube-Side 4.99 3.30 8.251E+04 2.348E+04 2.14 4.71 0.82 1.71 0.88 1.36 60.53 62.03 1.00 1.00 0.39 0.36 U Overall (BTU/hr-ft 2-IF) 2, Shell Temp In (&deg;F) 1I Shell Temp Out (OF) 1I Tav Shell (IF) I1 Shell Skin Temp (OF) I Tube Temp In (IF)Tube Temp Out (OF) I Tav Tube (OF)Tube Skin Temp (OF) I Proto-Power Calc: 97-195 

==Attachment:==

G Rev: A Page 6 of 17 22.6)0.0 73.9 81.9 72.6 70.0 23.6 96.8 19.2** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 09:03:56 PROTO-HX 3.02 by Proto-Power Corporation (SNPHIX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = SOF 06/29/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Extrapolation Data Data Date Tube Flow (gpm) 399.3 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In (IF) Tube Inlet Temp ('F) 80.0 Shell Temp Out (OF) Shell Inlet Temp (OF) 190.0 Tube Flow (gpm)Tube Temp In (0 F)Tube Temp Out (IF)Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr ft 2-OF)Tube Mass Flow (lbmfhr) Shell-Side ho (BTU/hr-ft 2-OF)Tube-Side hi (BTU/hr-ft 2-OF)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr.ft 2-IF)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2.&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (OF)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (OF)Skin Vise (Ibm/ft-hr)
Tube Temp In (OF)Density (Ibm/ft 3) Tube Temp Out (OF)Cp (BTU/Ibm.0 F) Tav Tube (IF)K (BTU/hr-ft-&deg;F)
Tube Skin Temp (IF)Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')5.325E+5 1.997E+5 8.6E+6 79.6 471.2 Overall Fouling (hr-ft'.&deg;F/BTU)
Shell-Side ho (BTU/hr-ft 2.&deg;F)Tube-Side hi (BTU/hrpft 2.0 F)I/Wall Resis (BTU/hr.ft 2.IF)LMTD Correction Factor U Overall (BTU/hr-ft 2-F)0.002782 2,033.0 1,186.3 25,594.8 0.9814 233.5 C4.4 190.0 173.9 t- ff l Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbmift-hr)
Skin Vise (lbm/ft.hr)
Density (Ibm/ft 3)Cp (BTU/Ibm-0 F)K (BTU/hr-ft-&deg;F)
Shell-Side Tube-Side 4.99 4.11 8.25 IE+04 3.075E+04 2.14 4.45 0.82 1.62 0.88 1.35 60.53 61.97 1.00 1.00 0.39 0.36 Shell Temp In (&deg;F)Shell Temp Out (&deg;F)Tav Shell (&deg;F)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (OF)U0~0~0 0 172.7 80.0 123.1 101.5 119.8 4)** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 09:00:52 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DG0IA -DG Jacket Water Cooler CSCS = 90&deg;F 06/29/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Extrapolation Data Data Date Tube Flow (gpm) 530.9 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In (IF) Tube Inlet Temp (IF) 90.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 190.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr.ft 2 F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr.ftzO.F)
Tube-Side hi (BTU/hr-ft 2.&deg;F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2.F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hrft 2-&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (OF)Bulk Vise (lbm/ft-hr)
Shell Skin Temp (IF)Skin Vise (lbm/ft-hr)
Tube Temp In (IF)Density (lbm/ft')
Tube Temp Out (IF)Cp (BTU/lbm 0'F) Tav Tube (&deg;F)K (BTU/hr'ft.&deg;F)
Tube Skin Temp (&deg;F)Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 2.656E+5 8.6E+6 75.4 471.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Vise (lbm/ft'hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm.0 F)K (BTU/hr-ft.&deg;F)
Shell-Side Tube-Side 4.99 5.47 8.251E+04 4.293E+04 2.14 4.22 0.82 1.54 0.88 1.34 60.53 61.91 1.00 1.00 0.39 0.37 Overall Fouling (hr ft 2-&deg;F/BTU)Shell-Side ho (BTU/hr.ft 2.&deg;F)Tube-Side hi (BTU/hr-ft 2-&deg;F)1/Wall Resis (BTU/hr-ft 2 0.F)LMTD Correction Factor U Overall (BTU/hr ft 2.&deg;F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (TF)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (&deg;F)Tube Skin Temp (OF)0.002782 2,033.2 1,519.8 25,594.8 0.9845 0Li 1.-V 0 10 04 I-04-00 00 245.7 190.0 173.9 181.9 172.8 90.0 122.4 106.2 120.3** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 08:54:07 PROTO-HX 3.02 by Proto-Power Corporation (SNPIPX-0000)
Commonwealth Edison Calculation Report for DG01A -DG Jacket Water Cooler CSCS = 100&deg;F 06/29/98 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Shell Flow (gpm)Shell Temp In (0 F)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)795.3 1,064.5 100.0 190.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2 0-F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr'ft 2'&deg;F)Tube-Side hi (BTU/hr-ft 2.&deg;F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr ft 2.&deg;F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr ft 2.&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (&deg;F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (&deg;F)Bulk Visc (Ibm/ft-hr)
Shell Skin Temp (&deg;F)Skin Visc (Ibm/ft-hr)
Tube Temp In (&deg;F)Density (Ibm/fl 3) Tube Temp Out (&deg;F)Cp (BTU/Ibm.&deg;F)
Tav Tube (IF)K (BTU/hr-ft-&deg;F)
Tube Skin Temp (&deg;F)Extrapolation Calculation Results Shell Mass Flow.(lbm/hr)
Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')5.325E+5 3.978E+5 8.6E+6 71.1 471.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr-ft.&deg;F)
Shell-Side Tube-Side 4.99 8.20 8.251E E+04 6.738E+04 2.14 4.01 0.82 1.47 0.88 1.34 60.53 61.85 1.00 1.00 0.39 0.37 Overall Fouling (hr'ft 2.&deg;F/BTU)Shell-Side ho (BTU/hrft 2.0 F)Tube-Side hi (BTU/hr-ft 2.&deg;F)I/Wall Resis (BTU/hr.ft 2.&deg;F)LMTD Correction Factor U Overall (BTU/hr ft 2.OF)Shell Temp In (OF)Shell Temp Out (IF)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)0.002782 2,033.3 2,140.0 25,594.8 0.9885 tn -C-.0 00 259.7 190.0 173.9 181.9 172.9 100.0 121.6 110.8 120.8** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 11:02:12 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 35 0 F 06/29/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Extrapolation Data Data Date Tube Flow (gpm) 161.1 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In (OF) Tube Inlet Temp (OF) 35.0 Shell Temp Out (OF) Shell Inlet Temp (OF) 190.0 Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2.&deg;F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr ft 2'&deg;F)Tube-Side hi (BTU/hr-ft 2"&deg;F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2"&deg;F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2&deg;F/BTLJ)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (OF)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (fF)Skin Vise (lbm/ft-hr)
Tube Temp In (OF)Density (lbm/ft 1) Tube Temp Out (OF)Cp (BTU/Ibm-&deg;F)
Tav Tube (7F)K (BTU/hr-ft.&deg;F)
Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow (lbmn/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 8.059E+4 7.8E+6 93.3 471.2 Overall Fouling (hr'ft 2-&deg;F/BTU)Shell-Side ho (BTU/hr-ft 2.&deg;F)Tube-Side hi (BTU/hr.ft 2-F)I/Wall Resis (BTU/hr-ft 2.&deg;F)LMTD Correction Factor U Overall (BTU/hr'ft 2.&deg;F)0.002782 2,037.1 531.4 25,594.8 0.9713 182.6 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbmrft-hr)Skin Visc (lbm/ft-hr)Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr.ft.&deg;F)
Shell-Side Tube-Side 4.99 1.65 8.292E+04 1.010E+04 2.13 5.59 0.82 1.99 0.87 1.31 60.52 62.18 1.00 1.00 0.39 0.36 Shell Temp In (OF)Shell Temp Out (&deg;F)Tav Shell (OF)Shell Skin Temp ('F)Tube Temp In ('F)Tube Temp Out (OF)Tav Tube (&deg;F)Tube Skin Temp ('F)"7 0~0~1-01 0 N C 4-4 0 04 co 190.0 175.4 182.7 173.8 35.0 131.8 83.4 122.7** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:45:26 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DG01A -DG Jacket Water Cooler CSCS = 40OF 06/29/98 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Shell Flow (gpm)Shell Temp In ('F)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)169.8 1,064.5 40.0 190.0[1 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.&deg;F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2.&deg;F)Tube-Side hi (BTU/hr-ft 2 0.F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr'ft 2"F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr- ft 2 0'F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (&deg;F)Reynold's Number Shell Temp Out (&deg;F)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (OF)Skin Visc (Ibm/ft hr) Tube Temp In (&deg;F)Density (lbm/ft 3) Tube Temp Out (&deg;F)Cp (BTU/Ibm'&deg;F)
Tav Tube (&deg;F)K (BTU/hr-ft.&deg;F)
Tube Skin Temp (IF)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft')Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft.&deg;F)
Shell-Side 4.99 8.292E+04 2.13 0.82 0.87 60.52 1.00 0.39 5.325E+5 8.492E+4 7.8E+6 91.4 471.2 Tube-Side 1.74 1.097E+04 5.40 1.93 1.31 62.16 1.00 0.36 Overall Fouling (hr ft 2-&deg;F/BTU)Shell-Side ho (BTU/hr-ft 2-&deg;F)Tube-Side hi (BTU/hr-ft 2.&deg;F)I/Wall Resis (BTU/hr-ft 2.F)LMTD Correction Factor U Overall (BTU/hr ft 2.OF)Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (&deg;F)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (&deg;F)0.002782 2,037.2 561.0 25,594.8 0.9716 U 1..00186.5 190.0 175.4 182.7 173.8 40.0 131.9 86.0 122.9** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:40:50 PROTO-lX 3.02 by Proto-Power Corporation (SN#ItX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 50'F 06/29/98 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Shell Flow (gpm)Shell Temp In (&deg;F)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (&deg;F)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (&deg;F)190.5 1,064.5 50.0 190.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2.&deg;F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr'ft 2-&deg;F)Tube-Side hi (BTU/hr ft 2 -F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr ft 2-&deg;F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2 .F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (&deg;F)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ft hr) Shell Skin Temp (&deg;F)Skin Visc (Ibm/ft-hr)
Tube Temp In (IF)Density (Ibm/ft 3) Tube Temp Out (&deg;F)Cp (BTU/lbm-&deg;F)
Tav Tube (IF)K (BTU/hr-ft-&deg;F)
Tube Skin Temp (&deg;F)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 9.527E+4 7.8E+6 87.5 471.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-ir)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/Ibm-0 F)K (BTU/hr-ft-&deg;F)
Shell-Side 4.99 8.292E+04 2.13 0.82 0.87 60.52 1.00 0.39 Tube-Side 1.96 1.305E+04 5.06 1.82 1.30 62.10 1.00 0.36 Overall Fouling (hr ft 2.F/BTU)Shell-Side ho (BTU/hr-ft 2-&deg;F)Tube-Side hi (BTU/hrlft 2-&deg;F)I/Wall Resis (BTU/hr-ft 2-&deg;F)LMTD Correction Factor U Overall (BTU/hr.ft 2-IF)Shell Temp In (&deg;F)Shell Temp Out (IF)Tav Shell (&deg;F)Shell Skin Temp (&deg;F)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Tav Tube (&deg;F)Tube Skin Temp (IF)"7 0*i 0,.0 4-.0 1-o4 0.002782 2,037.4 629.9 25,594.8 0.9726 0 194.6 190.0 175.4 182.7 173.9 50.0 131.9 91.0 123.6 4-.4)** Reynolds Number Outside Range of Equation Applicability
!I With Minimum Fouling The Test Heat Load Could Not Be Achie 10:24:06 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PflX-0000)
Commonwealth Edison Calculation Report for DGO I A -DG Jacket Water Cooler CSCS = 60'F 06/29/98.1 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (0 F)Tube Temp Out (OF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)217.5 1,064.5 60.0 190.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2-&deg;F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-ft 2"&deg;F)Tube-Side hi (BTU/hr.ft 2.OF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hrift 2.OF)LMTD LMTD Correction Factor Effective Area (ft2)Overall Fouling (hr-ft 2"&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (IF)Skin Vise (lbm/ft-hr)
Tube Temp In (IF)Density (lbm/ft) Tube Temp Out (IF)Cp (BTU/Ibm-'F)
Tav Tube (IF)K (BTU/hr'ft-0 F) Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (lbmlhr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')Property Shell-Side Velocity (ft/s) 4.99 Reynold's Number 8.292E+04 Prandtl Number 2.13 Bulk Visc (lbm/ft-hr) 0.82 Skin Visc (lbm/ft'hr) 0.87 Density (Ibm/fr) 60.52 Cp (BTU/lbm&deg;F) 1.00 K (BTU/hrft'&deg;F) 0.39 5.325E+5 1.088E+5 7.8E+6 83.6 471.2 Tube-Side 2.24 1.575E+04 4.76 1.72 1.29 62.05 1.00 0.36 Overall Fouling (hr.ft2.&deg;F/BTU)
Shell-Side ho (BTU/hr.ft 2-&deg;F)Tube-Side hi (BTU/hr.ft 2.OF)I/Wall Resis (BTU/hr ft 2-OF)LMTD Correction Factor U Overall (BTU/hr-ft 2 OF)Shell Temp In (IF)Shell Temp Out (&deg;F)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (&deg;'F)0.002782 2,037.6 716.3 25,594.8 0.9739 U 00 4-1 0 203.3 190.0 175.4 182.7 174.0 60.0 131.8 95.9 124.2** Reynolds Number Outside Range of Equation Applicability H With Minimum Fouling The Test Heat Load Could Not Be Achie 10:16:36 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 70OF 06/29/98 I. .1 Calculation Specifications 11 Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)254.2 1,064.5 70.0 190.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr'ft 2.&deg;F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-ft 2'-F)Tube-Side hi (BTU/hr-ft.&deg;F)
Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2-&deg;F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2.&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (&deg;F)Reynold's Number Shell Temp Out (&deg;F)Prandtl Number Tav Shell (&deg;F)Bulk Visc (lbm/ft hr) Shell Skin Temp (&deg;F)Skin Visc (lbm/ft-hr)
Tube Temp In (&deg;F)Density (lbm/fV) Tube Temp Out (&deg;F)Cp (BTU/Ibm-&deg;F)
Tav Tube (IF)K (BTU/hr-ft.&deg;F)
Tube Skin Temp (&deg;F)Extrapolation Calculation Results Shell Mass Flow.(lbmnhr)
Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')5.325E+5 1.272E+5 7.8E+6 79.7 471.2 Overall Fouling (hr'ft 2.&deg;F/BTU)Shell-Side ho (BTU/hr-ft 2 0.F)Tube-Side hi (BTU/hr-ft 2-&deg;F)I/Wall Resis (BTU/hr-ft 2-OF)LMTD Correction Factor U Overall (BTU/hr-ft 2.&deg;F)0.002782 2,037.8 829.2 25,594.8 0.9757 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ftR)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Shell-Side Tube-Side 4.99 2.62 8.292E+04 1.940E+04 2.13 0.82 0.87 60.52 1.00 0.39 4.50 1.63 1.29 61.99 1.00 0.36 Shell Temp In (&deg;F)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Tav Tube (IF)Tube Skin Temp (&deg;F)tn 0 CIS-0u 0 C*2 A(212.8 190.0 175.4 182.7 174.1 70.0 131.4 100.7 124.9** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:12:25 PROTO-HX 3.02 by Proto-Power Corporation (SN#IPX-0000)
Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 80OF 06/29/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Extrapolation Data Data Date Tube Flow (gpm) 307.0 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In (OF) Tube Inlet Temp (IF) 80.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 190.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Fouling Calculation Results Shell Mass Flow (Ibm/lhr)
U Overall (BTU/hr-ft 2 0-F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hrIft 2.&deg;F)Tube-Side hi (BTU/hr-ft 2.0 F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft.&deg;F)
LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2.&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ft-hr)
Shell Skin Temp (IF)Skin Vise (lbmn/ft-hr)
Tube Temp In (IF)Density (ibm/fl 3) Tube Temp Out (IF)Cp (BTU/1bm-'F)
Tav Tube (IF)K (BTU/hr-ft.&deg;F)
Tube Skin Temp (IF)Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ftW)5.325E+5 1.536E+5 7.8E+6 75.8 471.2 Overall Fouling (hr-ft2.0 F/BTU)Shell-Side ho (BTU/hr ft 2-OF)Tube-Side hi (BTU/hr.ft 2'-F)1/Wall Resis (BTU/hr.ft 2.&deg;F)LMTD Correction Factor 0.002782 2,038.0 984.2 25,594.8 0.9779 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbmr/ft)Cp (BTU/Ibm 0'F)K (BTU/hr-ft.&deg;F)
Shell-Side Tube-Side 4.99 3.16 8.292E+04 2.462E+04 2.13 0.82 0.87 60.52 1.00 0.39 4.26 1.56 1.28 61.92 1.00 0.37 U Overall (BTU/hr-ft 2.&deg;F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (&deg;F)tn U 0 0 I-0223.2 190.0 175.4 182.7 174.2 80.0 130.8 105.4 125.6** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:08:33 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DGOI A -DG Jacket Water Cooler CSCS = 90&deg;F 06/29/98 Calculation Specifications II[Ij Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Shell Flow (gpm)Shell Temp In (&deg;F)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (&deg;F)Shell Inlet Temp (fF)389.3 1,064.5 90.0 190.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2-&deg;F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr'ft 2 0'F)Tube-Side hi (BTU/hr'ft 2-&deg;F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2-&deg;F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr ft 2.&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (&deg;F)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)
Shell Skin Temp (OF)Skin Visc (lbmr/ft-hr)
Tube Temp In (OF)Density (lbm/ft) Tube Temp Out (IF)Cp (BTU/lbm-&deg;F)
Tav Tube (OF)K (BTU/hr-ft.&deg;F)
Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (lbm/nhr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')5.325E+5 1.947E+5 7.8E+6 71.9 471.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Shell-Side 4.99 8.292E+04 2.13 0.82 0.87 60.52 1.00 0.39 Tube-Side 4.01 3.273E+04 4.04 1.48 1.27 61.86 1.00 0.37 Overall Fouling (hr-ft 2-&deg;F/BTU)Shell-Side ho (BTU/hr'ft 2 0 iF)Tube-Side hi (BTU/hrft 2 0.IF)I/Wall Resis (BTU/hr ft 2.&deg;F)LMTD Correction Factor U Overall (BTU/hr-ft 2-&deg;F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (&deg;F)Shell Skin Temp (&deg;F)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (&deg;F)Tube Skin Temp (F)0.002782 2,038.2 1,213.3 25,594.8 0.9808 U 0 0 4-0 A4 P4 234.8 190.0 175.4 182.7 174.3 90.0 130.1 110.1 126.2** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:03:05 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)
Commonwealth Edison Calculation Report for DG01A -DG Jacket Water Cooler CSCS = 1O0&deg;F 06/29/98 Calculation Specifications II I. *1 Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (&deg;F)534.5 1,064.5 100.0 190.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr ft 2.&deg;F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2.&deg;F)Tube-Side hi (BTU/hr-ft 2-&deg;F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2-IF)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr. ft 2.&deg;F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ft hr) Shell Skin Temp (IF)Skin Visc (Ibm/ft-hr)
Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (IF)Cp (BTU/lbm-0 F) Tav Tube (&deg;F)K (BTU/hr-ft.&deg;F)
Tube Skin Temp (IF)Extrapolation Calculation Results Shell Mass Flow. (lbm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)Property Shell-Side Velocity (ft/s) 4.99 Reynold's Number 8.292E+04 Prandtl Number 2.13 Bulk Visc (lbm/ft-hr) 0.82 Skin Visc (lbm/ft-hr) 0.87 Density (Ibm/ft 3) 60.52 Cp (BTU/Ibm.&deg;F) 1.00 K (BTU/hr-ft.&deg;F) 0.39 5.325E+5 2.674E+5 7.8E+6 67.8 471.2 Tube-Side 5.52 4.701 E+04 3.85 1.42 1.27 61.79 1.00 0.37 Overall Fouling (hr ft 2-&deg;F/BTU)Shell-Side ho (BTU/hr.ft 2.-F)Tube-Side hi (BTU/hr-ft 2.&deg;F)I/Wall Resis (BTU/hr.ft 2-OF)LMTD Correction Factor U Overall (BTU/hr~ft 2'-F)ttn 0\Shell Temp In (IF)Shell Temp Out (OF) ON Tav Shell (IF) 6 Shell Skin Temp (OF)T Tube Temp In (OF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (OF)0 0.002782 2,038.4 1,592.6 25,594.8 0.9844 0 tN 247.9 190.0 175.4 182.7 174.4 100.0 129.2 114.6 126.8 0 U** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Attachment H to Proto-Power Calculation 97-195 Revision A Proto-Power Calc: 97-195 

==Attachment:==

H Rev: A Page 1 of 2 PROTO-HX T M Version 3.02 MODEL LASALLE STATION STANDBY DIESEL GENERATOR HEAT EXCHANGER.
FILE NAME: DGO1A.PHX DATE LAST MODIFIED:
6/29/98 TIME LAST MODIFIED:
1:50:34 PM FILE SIZE: 640 KB Proto-Power Calc: 97-195 

==Attachment:==

H Rev: A Page 2 of 2 CC-AA-309-1001 Revision 6 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page 1 Design Analysis (Minor Revision)
Last Page No. 'Attachment A, A9 Analysis No.:' 97-199 Revision:
I B03 Title: 3 VY Cooler Thermal Performance Model -1(2)VY03A EClECR No.:' 388666 Revision:'
000 Station(s):
LaSalle Unit No.:' 01 &02 SafetylQA Class:' SR System Code(s):" VY Is this Design Analysis Safeguards Information?" Yes El No Z If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?
12 Yes [] No 0 If yes, ATI/AR#: N/A This Design Analysis SUPERCEDES: 
'1 NIA in its entirety.Description of Changes (list affected pages): 4 This revision evaluates a maximum cooling water inlet temperature of 107 'F. The previous temperature that was evaluated was 104 'F. Affected pages are Pages 1 -2 and Attachment A, Pages A1-A9.Disposition of Changes: " See attached pages. The changes made are acceptable.
Preparer:" -Prnt Nae Is Method of Review: ' Detailed Review [] Alternate Calculations 
[I Testing E]Reviewer:" ___ _ __ __ Cis sL. C/A Print Name Sign Name Date Review Independent review Peer review El Notes: " (For Extemrna Analyses Only)External Approver:
O Prit Nam Sign Name Oata Exelon Reviewer 2 SPrngame Sign Name Dale Exelon Approver: 
/2 L ___________"_
_ 5/-/-7/12-P -I Nam ( Sign Name Date 97-199 Rev. B03 Page 2 of 2 Purpose: The purpose of this revision is to verify that the 1(2)VY03A cooler can remove the design heat load of 722,217 BTU/hr with a revised maximum cooling water temperature of 107 OF.Assumptions:
There are no assumptions for this revision.Inputs:* Cooling water temperature 
= 107 OF (Reference 2)* Air temperature 
= 148 OF (Reference 1)* Water flow rate = 72.5 gpm (Reference 1)* Air Flow rate = 23,760 cfm (Reference 1)* Fouling factor = 0.02650655 hrft 2 e.F/BTU (design fouling factor) (Reference 1)* 1 tube plugged (5% tube plugging) (Reference 1)

==References:==
: 1. Design analysis 97-199, Rev. B, up to and including Revs BOO through B02 2. EC 388666, Rev. 000 Identification of Computer Programs: The computer program used in this analysis is Proto HX version 4.01. This program has been validated per DTSQA tracking number EX0000103.
Method of Analysis / Numeric Analysis: The existing heat exchanger model will be revised by changing the input of the "Tube Inlet Temp" from 104 OF to 107 OF. Because the fan for the 1(2)VY03A cooler is at the exit of the cooler, the inlet air flow for the front cooler A is iterated until the flow rate at the exit of the last row of the cooler is approximately 23,760 cfm. The iteration process is detailed in section 6.7 of revision B. The air flow values can be found on pages A9 for the case that was considered.
Results /

== Conclusions:==

The 1(2)VY03A coolers can remove the design heat load of 722,217 BTU/hr with the following conditions:
* 107 OF cooling water temperature a 148 OF air temperature
* design fouling factor of 0.02650655 hr-ft 2-&deg;F/BTU* 1 tube plugged* air flow rate of 23,760 cfm* water flow rate of 72.5 gpm The total heat removed at these conditions is 757,712 BTU/hr, which provides 4.9% thermal margin over the design heat load. This thermal margin is enough to account for the 4.5% model uncertainty shown in Attachment J and is acceptable.
Note that a maximum fouling factor was not calculated as was done in previous revisions because it is not practical to set up test conditions that would allow accurate measurement of the fouling factor for these heat exchangers.
The bounding fouling factor is the design fouling factor of 0.02650655 hr.ft.F/BTU.
This case is shown in Attachment A.Attachments:
A. Data Report for 1(2)VY03A (9 pgs) 04-26-2012 16:03:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
ComEd -- LaSalle Data Report for 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 -148 TF air side, 23,760 cfmi, 107 'F water side, 72.5 gpm, Design FF, I tube plugged Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Flow 31,066.00 acfm 180.00 gpm Mass Flow 0.00 lbm/hr 0.00 lbm/hr Dry Bulb (Inlet Temperature) 150.00 OF 105.00 OF Inlet Wet Bulb Temperature 92.00 OF Inlet Relative Humidity 0.00 %Dry Bulb (Outlet Temperature) 108.80 OF 117.70 OF Outlet Wet Bulb Temperature 84.00 OF Outlet Relative Humidity 0.00 %Tube Fluid Name Tube-Side Fouling Air-Side Fouling Design Q (BTU/hr)Atmospheric Pressure (psia)Design Sensible Heat Ratio Performance Factor (% Reduction)
Coil Flow Direction Fin Type Configuration (for Air-Side h)Coil Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-PF)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Conductivity (BTU/hr-ft.&deg;F)
Fresh Water 0.001500 0.000000 1,108,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 23.00 0.5270 0.6250 1.400 1.410 97-199 1.000 Rev. B03 225.00 Attachment A Page Al of A9 04-26-2012 16:03:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
ComEd -- LaSalle Calculation Report for I(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 -148 'F air side. 23,760 cfm, 107 'F water side, 72.5 gpm, Design FF, 1 tube plugged Page 1 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure (psia)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (&deg;F)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm)Air Flow (acfm)Tube Inlet Temp (IF)Air Inlet Temp (IF)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (IF)Atmospheric Pressure (psia)72.50 25,109.00 107.00 148.00 12.76 0.00 14.315 97-199 Rev. B03 Attachment A Page A2 of A9* Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 16:03:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 2 CornEd -- LaSalle Calculation Report for 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 -148 'F air side, 23,760 cfm, 107 7F water side, 72.5 gpm, Design FF. I tube plugged Extrapolation Calculation Summary Air-Side Tube-Side Mass Flow (lbm/hr) 92,786.23 35,999.06 Tube-Side hi (BTU/hr-ft 2.&deg;F) 0.00 Inlet Temperature 
(&deg;F) 148.00 107.00 j Factor 0.0000 Outlet Temperature 
(&deg;F) 115.36 128.06 Air-Side ho (BTU/hr-ft 2.&deg;F) 0.00 Inlet Specific Humidity Tube Wall Resistance (hr-fft.&deg;F/BTU) 

==0.0 0029413==
Outlet Specific Humidity Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2) 10,093.49 LMTD 0.00 Total Heat Transferred (BTU/hr) 757,712 Surface Effectiveness (Eta) 0.0000 Sensible Heat Transferred (BTU/hr) 757,712 Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)Extrapolation Calculation for Row l(Dry)Air-Side Mass Flow (!bm/hr) 92,786.23 Inlet Temperature 
(&deg;F) 148.00 Outlet Temperature (IF) 143.27 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (&deg;F) 145.63 Skin Temperature 
(&deg;F) 131.69 Velocity *** 3,921.86 Reynold's Number 874**Prandtl Number 0.7253 Bulk Visc (lbm/ft-hr) 0.0491 Skin Visc (Ibm/ft hr) 0.0000 Density (Ibm/ft 3) 0.0621 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr'ftr.F) 0.0163 Relative Humidity In (%) 12.76 Relative Humidity Out (%) 14.37 Tube-Side 35,999.06 125.01 128.06 126.5327 128.7549 2.3294 17,899 3.4023 1.2676 1.2425 61.6077 0.9989 0.3722 Tube-Side hi (BTU/hr-ft 2.&deg;F) 871.38 j Factor 0.0073 Air-Side ho (BTU/hr ft 2-&deg;F) 8.50 Tube Wall Resistance (hr-ft 2.&deg;F/BTU) 0.00029413 Overall Fouling (hr-fi2.&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hrlft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.74 1,009.35 18.97 109,834 0.9250 109,834** Reynolds Number Outside Range of Equation Applicability 97-199 Rev. B03 Attachment A Page A3 of A9* Air Mass Velocity (Lbm/hrift 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 16:03:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
ComEd -- LaSalle Page 3 Calculation Report for 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 -148 'F air side, 23,760 cfm, 107 'F water side. 72.5 gpm, Design FT, I tube plugged Extrapolation Calculation for Row 2(Dry)Air-Side Tube-Side Mass Flow (Ibm/hr) 92,786.23 35,999.06 Tube-Side hi (BTU/hrft2.&deg;OF) 858.99 Inlet Temperature 
(&deg;F) 143.27 122.22 j Factor 0.0073 Outlet Temperature 
(&deg;F) 138.95 125.01 Air-Side ho (BTU/hrft2.&deg;IF) 8.48 Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2-&deg;F/BTU) 0.00029413 Outlet Specific Humidity 0.020268 Overall Fouling (hr-fl 2.&deg;F/BTU) 0.02650655 Average Temp (OF) 141.11 123.6110 Skin Temperature (IF) 128.35 125.6691 U Overall (BTU/hr.ft 2.&deg;F) 5.72 Velocity *** 3,921.86 2.3276 Effective Area (ft 2) 1,009.35 Reynold's Number 879** 17,428 LMTD 17.38 Prandtl Number 0.7257 3.5030 Total Heat Transferred (BTU/hr) 100,285 Bulk Vise (lbm/ft'hr) 0.0488 1.3019 Skin Vise (lbm/ft-hr) 0.0000 1.2776 Surface Effectiveness (Eta) 0.9252 Density (lbm/ft 3) 0.0625 61.6549 Sensible Heat Transferred (BTU/hr) 100,285 Cp (BTU/Ibm-&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr'ft&deg;F) 0.0162 0.3712 Heat to Condensate (BTU/hr)Relative Humidity In (%) 14.37 Relative Humidity Out (%) 16.05** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)Air-Side Mass Flow (lbm/hr) 92,786.23 Inlet Temperature (IF) 138.95 Outlet Temperature (OF) 135.00 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 136.97 Skin Temperature 
(&deg;F) 125.30 Velocity *** 3,921.86 Reynold's Number 884*, Prandtl Number 0.7261 Bulk Vise (lbm/ft-hr) 0.0486 Skin Vise (lbm/ft-hr) 0.0000 Density (Ibm/ft 3) 0.0629 Cp (BTU/Ibm'&deg;F) 0.2402 K (BTU/hr"ft'&deg;F) 0.0161 Relative Humidity In (%) 16.05 Relative Humidity Out (%) 17.79 Tube-Side 35,999.06 119.67 122.22 120.9425 122.8478 2.3260 17,001 3.5994 1.3346 1.3111 61.6970 0.9988 0.3703 Tube-Side hi (BTU/hr-ft 2-&deg;F) 847.63 j Factor 0.0073 Air-Side ho (BTU/hr.ft 2.&deg;F) 8.46 Tube Wall Resistance (hr-ft 2.&deg;F/BTU) 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.70 1,009.35 15.92 91,613 0.9253 91,613** Reynolds Number Outside Range of Equation Applicability 97-199 Rev. B03 Attachment A Page A4 of A9** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 16:03:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page4 ComEd -- LaSalle Calculation Report for I(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 -148 'F air side, 23,760 cfm, 107 7F water side, 72.5 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 4(Dry)Air-Side Tube-Side Mass Flow (lbm/hr) 92,786.23 35,999.06 Tube-Side hi (BTU/hr ft 2.&deg;F) 837.20 Inlet Temperature (IF) 135.00 117.34 j Factor 0.0072 Outlet Temperature 
(&deg;F) 131.39 119.67 Air-Side ho (BTU/hr ft 2.&deg;F) 8.44 Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2.&deg;F/BTU) 0.00029413 Outlet Specific Humidity 0.020268 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 Average Temp (IF) 133.20 118.5042 Skin Temperature (IF) 122.51 120.2672 U Overall (BTU/hr ft2.&deg;F) 5.68 Velocity *** 3,921.86 2.3246 Effective Area (fW 2) 1,009.35 Reynold's Number 888** 16,614 LMTD 14.59 Prandtl Number 0.7264 3.6913 Total Heat Transferred (BTU/hr) 83,730 Bulk Vise (lbm/ft-hr) 0.0483 1.3656 Skin Vise (lbm/ft-hr) 0.0000 1.3431 Surface Effectiveness (Eta) 0.9254 Density (Ibm/ft 3) 0.0633 61.7347 Sensible Heat Transferred (BTU/hr) 83,730 Cp (BTU/Ibm.&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hrift.&deg;F) 0.0160 0.3695 Heat to Condensate (BTU/hr)Relative Humidity In (%) 17.79 Relative Humidity Out (%) 19.56** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)Air-Side Mass Flow (lbm/hr) 92,786.23 Inlet Temperature (IF) 131.39 Outlet Temperature (IF) 128.09 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 129.74 Skin Temperature (IF) 119.95 Velocity *** 3,921.86 Reynold's Number 892**Prandtl Number 0.7267 Bulk Visc (lbm/ifihr) 0.0481 Skin Visc (Ibm/fi hr) 0.0000 Density (lbm/ft 3) 0.0637 Cp (BTU/lbm.&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0159 Relative Humidity In (%) 19.56 Relative Humidity Out (%) 21.37 Tube-Side 35,999.06 115.21 117.34 116.2751 117.9057 2.3234 16,263 3.7787 1.3951 1.3735 61.7685 0.9988 0.3688 Tube-Side hi (BTU/hr-fl 2 -F) 827.64 j Factor 0.0072 Air-Side ho (BTU/hrftl 2 -F) 8.43 Tube Wall Resistance (hr-ft 2.&deg;F/BTU) 0.00029413 Overall Fouling (hr.ft2-&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hr.ft2.
0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.67 1,009.35 13.38 76,559 0.9256 76,559** Reynolds Number Outside Range of Equation Applicability 97-199 Rev. B03 Attachment A Page A5 of A9 Air Mass Velocity (Lbmlhr.ftz), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 16:03:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 5 ComEd -- LaSalle Calculation Report for I(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 -148 'F air side, 23,760 cfm, 107 'F water side, 72.5 gpm, Design FE, I tube plugged Extrapolation Calculation for Row 6(Dry) _3 Air-Side Tube-Side Mass Flow (ibm/hr) 92,786.23 35,999.06 Tube-Side hi (BTU/hr-ft 2.&deg;F) 818.86 Inlet Temperature (OF) 128.09 113.26 j Factor 0.0072 Outlet Temperature (OF) 125.08 115.21 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.41 Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr f 2 .&deg;F/BTU) 0.00029413 Outlet Specific Humidity 0.020268 Overall Fouling (hr-fti 2.F/BTU) 0.02650655 Average Temp (OF) 126.59 114.2366 Skin Temperature (OF) 117.62 115.7441 U Overall (BTU/hr-ft2.&deg;F) 5.66 Velocity *** 3,921.86 2.3222 Effective Area (ft 2) 1,009.35 Reynold's Number 896** 15,944 LMTD 12.27 Prandtl Number 0.7269 3.8617 Total Heat Transferred (BTU/hr) 70,031 Bulk Visc (lbm/ft-hr) 0.0479 1.4230 Skin Visc (lbm/ft-hr) 0.0000 1.4023 Surface Effectiveness (Eta) 0.9257 Density (lbm/ft 3) 0.0640 61.7988 Sensible Heat Transferred (BTU/hr) 70,031 Cp (BTU/lbm.&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hrfi.t&deg;F) 0.0158 0.3681 Heat to Condensate (BTU/hr)Relative Humidity In (%) 21.37 Relative Humidity Out (%) 23.18** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)Air-Side Mass Flow (lbm/hr) 92,786.23 Inlet Temperature (OF) 125.08 Outlet Temperature (OF) 122.32 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (OF) 123.70 Skin Temperature (OF) 115.48 Velocity *** 3,921.86 Reynold's Number 899*4 Prandtl Number 0.7272 Bulk Visc (Ibm/f hr) 0.0477 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0643 Cp (BTU/lbm.&deg;F) 0.2402 K (BTU/hr-ff-&deg;F) 0.0158 Relative Humidity In (%) 23.18 Relative Humidity Out (%) 25.01 Tube-Side 35,999.06 111.48 113.26 112.3716 113.7647 2.3212 15,655 3.9402 1.4493 1.4296 61.8261 0.9988 0.3674 Tube-Side hi (BTU/hr-fl 2 l-F) 810.81 j Factor 0.0072 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.40 Tube Wall Resistance (hr-ft2-&deg;F/BTU) 

==0.0 0029413==
Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.64 1,009.35 11.25 64,083 0.9258 64,083** Reynolds Number Outside Range of Equation Applicability 97-199 Rev. B03 Attachment A Page A6 of A9* Air Mass Velocity (Lbm/hrft 2), Tube Fluid Velocity (fi/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 16:03:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 6 ComEd -- LaSalle Calculation Report for l(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 -148 'F air side, 23,760 cfm, 107 'F water side, 72.5 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 8(Dry)Air-Side Tube-Side Mass Flow (Ibm/hr) 92,786.23 35,999.06 Tube-Side hi (BTU/hr'ft2-0 F) 803.42 Inlet Temperature (IF) 122.32 109.85 j Factor 0.0072 Outlet Temperature (IF) 119.79 111.48 Air-Side ho (BTU/hr ft 2 -F) 8.39 Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2.&deg;F/BTU) 0.00029413 Outlet Specific Humidity 0.020268 Overall Fouling (hr-ft 2.0 F/BTU) 0.02650655 Average Temp (IF) 121.05 110.6647 Skin Temperature (IF) 113.52 111.9516 U Overall (BTU/hr-fl2.&deg;F) 5.63 Velocity *** 3,921.86 2.3203 Effective Area (ft') 1,009.35 Reynold's Number 902** 15,391 LMTD 10.32 Prandtl Number 0.7273 4.0144 Total Heat Transferred (BTU/hr) 58,661 Bulk Visc (lbm/f-fhr) 0.0476 1.4742 Skin Visc (lbm/ftfhr) 0.0000 1.4554 Surface Effectiveness (Eta) 0.9259 Density (Ibm/ft 3) 0.0646 61.8506 Sensible Heat Transferred (BTU/hr) 58,661 Cp (BTU/lbm'&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr'ftf'F) 0.0157 0.3668 Heat to Condensate (BTU/hr)Relative Humidity In (%) 25.01 Relative Humidity Out (%) 26.82** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 9(Dry)Air-Side Mass Flow (lbm/hr) 92,786.23 Inlet Temperature (OF) 119.79 Outlet Temperature (IF) 117.48 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (OF) 118.63 Skin Temperature (OF) 111.73 Velocity *** 3,921.86 Reynold's Number 905**Prandtl Number 0.7275 Bulk Visc (Ibm/ft hr) 0.0474 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0648 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0157 Relative Humidity In (%) 26.82 Relative Humidity Out (%) 28.61 Tube-Side 35,999.06 108.36 109.85 109.1020 110.2904 2.3194 15,151 4.0844 1.4975 1.4797 61.8727 0.9988 0.3662 Tube-Side hi (BTU/hr-ft 2-&deg;F) 796.64 j Factor 0.0072 Air-Side ho (BTU/hr'ft 2.&deg;F) 8.38 Tube Wall Resistance (hr-ft 2.&deg;F/BTU) 0.00029413 Overall Fouling (hr-ft2-*F/BTU) 

==0.0 2650655==
U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.62 1,009.35 9.47 53,715 0.9260 53,715** Reynolds Number Outside Range of Equation Applicability 97-199 Rev. B03 Attachment A Page A7 of A9 Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T. Other Properties at Average T 04-26-2012 16:03:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 7 ComEd -- LaSalle Calculation Report for 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 -148 *F air side, 23,760 cfm, 107 'F water side, 72.5 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 10(Dry)Air-Side Mass Flow (lbm/hr) 92,786.23 Inlet Temperature (0 F) 117.48 Outlet Temperature (0 F) 115.36 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (&deg;F) 116.42 Skin Temperature (0 F) 110.08 Velocity *** 3,921.86 Reynold's Number 908**Prandtl Number 0.7276 Bulk Visc (Ibm/if hr) 0.0473 Skin Visc (lbm/ftfhr) 0.0000 Density (lbm/ft 3) 0.0651 Cp (BTU/Ibm-0 F) 0.2402 K (BTU/hr-ft.
0 F) 0.0156 Relative Humidity In (%) 28.61 Relative Humidity Out (%) 30.37 Tube-Side 35,999.06 106.99 108.36 107.6708 108.7679 2.3187 14,933 4.1502 1.5194 1.5026 61.8926 0.9988 0.3657 Tube-Side hi (BTU/hr-ft 2.0 F) 790.41 j Factor 0.0072 Air-Side ho (BTU/hr-ft2-0 F) 8.37 Tube Wall Resistance (hrifl2-0 F/BTU) 0.00029413 Overall Fouling (hr ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hrift 2.&deg;F)Effective Area (Wf 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.61 1,009.35 8.69 49,200 0.9260 49,200** Reynolds Number Outside Range of Equation Applicability 97-199 Rev. B03 Attachment A Page A8 of A9* Air Mass Velocity (Lbm/hr-fi 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Formulas from Section 6.7 for iteration process to determine inlet airflow for extrapolation conditions Total P: T P = 1 14.3151psia Dry Bulb T OUT: T1 = 115.36 F Specific Hum.: W = 0.0203p H20 Vap. P: Pv = (W*Rv*P)/(Ra+(W*Rv)) 
= 0.452444 psia_ jRv = 85.778 (ft-lbf)/(Ibm-R)
_Ra = 53.352 (ft-lbf)/(Ibm-R)
I Dry Air P: Pa = P -Pv = 1 13.86256 psia Dry Air rho OUT: rho.out = (144/Ra)*(Pa/(459.67+T1)) 
= _ 0.065068 Ibm/ftA3 Dry Air rho IN: rho.in = (144IRa)*(PaI(459.67+T2)) 
= 0.061573 Ibm/ft 3 Dry Bulb T IN: T2 = 148 F Outlet Air Flow: V = 23760 cfm cfm.in cfm.in = V*(rho.out/rho.in) 
= 25108.67 acfm 97-199 Rev. B03 Attachment A Page A9 of A9 CC-AA-309-1001 Revision 4 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Design Analysis (Minor Revision) 
[ Last Page No. 6 Attachment A page 7 Analysis No.: 97-199 Revision:
B02 Title: 3 VY Cooler Thermal Performance Model -1(2)VY03A EC/ECR No.: EC 368604 Revision:
0 Station(s):'
LaSalle Unit No.: 8 00 Safety/QA Class: 8 Safety Related System Code(s): ,0 VY Is this Design Analysis Safeguards Information? " Yes M No s If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?" Yes 1] No s If yes, ATI/AR#: This Design Analysis SUPERCEDES: 
"3 N/A in its entirety.Description of Changes (list affected pages): 4 The following pages fromRev. A this calculation are affected by this minor revision:
2, 16, 22, 23 and 24 as well as Attachment A pages 2, 3, 4, 6 and 7. This minor revision incorporates the changes that were identified in IR 641522 as a result of the Key Calculation review effort. ax, o.s r- ot- -w- o Iev.(The following changes were made: 1. Ref. 4 UFSAR Table 3.11-8 was replaced with Calculation L-00251 1.2. References 5 and 6 were revised to indicate that they are uncontrolled and that the current UFSAR should be referenced to find current values. Subsequent revisions to calculation 97-199 have incorporated these changes to the UFSAR.3. The references were corrected/revised as necessary to make them current.Disposition of Changes: 15 These changes are enhancements suggested as a result of a Key Calculation review. None of these changes adversely affect the ability of the 1(2)VY03A room coolers to perform their design function.See Attached Pages for details Preparer:
16 Debbie Henley-
* ri 12/12/07 Pint Name Name  Method of Review: '" Detailed Review IS Alternate Calculations (lbsting 0 Reviewer:
Is Cc &#xfd;s \_\_IA,__________"__
i I /,0o7 Pnnt Name Sign Name Date Review Independent review E] Peer review El Notes: " (For External Analyses Only)External Approver:
0 Print Name Sign Name Date Exelon Reviewer 1'PrintName S n / N~ame Date Exelon Approver:
11 C 6-- ...Print Name Vt Slign Name Date PROTO-POWER CORPORATION CALC NO.97199 REV JPAGE 2 O 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED DY M. Aboye j10"0 o 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I(2)VY03A 3. DESIGN INPUTS The thermal performance model is developed using PROTO-HX T M , Version 3.01. PROTO-HXTM was developed and validated in accordance with Proto-Power's Nuclear Software Quality Assurance Program (SQAP). This program meets the requirements of IOCFR50 Appendix B, I OCFR2 1, and ANSI NQA- 1, and was developed in accordance with the guidelines and standards contained in ANSII[EEE Standard 730/1984 and ANSI NQA-2b-1991.
PROTO-HXTM Version 3.01 was verified and approved for use as documented in Reference (1).The design inputs for this calculation consist of the heat exchanger design basis performance requirements (Table 1), performance specifications (Table 2) and construction details (Table 3)provided by the heat exchanger manufacturer data sheet (Attachment A) or other design documents as referenced.
Construction details give the necessary information for model construction while performance specifications are used to benchmark the model.VY cooler thermal performance in this calculation will be assessed only with respect to the nominal accident conditions (i.e., design basis LOCA) with no tubes plugged. Condensing modes of operation and tube plugging margins are not addressed.
I Table 1: LaSalle Station Reference Conditions Parameter Value HIeat Rate -- I(2)VY013A (BTU/hr) 722,217 Atmospheric Pressure (in-w.g.) 
-0.4 {" , Air-Side Inlet Temperature 
-- Dry Bulb (0 F) 148 Fan Volumetric Flow Rate (cfm) 26,400 Tube-Side Flow Rate (gpm) 180 , Tube-Side Inlet Temperature (0 F) 100 *1(0*Selected references included as Attachment A LL3c L -Y ~ Y -'. Ti- 'IC 'Ik\C c~;~S 4 -6 \'e.f fT4~\ ~ $.f~~icovc,~c c.KCN /A."(r~Xc.~
v~QtfA ~ ~ 1?
Calculation 97-199 Revision B02 Page 2a of 24 Insert A: The basis for the -0.4 in.-w.g. atmospheric pressure in Table I in Rev. AO was Ref. 4 UFSAR Table 3.11-8, provided in Attach. A. This value is used in determining the coil pressure value to be used in the Proto-HX thermal model. The -0.4 in. w.g. in this UFSAR table has subsequently been revised and is now 0 in. w.g. Nevertheless, as discussed on pgs. 9 and 12 of Calculation L-002511 Rev. 0, and as verified in Passport D071 panel for reactor building (RB) HVAC differential pressure controllers 1(2)PDC-VR007, the nominal value is still -0.4 in. w.g. Under abnormal conditions, the reactor building is maintained at least -0.25 in. w.g. by the Standby Gas Treatment System (VG), however there is a short period of time before VG starts during which RB pressure may approach 0 in. w.g. If both VG trains are operating, the pressure could reach a minimum of -0.69 in. w.g. until one train is secured. Recent surveillance test data (WO #727706 for Secondary Containment Leak Rate Test LTS-300-3) indicates with one train of VG in operation for at least 5 minutes, the refuel floor RB pressure averaged approx. -0.4 to -0.5 in. w.g.) In conclusion, the -0.4 in. w.g. pressure is still a reasonable value to use in conjunction with Proto-HX thermal performance evaluations.
Slight variations, e.g. a difference of 0.4 -0.25 = 0.15 in. w.g., equates to a pressure difference of 0.005 psig (see bottom of pg. 14/24 of Calculation.97-199 Rev. A).For purposes of comparison, the Proto-Power Corp. (preparer/approver of Rev. A of the calculation) was contacted and the LaSalle Proto-HX model for 1(2)VY03A was run for two cases. Both cases used the same input parameters and extrapolation conditions, with the exception of the atmospheric pressure extrapolation condition.
One case used an atmospheric pressure of 14.329 psig corresponding to 0.0 in. w.g. differential pressure in the cooler room, and one with 14.315 psig corresponding to the -0.4 in. w.g. differential room pressure.
As expected based on discussions with the DEM HVAC engineer, these runs demonstrated that the calculated heat removal rate was essentially unchanged (calculated was actually slightly higher at the higher room pressure, however the difference was insignificant (0.1% higher)).
Given the available heat transfer margin, small differences in ambient room pressure are therefore considered insignificant.
Per Revision B02, Reference 4 has been changed to calculation L-002511 Rev. OA to provide the basis for the -0.4 in, w.g.
A309, PROTO-POWER CORPORATION CALCNO. 97199 REV PAGE 16 O 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERUFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A The iteration process described above was completed twice for this model for a clean (f= 0.0)and service (f = design) condition with results as follows: Clean: (cfmj") -(Po,,)x (pin)(0.066345159)
(26,400) x = 28,445 (Fan Temperature 
= 104.31)(0.06 1575 103)Service: (cfmi.) = (cfmon,) x (pin)(0.066128241)
(26,400) x = 28,352(FanTemperature 
= 106.16)(0.061575103)
Summary of PROTO-HXTM Inputs for Extrapolation to Reference Conditions The Extrapolation conditions are defined as the vendor data sheet conditions without high energy line break modified for ultimate heat sink temperature and room limiting temperature per 4te Laall, Station UFS.AR Reference (4)) ocxd (6)The required PROTO-HXTM inputs for these conditions are as follows: 'oa.Tube-Side Flow Rate Tube-Side Inlet Temperature Air-Side Flow Rate Air-Side Inlet Temperature 
-- Dry Bulb Air-Side Inlet Humidity Atmospheric Pressure 180 gpm f 1OL --0&deg;F (varies with temperature) 148 0 F 12.76%14.315 psia 6.8 Thermal Margin Assessment The available thermal margin is defined as the difference between the available and the required heat removal rates at reference conditions.
The maximum available heat removal rate is calculated using the benchmarked PROTO-HXTM model and the inlet conditions defined in Section 6.7 with zero fouling. By comparing the available heat removal rate calculated with zero fouling (qciann) to the required heat removal rate, the maximum available margin is determined.
A similar comparison is made between the required heat load to the available heat load at design fouling conditions (qserice).-in c.o3c.
n..s)'&c)-Otbe_
t k fo-vt 4 7 c&#xfd;&#xfd;,5&#xfd;em i6 PROTO-POWER CORPORATION CALC NO 97199 PAGE22OF24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye oB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A Table 12: Fouling Sensitivity Analysis -1(2)VY03A at 72.5 gpm Air-Sidef Tube-Sidef Required q Available q %Margin 0.0020 0.0000 722,217 1,002,563 38.82%0.0020 0.0010 722,217 969,164 34.19%0.0020 0.0020 722,217 938,124 29.90%0.0020 0.0030 722,217 907,127 25.60%0.0020 0.0040 722,217 879,956 21.84%8. CONCLUSIONS A model for the LaSalle County Station Units 1 & 2 SE Cubicle Area Coolers was developed using PROTO-HX T M Version 3.01. The model was benchmarked and validated using the performance specifications provided by the cooler vendor. The close correlation with vendor specified and model predicted thermal performance confirms that the models are to be considered acceptable for use in the GL 89-13 heat exchanger testing program and related performance analyses.The available thermal margin for the coolers has been defined for the nameplate rated flow of 180 gpm and for a reduced flow rate of 72.5 gpm in support of service water system re-balancing efforts. Inclusion of a conservative assessment of the uncertainty in the analytical methods of PROTO-HXTM has provided high confidence in the thermal margins defined by the model for all cases.The model database is saved under file name vy-03a.phx, with a file size of 1,277,952 bytes, and a file date and time of 7/6/98 at 6:21:52 pm. The saved database is set up to run the 72.5 gpm case with adjusted design fouling factors of 0.002 air-side and 0.002 tube-side.
The database file is included as Attachment N.9. REFERENCES
: 1. Heat Exchanger Thermal Performance Modeling Software Program PROTO-HXTM Version 3.01 Software Validation and Verification Report (SVVR) SQA No. SVVR-93948-02, Revision E, dated 11/5/97 2. LaSalle Calculation L-001077, Revision/
RHR Pump A Cubicle Cooler Ventilation iB g System PROTO-POWER CORPORATION CALC NO. 97-199 REV PAGE 23 OF 24 I GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO, 31-003 CLIENT Commonwealth Edison PROiEcr LaSalle Station GL 89-13 Heat Exchanger Testing TILE VY Cooler Thermal Performance Model -- 1(2)VY03A 3. Procedure LTS-200-19, Revision 4, performed on cooler IVY03A on 6/12/98 4. L~aSalle Statien iUpdatze Fina! Safcfty htysis Report, Trable 3.11 8, Hlar~h Ernvirerdnefti Zone 146 Bounding Enviromet.
al C"ndition_
_ "___ the EeCs eabichl-, (Aittaluh~1 B*A4 ~~ ~- 'or) L.- Ooaitm 3e_\3oC(OA, 10JPfn).&#xfd;rt 0Y PKM~5. LaSalle Station Updated Final Safety Analysis Report, Section 9.2.1, ECCS Equipment Cooling Water System (excerpt -Attachment A)- t'713 5 h;3- 5hcb.e. bQ,.Q.C)6. LaSalle Station Updated Final Safety Analysis Report, Section 9.2.6, Ultimate Heat Sink (excerpt -Attachment A) b "5 -. Zv, ,,(&#xfd;.-7. Drawing Number 28SW4045X3, "CSCS Equipment Area Cooling Coils," original issue, 7/21/76 (Attachment A) 5 8. LaSalle Calculation L-000581, Revision 0, Evaluation of the CSCS Cubicle Area Coolers Operation with a Reduced Cooling Water Inlet Temperature
: 9. Piping and lpstrumentation Drawing M-87, Sheet 3, "CSCS Equipment Cooling Water System," Revision-F datedSI4Q'8 K Ci-_ced 3iCVOG 10. Piping and Instrumentation Drawing M-134, Sheet 3, "CSCS Equipment Cooling Water t System," Revision F dated S5 L.. -Q-.. a/1 ,5/04 11. RAhnv~qn Dr.wno20 131213, & 14 (AfttahcnA Vedoc dm)inytOQ--i w4e;t C3 cvJ t3B..- a..)_ 12. Standays of the Tubular Exchanger Manufacturers Assocition (TEMA), Seventh Edition, 1988 13. Specification Number J-2582, Heat Exchange Coils and Cabinets, La Salle County -Units 1 and 2, Revision 1, dated 1/16/75 (excerpt -Attachment A) -(.QAc',t,_
A",_) i a0 14. Proto-Power Calculation 96-069, Revision -, Fluid Properties 
-Moist Air -Range 8' to 300&deg;F 15. Compact Heat Exchangers, W.M. Kays and A.L. London, McGraw Hill, Third Edition, 1984. (excerpt -Attachment C)
PROTO-POWER CORPORATION CALC NO. 97-199 REV PAGE 24 OF 24 r//iAL-GROTON, CONNECTICUT ORIGINArOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROIECF LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A I B 16. 1997 ASHRAE Handbook -- Fundamentals, inch pound Edition, American Society of Heating, Refrigerating and Air Conditioning Engineers, Inc., Atlanta, GA (excerpt -Attachment A)17. Drawing M-1366, Sheet 1, "Reactor Building Ventilation System -- Elevation 694'-6" East," Revision H dated 4/29/83 Doi&#xfd;.eni -f/Y5/0O00
: 18. Drawing M-1464, "CSCS Equipment Cooling System," Revision B dated .3/l2ft 19. Drawing M-1465, "CSCS Equipment Cooling System," Revision 1(-dated SA 20. Coil Walkdown Data, ComEd NDIT No. LS-0847 dated 7/6/98 (Attachment L)
I1-W4ert.VCt.
LSCS-UFSAR TA.BLE 3. 1 17R9 rMTRflWfl4DT ZOHE Hi6/I.1-8 /RflrNflTHC~
EN'J T RONME~4 AL&#xfd; -.1 CONDTIOS ISID2E TEX ECCS CtUBICLES,/(EECLUDINg LECSlRLILL1J 4S.L&I IRE AH& ALAI." 2U UM AA!The maximum cubicl'k temperature is i148&deg;F, 90% reliave humidity and at atmospheric pressure\for the duration of 100 day&#xfd;. .The total number of hours the cubicle is at 148f will be -22,110 hours (7921 days). The o100 days accident conditions are included.
I Radiation:
1 x l O1ads gamma (inegrated)
Pressure: 
-0.4 inch./~ NO~E~RevX q ;/I C CA t -1(9e.i t --O-q vt, i. 3  A,.-, _i  NOTE: Tie bounding radiation-dose I (normal service radiation dose.ntegrated over 40 years + accident does + 10% margin on the accident d dose per IEEE 323-1974, Section 6.3.2.5)./ Proto-Power Calc: 91 

==Attachment:==

A Re'v: t" Paue 2 T- 199 of I1 PR*B-k99" TABLE 3.*11-8 130;'- ROY. 6 -A LSCS-UFSAR
: 4. RHR pump seal cooler ('A' and 'B' RHR pumps only) -20 gpm 5. LPCS pump motor cooling coil -4 gpm 6. northwest cubicle area cooling coil -m15 gpm 7. southwest cubicle area cooling coil -150 gpm S. northeast cubicle area cooling coil -200 gpm 9. southeast cubicle area cooling coil -180 gpm 10. emergency makeup to fuel pool -50 gpm minimum 11. containment flood -.300 gpm maximum.b. System classifications are as shown in Section 3.2. All portions of this system are protected from the effects of tornados, missiles, pipe whip, and flooding.c. To -mt single failure criteria, the CSCS-ECWS for each unit is designed as three independent subsystems, one of which is shared t .. ibetween units (Drawing Non. M-87 and M-134).USVF d. Strainers are provided to prevent plugging of cooled component heat transfer passages.
All strainers include provisions for rLi' backwashing without significantly affecting system operation.
;, 2; Organic fouling of heat transfer surfaces will be minimized by the i'-'
feed system which will treat the service water tunnel; flow-with oxidizing biocides.
However, the chemical feed' ..system should not be considered auxiliary equipment required for~ the CSCS-ECW systems to perform their function.
Therefore, the I operability of the-CSCS-ECW systems should not be tied to the operability-of the chemical f eed system. connections and isolation valves are also provided immediately upstream and downstream of each cooled component for injection and circulation of biocidal agents, if necessary.
: e. To detect leakage of radioactivity to the environment, radiation monitors are installed in the CSCS-ECWS immediately downstream of cooled components that contain radioactive fluids. The CSCS-ECWS discharge lines from these components are capable of remote manual isolation from the main control room.f. Design of system piping and components is based on a 40-year life.Exterior surfaces of all buried system piping is protected by bituminous coatings and wrappings and provisions for cathodic protection are installed where such protection is found to be required based on electrical potential measurements.
The design of all system piping includes a corrosion allowance of at least 0.08 inches.Proto-Power Caic: 97-199 

==Attachment:==

A 9.2-2 Rev:/AX Page 3 of 11 9.2-, 10 -I LSCS-UFSAR the normally closed portions the integrity and operability are checked.9.2.6 Ultimate Heat Sink The ultimate heat sink (UHS) provides sufficient cooling water to permit the safe shutdown and cooldown of the station for 30 days with no makeup for both normal and accident conditions.
9.2.6.1 Design Bases 9.2.6.1.1 Safety Design Bases The ultimate heat sink has the following design bases: a. to provide sufficient water volume permitting a safe shutdown and cooldown of the station for 30 days with no water makeup for both normal operating andaccident conditions 
-mLhe.,aximum permissible water temperature supplied to the plant is taken as 1000 F;b. to withstand the most severe postulated natural-phenomenon as discussed in Chapter 2.0;c. to withstand the postulated site-related incidents as riri in Subsection 2.5.5; and~ ~d. to provide water for fire protection equipment.
lI more detailed physical description of the ultimate heat sink is j W10 provided in Sections 2.4 and 2.5.-9.2.6.1.2 Power Generation Design Bases The ultimate heat sink, as a safety system, is not used during normal plant operations.
Therefore, the ultimate heat sink hasfl'&#xb6;no power generation bases.t.-. 9.2.6.2 System Description In the unlikely event that the main dike is breached, the cooling= for the La Salle County Station is designed to hold 460 acre-feet of water with a surface area of 83 acres. This;Weremaining water constitutes the ultimate heat sink for the station, and has a depth of approximately 5 feet and a top water elevation established at 690 feet. Figures 2.4-4 and 9.2-1 illustrate the physical layout and area capacity of the ultimate heat sink.9.2.6.3 Safety Evaluation The station's ultimate water requirements (Units I and 2) in gpm are summarized below.Proto-Power Cal: 97-199~J~i1-.: Tv~, -. ~-W~~jP5\K 25 Attachxet A-)-' 1 Rev: 4 of 11.. .), c 0~ ~ ~~Curo~'.-1 
-POL. 0A A~lL ( K( I, LLAUIX- 7.4-) 
-I~ K---~I I i I.f~Iv?I DRAIN CONN~ECTION A-4--000floZ1 xl2-W40 40 AN toy 40&#xfd;1 PCPIiMETEA 0F UNIT-'i 3/BASE ST EEL 7 k.NGE.ALL 4 SIDES.-IVC -32'WET PEAI -A.U NOGONTROLLS 
, CHOR DOLTSSA VFVs* ~ ~ L mt Mk. .: IIWIW^2 Isr Bo i su o f it.: Ist -in,~a 351 35. L Acau cols Ivic. b,. FACm argn 0. I-OAKl-1flu.
: 6. UMM Wit 14 I III on. n i 8M t F S~lu (IM11tol ljo t Tom~w nsuu. ~ "MMa$2 3' ~~~SEEVC.
Dwt2SiL! rOft h1IjL SPE~CS ?SHLOP~IvG WEGJ.T 71545" OPCRATIN4 wlaOG4T 79M1 I CUT MA140 UNI T i orD80( W. O0A00YE orj ALL 0d(IrnStOS*~
I~O ATO tOft FIEILD~SCALE ABAAkXALI Ay UACQAJ 10T1 aocerncopyk10b1 loy.-p PAI4..Proto-PowertCuWh:91-1-99'

==Attachment:==

A Rev: X Page 6 of 11 r, "~. ...LUMPL A~t LVlL (.AfIfiL I I J k -,...-*.-* -A lp .6'. .REECE. 0 la rmu asil K11aj ?11 CONN n.111101 FIM. I*M*T v ate MD un IN alt" rM Awl iS Wi-P o' .2n IN iU4 vwsals &#xa3;meuow. fulm MA ..*-M~us.I-12. Aj SAE 04..5.1'-- 40I~*ANCHOR DOLTS PERIMETECA Of UNI~T.1 2 O~s an 1 .Mr W~ M sl6 IIIIIIN Mt U49. ns. IAOM WON II.1. ~ a C PLI 1 Ois CP. IN. rINN am a. *q-WlNiM.ALupo ew I vxU wit to t Lmu inc. IN. ,imu emn v.I-G JS .--L &#xa3;szhs am MCI. 4. MmNI MIA 111 m..us-u.C1.1tin (flU 1%s iiIi OR 0 ad (1111M Ill" l.Wl.3191 gNisI mu re.fl it. muma. sum4 qss -i n. urnst Mt(. 6 a bi. I1ms M4P. "-nw I g 1. 0111111 OHL NOW "a CM1C N 16 "M un ""a IIN tt ..112. 241Ma.1.SEE OV6. 260540. FOR uKri. SPEC'S SHI*PING WEQIGT 7545'MEWAAING WEIGHT? 7965'.7.o LEFT HAND tm'T ALL DOW0S42011221 Proto-Power Calc: 97-199 

==Attachment:==

A Rev:)X Page 7 of 11 a 0N.1LLvATIQef
* ..PS... I. ... t CC-AA-309 
-ATTACHMENT 1 -Design Analysis Approval Page 1 of 2 DESIGN ANALYSIS NO.: Calc. #97-199 PAGE NO. I Major REV Number: B Minor Rev Number: 01 S ] BRAIDWOOD STATION[ ] BYRON STATION DESCRIPTION CODE:(c0i)
MI0[ ] CLINTON STATION[ ] DRESDEN STATION D[X ] LASALLE CO. STATION DISCIPLINE CODE: (col) M[ ] QUAD CITIES STATION Unit:[ ]0 [X]l [X]2 [ ]3 SYSTEM CODE: (C011) VY TITLE: VY COOLER THERMAL PERFORMANCE MODEL -1(2)VY03A[X ] Safety Related [ ] Augmented Quality [ ] Non-Safety Related ATTRIBUTES (CO16)TYPE VALUE TYPE VALUE Elevation 694'Software PROTO-HX COMPONENT EPN: (C014 Panel) DOCUMENT NUMBERS: (C012 Panel) (Design Analyses References)
EPN TYPE TypelSub Document Number Input (YIN)IVY03A H15 DCD/ EC#337494 Y EVAL 2VY03A H15 /REMARKS:
CC-AA-309 
-ATTACHMENT I -Design Analysis Approval Page 2 of 2 DESIGN ANALYSIS NO. 97-199 REV: B01 PAGE NO. 2 Revision Summary (including EC's incorporated):
evaluated issues associated with 1) the impact of an error flag" message on the printouts of Proto-Hx.
which states that the Air Side Reynolds number is outside the range of equation applicability. 
: 2) the "Data Report" output for the air coolers indicates a LOG (base 10) in the Fin Configuration equation for the Colbum 'j' factor, however the equation in the body of this calculation shows this as the natural log (Ln). The calc. has been evaluated to be acceptable as-is.Electronic Calculation Data Files: Proto-Hx (This data is same as previous minor revision:
no computer runs were performed for this minor revision)(Program Name, Version. File Name extensioni/size/datethour/min)
Design Impact review completed? 
[ ] Yes [x ] N/A, Per ECU:_337494 (If yes, attach impact review sheet)Prepared by: __B._L. Davenport______/
J, IA --Print Sign D te Reviewed by: _D. J. Schmit_ _
_ad__,_Method of Review: [ Detailed []Alternate 
[]Test This Design Analysis supersedes:
NIA In Its entire.External Design Analysis Revie (Attachment 3 Attached)Reviewed by: _evie__ SpcilReiew 
/-Prit Sin oat *Approved by: __ !_-A Print Sign Oate Do any ASSUMPTIONS 
/ ENGINEERING JUDGEMENTS require later verification? 
[ 1 Yes [X I No Tracked By: AT#. EC# etc.)
Calculation No. 97-199, Rev. B301 Page3 of_4-Purpose/Objective The purpose of this minor revision is to assess the following: 
: 1) the impact of error"flag" message on the printouts of Proto-Hx, which states that the Air Side Reynolds number is outside the range of equation applicability.
An example of this flag can be found on Attachment G, page 4. 2) the "Data Report" output for the air coolers (example Attachment G, page 2) indicates a LOG (base 10) in the Fin Configuration equation for the Colburn 'j' factor, however Equation 9 of this calculation shows this as the natural log (Ln).Methodology and Acceptance Criteria N/A, this is an assessment of the current calculation.
Assumptions I Engineering Judgments Assumptions and engineering judgements are documented within this analysis.Design Inputs N/A, this minor revision utilizes those of the current calculation.
References
: 1. SEAG 02-000086 (copy attached)2. Heat Transfer-Professional Version, Lindon C. Thomas, 2 nd Ed., 1999.Analysis 1) On page 13, the Colburn 'j' factor versus Reynolds Number (Re) relationship is given.This relationship was derived in this calculation to more closely match the manufacturer's heat transfer capability.
The Colburn 'j' factor relationship is based on the information in Attachment D. This attachment shows the straight line relationship between the 'j' factor and Re number when plotted on a log-log scale, with Re number end points between 1000 and 8000. This relationship was used to derive Equation 9, which is input into the computer model with the two end points. Even though the calculated Re is less than 1000 in some cases (it is normally in the range of approx. 800 to 1000), the program still uses the Equation 9 relationship with the actual Re. The computer program in this case is flagging that it had to extrapolate past the 1000 end point it was given. Reference 2, page 553 shows this relationship to be linear down to a Re of 600 for a similar type of finned tube. Based on engineering judgement, it is therefore reasonable to extrapolate this line to a somewhat lower Re down to a Reynolds number of approximately 800. Thus the results of the calculations are acceptable.
: 2) Equation 9 in the body of the calculation, which indicates Ln, is correct and Ln is the function being used by the program. A check of the j' factor numbers indicated on the computer output in the calculation show that the program is using the natural log Ln.The program manufacturer, Proto-Power, was contacted on 4-03-02. They indicated that the LOG on the Data Report represents indefinite text output and they confirmed Calculation No. 97-199, Rev. BOI Page 4 of 4-that the program is indeed using the natural log (Ln) function for its calculations. (A letter/fax was obtained from Proto-Power on 4-03-02 confirming this discussion.
The fax has been assigned file number SEAG 02-000086).
A copy of this letter is attached (see Attachment A of this minor revision.Summary and Conclusions Based on the above discussion, the calculation results are acceptable as-is.
Apr--03-02 08:55 P-01 Ae~M~fifd7 4 i PROTO-POWER CORPORATION Po A Utility Engineering Stihd.Wdlry
/4 &#xfd;'f'o i e-Al 15 THAMUS STRrrr (W)HONc, (;I O0L3S0 P~H: BriO.440.979'5 I-X: 800.440.8292 www.pm~topowor.com SEAG Number MEMORANDUM File No. 908SOF/050119/M02001 To: Brian Davenport Date: April 3,2002 

==Subject:==
PROTO-HX Air Coil Module Brian, The PROTO-1IX Data Sheet Output Report for Air Coils shows the equation for"Configuration (for Air-Side h)" with the "LOG" term in the equation.
This in fact represents the "Natural Log" and not "Log Base 10." The equation actually uses the Natural Log (LN) term, however, the output report is ambiguous in printing "LOG".If you have any other questions.
please feel free to give me a call.Sorry for the confusion.
JGF:baj CC: Joseph G. Fayan Job File LASALLE CALCULATION EDITORIAL 
-COMMENT TO CALCULATION A\~;'N When these comments are incorporated.
return this fubrm wi Incorporated on Calc Rev. -1l:
CC-AA-309 
-ATTACHMENT I -Design Analysis Approval Page l of 2 DESIGN ANALYSIS NO.: Calc. # 97-199 PAGE NO. I Major REV Number: B Minor Rev Number: 00 I I BRAIDWOOD STATION[ BYRON STATION DESCRIPTION CODE:(coig)
M 0 CLINTON STATION[ ] DRESDEN STATION[X] LASALLE CO. STATION DISCIPLINE CODE: (co0i) M[ I QUAD CITIES STATION Unit:[ 10 [X]l [X]2 [ ]3 SYSTEM CODE: (C011) VY TITLE: VY Cooler Thermal Performance Model -1(2)VY03A[X ] Safety Related [ ] Augmented Quality [ ] Non-Safety Related ATTRIBUTES (C016)TYPE VALUE TYPE VALUE Elevation 694'Software PROTO-HX COMPONENT EPN: (C014 Panel) DOCUMENT NUMBERS: (C012 Panel) (Design Analyses References)
EPN TYPE Type/Sub Document Number Input (YIN)IVY03A H15 EC/DCP EC# 334017 Y 2VY03A H15 //I//REMARKS: NA E-Form CC-AA-309-1 v1.1 for use with CC-AA-309 Revision 1 and above.
CC-AA-309 
-ATTACHMENT I -Design Analysis Approval Paqe 2 of 2 I DESIGN ANALYSIS NO. 97-199 REV: BOO PAGE NO. 2 Revision Summary (including EC's incorporated):
Updated ProtoHX model for 1040F Service Water inlet temperature and calculated Unit 1 and 2 B & C RHR Pump Room Cooler thermal margins for design fouling factor and 5% tubes plugged.Electronic Calculation Data Files: ProtoHX 3.02. vy-03a.phx, 1280 KB. 4/24/2002, 5:08 pm (Program Name, Version, File Name extension/size/date/hour/min)
Design impact review completed?(if yes, attach impact review sheet)[ ] Yes [.X IN/A, Per ECS: 334017 It I' 1 .A-Prepared by: Jeff W. VanStnen Pf" Reviewed by: Brian L. Davenoort I a -..;I A'Dale Method of Review: Pr)nt[X x D etailed'Sin IITest Date I I Alternate Approved by: J-1~~i"i Print --.) Sign Date External Design Analysis Review (Attachment 3 Attached)Reviewed by:-~ Pf nt sign o t Approved by: / /-P rt" Sign Date Do any ASSUMPTIONS 
/ ENGINEERING JUDGEMENTS require later verification? 
[ ] Yes IX ] No Tracked By: AT#, EC# etc.)Page 2 of 2 E-Form CC-AA-309-1 v1.1 for use with CC-AA-309 Revision 1 and above.
NES-G-14.01 Effective Date: 04/14/00 CALCULATION TABLE OF CONTENTS CALCULATION NO. 97-199 REV. NO. BOO PAGE NO. 3 SECTION: PAGE NO. SUB-PAGE I NO.DESIGN ANALYSIS APPROVAL / TITLE PAGE 1 DESIGN ANALYSIS APPROVAL / REVISION 

==SUMMARY==
2 TABLE OF CONTENTS 3 1.0 PURPOSE / OBJECTIVE 4 2.0 METHODOLOGY AND ACCEPTANCE CRITERIA 4 3.0 ASSUMPTIONS 
/ ENGINEERING JUDGEMENTS 4 4.0 DESIGN INPUT 4 

==5.0 REFERENCES==

4 6.0 CALCULATIONS 5 7.0 

==SUMMARY==
AND CONCLUSIONS 6 8.0 ATTACHMENTS:
6 Attachment "A" -Proto-Hx Calc. Report for 1(2)VY03A Al to A10 (CSCS=104&deg;F 
@ Design Fouling)Attachment "B" -Proto-Hx Caic. Report for 1(2)VY03A B1 to B10 (CSCS=104&deg;F 
@ Design FF, w\5% plugged)Attachment "C" -Proto-Hx CaIc. Report for 1(2)VY03A Cl to C10 (CSCS=104&deg;F 
@ Max. Allowable FF, w\5% plugged)Attachment "D" -Proto-Hx CaIc. Report for 1(2)VY03A D1 to D10 (CSCS=104&deg;F 
@ Design FF, 10% Reduced Airflow)&II E-FORM I CornEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO. 97-199 REV. NO. BOO PAGE NO. 4 of 6 1.0 PURPOSE/OBJECTIVE The purpose of this minor revision is to revise the thermal model of the B & C RHR Pump Room Coolers (1VY03A, 2VY03A) for a 104&deg;F Service Water inlet temperature.
This assessment will evaluate the adequacy of these heat exchangers during a maximum allowable inlet service water temperature of 104*F. Also a maximum design fouling factor will be determined.
2.0 METHODOLOGY AND ACCEPTANCE CRITERIA The existing heat exchanger model will be revised by changing the input of the "Tube Inlet Temp." from 100 0 F to 104OF and simulated for the following conditions:
design fouling factor and design fouling factor with 5% of the tubes plugged. The acceptance criteria will be for the thermal margin at each stated condition to exceed the LaSalle design heat load of 722,217 BTU/hr (Ref. 1, table 1). Additional conservatism was built into this acceptance criteria by assuming a 5% uncertainty in the Proto-HX heat transfer calculations.
The original benchmark model developed for this heat exchanger demonstrated a correlation to vendor performance specification well within this assumed 5% margin. In addition, as analyze within Reference 2, a sensitivity run will be performed with a 10% degraded airflow allowance at a service water inlet temperature of 104 0 F and a 5% plugging allowance.
A final case will be evaluated which determines the maximum acceptable fouling factor at which the design heat load can be accommodated including heat transfer model uncertainty and a 5%tube plugging allowance (w\ design airflow).3.0 ASSUMPTIONS I ENGINEERING JUDGMENTS The assumptions indicated in section 5.0 of References 1 and 2 are still valid.4.0 DESIGN INPUTS The design inputs consist of References 1 and 2 listed below.

==5.0 REFERENCES==
: 1. Calculation No. 97-199, Rev. A, "VY Cooler Thermal Performance Model -1(2)VY03A." 2. Calculation No. 97-199, Rev. B, " VY Cooler Thermal Performance Model -1(2)VY03A." II E-FORM CornEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO. 97-199 REV. NO. BOO PAGE NO. 5 of 6 6.0 CALCULATIONS The current calculation model is based on a Service Water inlet temperature of 100 0 F with a varying cooling water flow rates. Based on Reference 1 Calculation, the limiting flow rate for this unit is 72.5 gpm. At this flow rate, temperature and at an assumed fouling factor of 0.03734207 hr*ft 2*OF/BTU, the amount of heat transferred is 938,124 BTU/hr compared with a LaSalle Station Design Heat Load of 722,217 BTU/hr giving a 29.9% thermal margin (Ref. 1, Table 10).Thermal margin is calculated by the following method: Required Heat Load -Calculated Heat Transfer = Thermal Margin[Equation 1]To express this as a percent of the required heat load, the following method is used: ThermaL argm inx 100% = %ThermalMargin Re quiredHeatLoad
[Equation 2]When the service water inlet temperature is increased to 104 0 F for the same limiting flow rate, but with a design fouling factor of 0.02650655 hr*ft2*OF/BTU, the heat transfer reduces to 874,052 BTU/hr which results in a 21% thermal margin over the design heat transfer rate of 722,217 BTU/hr [Attachment A]. Factoring in a 5% plugging allowance in the heat exchanger and running the model again at the design fouling factor and 104 0 F inlet service water temperature resulted in a 869,248 BTU/hr heat transfer rate, a 20.4% thermal margin above the design heat load[Attachment B]. Furthermore, the maximum fouling factor (at 104*F & 5% plugged) was found to be 0.005 hr*ft 2*OF/BTU tube-side and 0.0005 hr*ft 2*OF/BTU air-side (0.0888 hr*ft 2*OF/BTU overall)[Attachment C]. Additional conservatism explored the heat transfer effects with a 10% outlet airflow reduction, from 26,400 acfm to 23,760 acfm. This yielded a heat transfer rate of 814,593 BTU/hr (at design fouling conditions, 104 0 F, and 5% tube plugging allowance) resulting in a 12.8%thermal margin [Attachment D].I E-FORM.I CornEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO. 97-199 REV. NO. BOO PAGE NO. 6 of 6 7.0 

==SUMMARY==
AND CONCLUSIONS The B & C RHR Pump Room Cooler Model was found to have adequate thermal margin for a maximum lake temperature of 104OF when operated at the design fouling condition.
The maximum fouling factor was found to be 0.005 hr*ft 2*OF/BTU tube-side and 0.0005 hr*ft 2*OF/BTU air-side (0.0888 hr*ft 2*OF/BTU overall) while maintaining the required heat transfer rate at 104 0 F inlet temperature and with a 5% plugging allowance.

==8.0 ATTACHMENTS==
Attachment "A" -Proto-Hx Calc. Report for 1(2)VY03A (CSCS=104 0 F @ Design Fouling)Attachment UB" -Proto-Hx Calc. Report for 1(2)VY03A (CSCS=104 0 F @ Design FF, 5% Plugged)Attachment "C" -Proto-Hx Calc. Report for 1(2)VY03A (CSCS=104 0 F @ Max. Allowable FF, 5% Plugged)Attachment "D" -Proto-Hx Calc. Report for 1(2)VY03A (CSCS=104 0 F @ Design FF, 10% Reduced Airflow)Final Page (Last Page)II E-FORM CornEd CALCULATION NO.97-199 REVISION NO. BOO PAGE NO. Al of A1O Attachment "A" Proto-Hx Calc. Report for 1(2)VY03A (CSCS=104&deg;F 
@ Design Fouling)I E-FORM I 15:54:22 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 04/24/02 ComEd -- LaSalle Data Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, DESIGN FF Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 31,066.00 acfm 180.00 gpm Inlet Dry Bulb Temp 150.00 OF 105.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature 108.80 OF 117.70 OF Outlet Wet Bulb Temp 84.00 OF Outlet Relative Humidity %Tube Fluid Name Fresh Water Tube Fouling Factor 0.001500 Air-Side Fouling 0.000000 Design Heat Transfer (BTU/hr) 1,108,000 Atmospheric Pressure 14.315 Sensible Heat Ratio 1.00 Performance Factor (% Reduction) 0.000 Heat Exchanger Type Counter Flow Fin Type Circular Fins Fin Configuration LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in) 108.000 Fin Pitch (Fins/Inch) 10.000 Fin Conductivity (BTU/hr-ft-&deg;F) 128.000 Fin Tip Thickness (inches) 0.0120 Fin Root Thickness (inches) 0.0120 Circular Fin Height (inches) 1.452 Number of Coils Per Unit 2 Number of Tube Rows 10 Number of Tubes Per Row 24.00 Active Tubes Per Row 24.00 Tube Inside Diameter (in) 0.5270 Tube Outside Diameter (in) 0.6250 Longitudinal Tube Pitch (in) 1.400 Transverse Tube Pitch (in) 1.410 Number of Serpentines 1.000 Tube Wall Conductivity (BTU/hr-ft-&deg;F) 225.00 Calculation No. 97-199 Revision No. BOO Attachment A Page No. Az of Ai, 15:54:22 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/24/02 ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, DESIGN FF Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Condensate Temperature 
(&deg;F)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfm) 27,956.00 Tube Inlet Temp (IF) 104.00 Air Inlet Temp (IF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (IF) 0.00 Atmospheric Pressure 14.315 Calculation No. 97-199 Revision No. BOO Attachment A__Page No. _j 3 of Al.
15:54:22 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, DESIGN FF 04/24/02 Extrapolation Calculation Summary Air-Side Tube-Side Mass Flow (lbm/hr) 103,306.85 36,020.13 Tube-Side hi (BTU/hr ft2-0 F)Inlet Temperature (IF) 148.00 104.00 j Factor Outlet Temperature (IF) 114.18 128.32 Air-Side ho (BTU/hr-ft 2-&deg;F)Inlet Specific Humidity Tube Wall Resistance (hr-ft 2 l-F/BTU' 0.00029413 Outlet Specific Humidity Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 Average Temp (&deg;F)Skin Temperature 
(&deg;F) U Overall (BTU/hr-ft2.&deg;F)
Velocity *** Effective Area (ft 2) 10,532.34 Reynold's Number LMTD Prandtl Number Total Heat Transferred (BTU/hr) 874,052 Bulk Visc (lbm/ft-hr)
Skin Vise (lbm/ft-hr)
Surface Effectiveness (Eta)Density (lbm/ft 3) Sensible Heat Transferred (BTU/hr) 874,052 Cp (BTU/Ibm'&deg;F)
Latent Heat Transferred (BTU/hr)K (BTU/hr-ft-'F)
Heat to Condensate (BTU/hr)Extrapolation Calculation for Row l(Dry)Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/frhr)
Skin Visc (lbmr/fthr)
Density (lbm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 103,306.85 148.00 143.47 0.0203 0.0203 145.73 132.04 4,184.61 932**0.7253 0.0491 0.0621 0.2402 0.0163 Tube-Side 36,020.13 125.07 128.32 126.69 129.04 2.23 17,188 3.3969 1.2658 1.2394 61.6051 0.9989 0.3722 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr.ft 2-F/BTU, Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total-Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)843.38 0.0071 8.87 0.00029413

==0.0 2650655==
5.88 1,053.23 18.91 117,114 0.9221 117,114** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment
_A Page No. oAf4. of/_Air Mass Velocity (Lbm/hr'it), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:54:22 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, DESIGN FF 04/24/02 Extrapolation Calculation for Row 2(Dry) :J Air-Side Tube-Side Mass Flow (lbm/hr) 103,306.85 36,020.13 Tube-Side hi (BTU/hr-ft 2.&deg;F) 830.54 Inlet Temperature 
(&deg;F) 143.47 122.03 j Factor 0.0071 Outlet Temperature (OF) 139.24 125.07 Air-Side ho (BTU/hr ft2.IF) 8.85 Inlet Specific Humidity 0.0203 Tube Wall Resistance (hr-ft 2.&deg;F/BTU' 0.00029413 Outlet Specific Humidity 0.0203 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02650655 Average Temp (IF) 141.36 123.55 Skin Temperature 
(&deg;F) 128.56 125.77 U Overall (BTU/hr-ft 2.0 F) 5.86 Velocity *** 4,184.61 2.23 Effective Area (ft 2) 1,053.23 Reynold's Number 938** 16,702 LMTD 17.69 Prandtl Number 0.7257 3.5052 Total Heat Transferred (BTU/hr) 109.161 Bulk Vise (lbm/ft.hr) 0.0488 1.3027 Skin Visc (lbm/ft-hr) 1.2764 Surface Effectiveness (Eta) 0.9222 Density (lbm/ft 3) 0.0625 61.6559 Sensible Heat Transferred (BTU/hr) 109,161 Cp (BTU/lbm'&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr'ft-'F) 0.0162 0.3712 Heat to Condensate (BTUihr)** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry) I Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbrn/ftihr)
Skin Visc (1bm/Ifthr)
Density (Ibm/fl 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft'&deg;F)
Air-Side 103,306.85 139.24 135.31 0.0203 0.0203 137.27 125.32 4,184.61 942**0.7261 0.0486 Tube-Side 36,020.13 119.20 122.03 120.62 122.72 2.23 16,252 3.6115 1.3387 1.3127 61.7021 0.9988 0.3702 Tube-Side hi (BTU/hr.ft 2.&deg;F) 818.52 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.83 Tube Wall Resistance (hr-ft 2.&deg;F/BTU1, 0.00029413 Overall Fouling (hr-ft 2.F/BTU) 0.02650655 U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.84 1,053.23 16.55 101,788 0.9224 101,788 0.0629 0.2402 0.0161** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. [3OO Attachment Page No. _&S of A_._*** Air Mass Velocity (Lbm/hr-ft'), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:54:22 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, DESIGN FF 04/24/02[I Extrapolation Calculation for Row 4(Dry)Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbml/ft 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft--F)
Air-Side 103,306.85 135.31 131.63 0.0203 0.0203 133.47 122.30 4,184.61 947**0.7264 0.0483 0.0633 0.2402 0.0160 Tube-Side 36,020.13 116.56 119.20 117.88 119.87 2.23 15,837 3.7154 1.3738 1.3481 61.7442 0.9988 0.3693 Tube-Side hi (BTU/hr.ft2.&deg;F) 807.26 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2-&deg;F) 8.81 Tube Wall Resistance (hr-ft2-&deg;F/BTU" 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (W)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.82 1,053.23 15.48 94,950 0.9225 94,950** Reynolds Number Outside Range of Equation Applicability U" Extrapolation Calculation for Row 5(Dry)II I.Air-Side Tube-Side Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/fl-hr)
Density (lbm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr-ff-&deg;F) 103,306.85 131.63 128.20 0.0203 0.0203 129.92 119.48 4,184.61 951**0.7267 0.0481 0.0637 0.2402 0.0159 36,020.13 114.10 116.56 115.33 117.21 2.23 15,453 3.8168 1.4079 1.3826 61.7826 0.9988 0.3684 Applicability Tube-Side hi (BTU/hr-ft 2.F) 796.71 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.79 Tube Wall Resistance (hr-ft2.&deg;F/BTU' 

==0.0 0029413==
Overall Fouling (hr- ft 2-&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)..
Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.81 1,053.23 14.49 88,602 0.9226 88,602** Reynolds Number Outside Range of Equation Calculation No. 97-199 Revision No. BOO Attachment A Page No. _/4 of,&,._*** Air Mass Velocity (Lbm/hrVft2).
Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 15:54:22 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, DESIGN FF 04/24/02 I! Extrapolation Calculation for Row 6(Dry) I Air-Side Tube-Side Mass Flow (Ibm/hr) 103,306.85 36,020.1 Inlet Temperature 
('F) 128.20 111.8 Outlet Temperature 
('F) 125.00 114.1 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp ('F) 126.60 112.9 Skin Temperature (0 F) 116.84 114.7 Velocity *** 4,184.61 2.2 Reynold's Number 956** 15,09 Prandtl Number 0.7269 3.915 Bulk Visc (ibm/ft hr) 0.0479 1.441 Skin Visc (ibm/ft hr) 1.416 Density (lbm/ft 3) 0.0640 61.817 Cp (BTU/lbm'&deg;F) 0.2402 0.998.K (BTU/hr.ft-&deg;F) 0.0158 0.367'** Reynolds Number Outside Range of Equation Applicability 3 0 0 5 3 3 7 6 1 2 7 8 6 Tube-Side hi (BTU/hr.ft 2.&deg;F) 786.83 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.78 Tube Wall Resistance (hr ft 2.&deg;0 F/BTU' 0.00029413 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hr ft 2.'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.79 1,053.23 13.56 82,706 0.9228 82,706 I.II Extrapolation Calculation for Row 7(Dry)II Air-Side Tube-Side Mass Flow (ibm/hr) 103,306.85 36,020.1: Inlet Temperature 
(&deg;F) 125.00 109.6: Outlet Temperature 
(&deg;F) 122.01 111.8(Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 123.51 110.7: Skin Temperature 
(&deg;F) 114.38 112.4(Velocity *** 4,184.61 2.2 Reynold's Number 959** 14,761 Prandtl Number ... .037272 4.011 Bulk Visc (ibm/ft hr) 0.0477 1.473: Skin Visc (ibm/ft-hr) 1.448 Density (Ibm/ft 3) 0.0643 61.849" Cp (BTU/lbm-&deg;F) 0.2402 0.998t K (BTU/hr-ft'&deg;F) 0.0158 ** Reynolds Number Outside Range of Equation Applicability 3 5 0 Tube-Side hi (BTU/hr-ft 2-&deg;F) 777.57 j Factor 0.0070 Air-Side ho (BTU/hr-ft2-&deg;F) 8.76 Tube Wall Resistance (hr-ft2.&deg;F/BTU' 

==0.0 0029413==
Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02650655 3 0 2 8 7 7 U Overall (BTU/hr-ft 2..F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr) .Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.77 1,053.23 12.70 77,227 0.9229 77,227 Calculation No. 97-199 Revision No. BOO Attachment A Page No. A-L of _..L Air Mass Velocity (Lbm/hr-fi 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:54:22 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, DESIGN FF 04/24/02 I[ Extrapolation Calculation for Row 8(Dry)Mass Flow (ibm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (ibm/tf.hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/fl 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 103,306.85 122.01 119.22 0.0203 0.0203 120.62 112.08 4,184.61 963**0.7274 0.0475 Tube-Side 36,020.13 107.65 109.65 Tube-Side hi (BTU/hr ft 2.&deg;F) 768.90 j Factor 0.0070 Air-Side ho (BTU/hr.ft 2-F) 8.75 Tube Wall Resistance (hr-ft 2.&deg;F/BTU' 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02650655 108.65 110.24 2.22 14,462 4.1049 1.5043 1.4805 61.8790 0.9988 0.3660 U Overall (BTU/hrft2.&deg;'F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.76 1,053.23 11.89 72,132 0.9230 72,132 0.0647 0.2402 0.0157** Reynolds Number Outside Range of Equation Applicability II Extrapolation Calculation for Row 9(Dry)II I Air-Side Mass Flow (ibm/hr) 103,306.85 Inlet Temperature 
(&deg;F) 119.22 Outlet Temperature 
(&deg;F) 116.62 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 117.92 Skin Temperature 
(&deg;F) 109.93 Velocity *** 4,184.61 Reynold's Number 967**Prandtl Number .. .. ........0:7275..Bulk Visc (lbm/ft.hr) 0.0474 Skin Visc (Ibm/ftrhr)
Density (ibm/fl 3) 0.0649 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0156** Reynolds Number Outside Range of Equation Tube-Side 36,020.13 105.78 107.65 106.71 108.21 2.22 14,179 4.1952 1.5344 1.5111 61.9058 0.9989 0.3653 Applicability Tube-Side hi (BTU/hr-ft 2-&deg;F)j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr.ft 2.&deg;F/BTU'Overall Fouling (hr-ft 2-&deg;F/BTU)U Overall (BTU/hr.ft 2.'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/br)Heat to Condensate (BTU/hr)760.77 0.0070 8.74 0.00029413

==0.0 2650655==
5.75 1,053.23 11.13.67,393 0.9231 67,393 Calculation No. 97-199 Revision No. BOO Attachment A Page No. _,oof fi.;*** Air Mass Velocity (Lbm/hr ft 2). Tube Fluid Velocity (fi/sec):
Air Density at Inlet T. Other Properties at Average T 15:54:22 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: I(2)VYO3A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, DESIGN FF 04/24/02 Extrapolation Calculation for Row 10(Dry)Air-Side Tube-Side Mass Flow (ibm/hr) 103,306.85 36,020.13 Inlet Temperature (OF) 116.62 104.03 Outlet Temperature (OF) 114.18 105.78 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 115.40 104.90 Skin Temperature (OF) 107.93 106.31 Velocity *** 4,184.61 2.22 Reynold's Number 970** 13,916 Prandtl Number 0.7277 4.2825 Bulk Visc (lbrnm/fthr) 0.0472 1.5634 Skin Visc (Ibm/ft-hr) 1.5407 Density (lbm/ft 3) 0.0652 61.9303 Cp (BTU/lbm-'F) 0.2402 0.9989 K (BTU/hr'ft-VF) 0.0156 0.3647** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hr'ft-'&deg;F) 753.16 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2-&deg;F) 8.73 Tube Wall Resistance (hr-ft 2.&deg;F/BTU, 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ftf)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.73 1,053.23 10.43 62,981 0.9232 62,981 Calculation No. 97-199 Revision No. BOO Attachment A Page No. __ of Aic*** Air Mass Velocity (Lbm/ihr-ft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Inlet Air Flowrate Calculator 
-1(2)VY03A Total P: P=Dry Bulb T OUT: T=Specific Hum.: W =H20 Vap P: Pv Dry Air P: Pa Dry Air rho OUT: rho Dry Air rho IN: rho Dry Bulb T IN: T=Outlet Air Flow: V =(W*RvP)/(Ra+(W*Rv)-P -Pv =a = (144/Ra)*(PaI(459.67+T) 
=a = (144/Ra)*(PaI(459.67+T) 
=Rv =Ra =14.315 psia Inlet Air Flow 114.18 F 27956 acfm 0.020273629 0.451874527 psia 85.778 (ft-lbf)/(Ibm-R) 53.352 (ft-lbf)/(Ibm-R) 13.86312547 psia 0.0652 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 26400 cfm Calculation No. 97-199 Revision No. BOO Attachment Page No. A of -.
Cornkd CALCULATION NO.97-199 REVISION NO. BOO PAGE NO. BI of BIO Attachment "B" Proto-Hx CaIc. Report for I(2)VY03A (CSCS=104 0 F @ Design FF, 5% Plugged)I E-FORM I 15:35:39 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Data Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, DESIGN FF 04/24/02 I Air Coil Heat Exchanger Input Parameters Fluid Quantity, Total Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 31,066.00 acfm 150.00 OF 92.00 OF 108.80 OF 84.00 OF Tube-Side 180.00 gpm 105.00 OF 117.70 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Fresh Water 0.001500 0.000000 1,108,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]108.000 10.000 128.000 0.0120 0.0120 1.452 Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row 2 10 24.00 23.00 Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-&deg;F) 0.5270 0.6250 1.400 1.410 1.000 225.00 Calculation No. 97-199 Revision No. BOO Attachment 8 Page No. 9- of 15:35:39 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/24/02 ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, DESIGN FF IF Calculation Specifications I Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfim)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfin) 27,948.00 Tube Inlet Temp ('F) 104.00 Air Inlet Temp ('F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ('F) 0.00 Atmospheric Pressure 14.315 Calculation No. 97-199 Revision No. BOO Attachment i Page No. B of _8 15:35:39 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, DESIGN FF 04/24/02 I[ Extrapolation Calculation Summary Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr-ft'&deg;F)
Air-Side 103,277.29 148.00 114.35 Tube-Side 36,020.13 104.00 128.15 Tube-Side hi (BTU/hr1'ft 2"F)j Factor Air-Side ho (BTU/hr-ft 2-&deg;F)Tube Wall Resistance (hr-ft2. F/BTU, Overall Fouling (hr-ft2.0 F/BTU)U Overall (BTU/hr-ft2-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/Ihr)0.00029413

==0.0 2650655==
10,093.49 869,248 869,248 I.Extrapolation Calculation for Row l(Dry)II I.Air-Side Tube-Side Mass Flow (Ibm/hr) 103,277.29 36,020.13 Inlet Temperature (OF) 148.00 124.93 Outlet Temperature (OF) 143.51 128.15 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 145.76 126.54 Skin Temperature 
(&deg;F) 131.98 128.88 Velocity *** 4,365.29 2.33 Reynold's Number 973** 17,910 Prandtl Number 0.7253 3.4021 Bulk Visc (lbm/ft-hr) 0.0491 1.2676 Skin Visc (Ibm/ft-hr) 1.2411 Density (lbm/ft 3) 0.0620 61.6076 Cp (BTU/lbm'&deg;F) 0.2402 0.9989 K (BTU/hr-ft-&deg;F) 0.0163 0.3722** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hrlft 2.&deg;F) 871.94 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2 1-F) 9.12.Tube Wall Resistance (hr-ft2.0 F/BTU' 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.01 1,009.35 19.09 115,887 0.9201 115,887 Calculation No. 97-199 Revision No. BOO Attachment p Page No. e4 of" a.;*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T. Other Properties at Average T 15:35:39 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, DESIGN FF 04/24/02 I Extrapolation Calculation for Row 2(Dry)Air-Side Mass Flow (lbm/hr) 103,277.29 Inlet Temperature (IF) 143.51 Outlet Temperature (IF) 139.33 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 141.42 Skin Temperature (IF) 128.53 Velocity *** 4,365.29 Reynold's Number 978**Prandtl Number 0.7257 Bulk Visc (ibm/ftrhr) 0.0488 Skin Visc (lbm/ft.hr)
Density (Ibm/ft 3) 0.0625 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-ft-.F) 0.0162 Tube-Side 36,020.13 121.92 124.93 123.42 125.64 2.33 17,408 3.5096 1.3041 1.2779 61.6578 0.9988 0.3712 Tube-Side hi (BTU/hr.ft 2-&deg;F) 858.79 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.&deg;F) 9.10 Tube Wall Resistance (hr-ft 2.&deg;F/BTU , 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.99 1,009.35 17.88 108,159 0.9203 108,159** Reynolds Number Outside Range of Equation Applicability yi-.Extrapolation Calculation for Row 3(Dry)II I. *1 Air-Side Tube-Side Mass Flow (lbm/hr) 103,277.29 36,020.1 Inlet Temperature 
(&deg;F) 139.33 119.1 Outlet Temperature (IF) 135.42 121.91 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 137.37 120.51 Skin Temperature (IF) 125.32 122.6" Velocity *** 4,365.29 2.3 Reynold's Number 983** 16,941 Prandtl Number , 0.7261 3.615 Bulk Visc (lbm/ft-hr) 0.0486 1.339*Skin Visc (lbm/ft-hr) Density (Ibm/fl 3) 0.0629 61.703(Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr.ft-&deg;F) 0.0161 0.3701** Reynolds Number Outside Range of Equation Applicability 3 1 2 2 2 3 3 1 9 Tube-Side hi (BTU/hr-ft 2.&deg;F) 846.45 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2-&deg;F) 9.08 Tube Wall Resistance (hr-ft 2.&deg;F/BTU, 0.00029413 Overall Fouling (hr.ft 2.0 F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.97 1,009.35 16.75 100,984 0.9204 100,984 Calculation No. 97-199 Revision No. BOO Attachment
_Page No. 3s of 0,*** Air Mass Velocity (Lbm/hr'ft 2). Tube Fluid Velocity (ft/sec);
Air Density at Inlet T. Other Properties at Average T 15:35:39 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, DESIGN FF 04/24/02 Extrapolation Calculation for Row 4(Dry) I Air-Side Tube-Side Mass Flow (lbm/hr) 103,277.29 36,020.13 Tube-Side hi (BTU/hr.ft2-&deg;F) 834.89 Inlet Temperature (OF) 135.42 116.49 j Factor 0.0070 Outlet Temperature 
(&deg;F) 131.77 119.11 Air-Side ho (BTU/hr-ft2.&deg;F) 9.06 Inlet Specific Humidity 0.0203 Tube Wall Resistance (hr-ft 2-&deg;F/BTU" 0.00029413 Outlet Specific Humidity 0.0203 Overall Fouling (hr-ft 2.OF/BTU) 0.02650655 Average Temp (OF) 133.59 117.80 Skin Temperature (OF) 122.31 119.79 U Overall (BTU/hr-ft 2.OF) 5.96 Velocity *** 4,365.29 2.33 Effective Area (ft 2) 1,009.35 Reynold's Number 988** 16,513 LMTD 15.69 Prandtl Number 0.7264 3.7184 Total Heat Transferred (BTU/hr) 94,320 Bulk Visc (lbm/ft-hr) 0.0483 1.3748 Skin Visc (lbm/ft.hr) 1.3491 Surface Effectiveness (Eta) 0.9205 Density (lbm/ft')
0.0633 61.7454 Sensible Heat Transferred (BTU/hr) 94,320 Cp (BTU/Ibm'&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr'ft-&deg;F) 0.0160 0.3693 Heat to Condensate (BTU/hr)** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ftl)Cp (BTUilbm'&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 103,277.29 131.77 128.36 0.0203 0.0203 130.06 119.51 4,365.29 992**0.7267 0.0481 0.0636 0.2402 0.0159 Tube-Side 36,020.13 114.04 116.49 115.27 117.15 2.32 16,115 3.8194 1.4088 1.3834 61.7836 0.9988 0.3684 Tube-Side hi (BTU/hr-ft 2.&deg; F) 824.04 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2-&deg;F) 9.04 Tube Wall Resistance (hr-ft 2 1-F/BTU7, 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr.ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.94 1,009.35 14.70 88,125 0.9207 88,125** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment
_Page No. _ of'&,*** Air Mass Velocity (Lbmihrf't 2), Tube Fluid Velocity (fi/sec);
Air Density at Inlet T, Other Properties at Average T 15:35:39 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, DESIGN FF 04/24/02 Extrapolation Calculation for Row 6(Dry) I Air-Side Tube-Side Mass Flow (lbm/hr) 103,277.29 36,020.13 Tube-Side hi (BTU/hr.ft 2.&deg;F) 813.86 Inlet Temperature 
(&deg;F) 128.36 111.75 j Factor 0.0070 Outlet Temperature 
(&deg;F) 125.17 114.04 Air-Side ho (BTU/hr-ft 2.&deg;F) 9.03 Inlet Specific Humidity 0.0203 Tube Wall Resistance (hrft 2 2.&deg;F/BTU, 0.00029413 Outlet Specific Humidity 0.0203 Overall Fouling (hr'ft 2-&deg;F/BTU) 0.02650655 Average Temp (&deg;F) 126.76 112.90 Skin Temperature 
("F) 116.88 114.68 U Overall (BTU/hr-ft 2.&deg;F) 5.92 Velocity *** 4,365.29 2.32 Effective Area (ft 2) 1,009.35 Reynold's Number 997** 15,745 LMTD 13.78 Prandtl Number 0.7269 3.9178 Total Heat Transferred (BTU/hr) 82,364 Bulk Visc (lbm/ft-hr) 0.0479 1.4418 Skin Visc (lbm/fr-hr) 1.4168 Surface Effectiveness (Eta) 0.9208 Density (Ibm/ft 3) 0.0640 61.8184 Sensible Heat Transferred (BTU/hr) 82,364 Cp (BTU/lbm'&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft.&deg;F) 0.0158 0.3676 Heat to Condensate (BTU/hr)** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)Mass Flow (lbm/hr)Inlet Temperature (7F)Outlet Temperature (7F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (7F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number.Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (ibm/fl 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 103,277.29 125.17 122.19 0.0203 0.0203 123.68 114.43 4,365.29 1,001.....0.7272 0.0477 0.0643 0.2402 0.0158 Tube-Side 36,020.13 109.61 111.75 110.68 112.37 2.32 15,403...4.0136 1.4739 1.4494 61.8503 0.9988 0.3668 Tube-Side hi (BTU/hr-ft 2-&deg;F) 804.32 j Factor 0.0069 Air-Side ho (BTU/hr-ft 2.&deg;F) 9.01 Tube Wall Resistance (hr-ft 2.&deg;F/BTU' 0.00029413 Overall Fouling (hr-ftl.&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hr-f2.&deg;'F)
Effective Area (ft 2)LMTD Total HeatTransferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.91 1,009.35 12.91 77,003 0.9209 77,003 Calculation No. 97-199 Revision No. BOO Attachment j, Page No. el of e/.;*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:35:39 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, DESIGN FF 04/24/02 Extrapolation Calculation for Row 8(Dry)Air-Side Tube-Side Mass Flow (lbm/hr) 103,277.29 36,020.13 Tube-Side hi (BTU/hr.ft 2.&deg;F) 795.37 Inlet Temperature (OF) 122.19 107.61 j Factor 0.0069 Outlet Temperature (IF) 119.40 109.61 Air-Side ho (BTU/hr.ft 2.&deg;F) 9.00 Inlet Specific Humidity 0.0203 Tube Wall Resistance (hr-ft1 2-F/BTU' 0.00029413 Outlet Specific Humidity 0.0203 Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02650655 Average Temp (IF) 120.80 108.61 Skin Temperature 
(&deg;F) 112.13 110.21 U Overall (BTU/hr.ft2-&deg;F) 5.89 Velocity *** 4,365.29 2.32 Effective Area (ft 2) 1,009.35 Reynold's Number 1,005 15,085 LMTD 12.11 Prandtl Number 0.7274 4.1067 Total Heat Transferred (BTU/hr) 72,012 Bulk Visc (ibm/ifthr) 0.0475 1.5049 Skin Visc (lbm/.fthr) 1.4809 Surface Effectiveness (Eta) 0.9210 Density (lbm/ft 3) 0.0646 61.8795 Sensible Heat Transferred (BTU/hr) 72,012 Cp (BTU/Ibm-.F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft-&deg;F) 0.0157 0.3660 Heat to Condensate (BTU/hr)IF Extrapolation Calculation for Row 9(Dry) 1 Air-Side Mass Flow (lbm/hr) 103,277.29 Inlet Temperature (IF) 119.40 Outlet Temperature (IF) 116.79 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 118.10 Skin Temperature (IF) 109.98 Velocity *** 4,365.29 Reynold's Number 1,008 Prandtl Number ..- --;--.... 0:7275 Bulk Visc (Ibm/ft-hr) 0.0474 Skin Visc (lbm/ft.hr)
Density (lbm/ft 3) 0.0649 Cp (BTU/lbm'&deg;F) 0.2402 K (BTU/hr"ft'&deg;F) 0.0156 Tube-Side 36,020.13 105.74 107.61 106.68 108.18 2.32 14,790 4.1970 1.5350 1.5115 61.9063 0.9989 0.3653 Tube-Side hi (BTU/hr.ft 2-&deg;F) 786.98 j Factor 0.0069 Air-Side ho (BTU/hr.ft2.&deg;F) 8.99 Tube Wall Resistance (hr-ft 2.&deg;F/BTU , 0.00029413 Overall Fouling (hr.ft 2.F/BTU) 0.02650655 U Overall (BTU/hr.t2.&deg;IF)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.88 1,009.35 11.35*67,363 0.9211 67,363 Calculation No. 97-199 Revision No. BOO Attachment a Page No. or of' pi,*** Air Mass Velocity (Lbm/hr-ft2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average r 15:35:39 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, DESIGN FF 04/24/02 Extrapolation Calculation for Row 10(Dry)Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibmlfthr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hrftf-F)
Air-Side 103,277.29 116.79 114.35 0.0203 0.0203 115.57 107.97 4,365.29 1,012 0.7277 0.0472 0.0652 0.2402 0.0156 Tube-Side 36,020.13 103.99 105.74 104.86 106.29 2.32 14,515 4.2844 1.5640 1.5411 61.9308 0.9989 0.3646 Tube-Side hi (BTU/hr-ft 2.&deg;F) 779.10 j Factor 0.0069 Air-Side ho (BTU/hr-ft 2.0 F) 8.97 Tube Wall Resistance (hr-ft1 2-F/BTU' 0.00029413 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.87 1,009.35 10.64 63,031 0.9212 63,031 Calculation No. 97-199 Revision No. BOO Attachment R Page No. > of a,.-*** Air Mass Velocity (Lbm/hr'ft2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Inlet Air Flowrate Calculator 
-1(2)VY03A Total P: P=Dry Bulb T OUT: T=Specific Hum.: W H20 Vap P: Pv Dry Air P: Pa=Dry Air rho OUT: rho Dry Air rho IN: rho Dry Bulb T IN: T=Outlet Air Flow: V =(W*Rv*P)/(Ra+(W*Rv)
~P -Pv'a = (144/Ra)*(PaI(459.67+T) 
=a = (144/Ra)*(Pa/(459.67+T) 
=Rv =Ra =14.315 psia Inlet Air Flow 114.35 F 27948 acfm 0.020273629 0.451874527 psia 85.778 (ft-lbf)/(Ibm-R) 53.352 (ft-lbf)/(Ibm-R) 13.86312547 psia 0.0652 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 26400 cfm Calculation No. 97-199 Revision No. BOO Attachment RL Page No. a ofj_&_
CoW..,I-1rn I CALCULATION NO.97-199 REVISION NO. BOO PAGE NO. C1 of C10 Attachment "C" Proto-Hx Calc. Report for I(2)VY03A (CSCS=104&deg;F 
@ Max. Allowable FF, w\5% plugged)I E-FORM I 16:19:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 04/24/02 ComEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, MAX FF 1L Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 31,066.00 acfrn 180.00 gpm Inlet Dry Bulb Temp 150.00 OF 105.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature 108.80 OF 117.70 OF Outlet Wet Bulb Temp 84.00 OF Outlet Relative Humidity %Tube Fluid Name Fresh V, ater Tube Fouling Factor 0.005000 Air-Side Fouling 0.000500 Design Heat Transfer (BTU/hr) 1,108,000 Atmospheric Pressure 14.315 Sensible Heat Ratio 1.00 Performance Factor (% Reduction) 0.000 Heat Exchanger Type Counter Flow Fin Type Circular Fins Fin Configuration LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in) 108.000 Fin Pitch (Fins/Inch) 10.000 Fin Conductivity (BTU/hr-ft-&deg;F) 128.000 Fin Tip Thickness (inches) 0.0120 Fin Root Thickness (inches) 0.0120 Circular Fin Height (inches) 1.452 Number of Coils Per Unit 2 Number of Tube Rows 10 Number of Tubes Per Row 24.00 Active Tubes Per Row 23.00 Tube Inside Diameter (in) 0.5270 Tube Outside Diameter (in) 0.6250 Longitudinal Tube Pitch (in) 1.400 Transverse Tube Pitch (in) 1.410 Number of Serpentines 1.000 Tube Wall Conductivity (BTU/hr-ft-&deg;F) 225.00 Calculation No. 97-I199 Revision No. BOO Attachment c_Page No. L&#xfd; of '-z 16:19:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/24/02 ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, MAX FF Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfm) 27,779.00 Tube Inlet Temp (&deg;F) 104.00 Air Inlet Temp ('F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ('F) 0.00 Atmospheric Pressure 14.315 Calculation No. 97-199 Revision No. BOO Attachment c Page No. _ of j_
16:19:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, MAX FF 04/24/02.1 Extrapolation Calculation Summary II 1.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbmr/fthr)
Skin Visc (lbm/ft-hr)
Density (Ibm/fl 3)Cp (BTU/lbm 0'F)K (BTU/hr-ft--F)
Air-Side 102,652.78 148.00 117.83 Tube-Side 36,020.13 104.00 125.53 Tube-Side hi (BTU/hr-ftl-&deg;F) j Factor Air-Side ho (BTU/hr-fl 2.&deg;F)Tube Wall Resistance (hr-ft 2 1-F/BTU, Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 8885517==
10,093.49 774,686 774,686 Extrapolation Calculation for Row l(Dry)II I.Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr-ft'&deg;F)
Air-Side 102,652.78 148.00 144.25 0.0203 0.0203 146.13 134.68 4,338.90 966*-0.7253 0.0491 0.0620 0.2402 0.0163 Tube-Side 36,020.13 122.85 125.53 124.19 126.15 2.33 17,531 3.4827 1.2950 1.2720 61.6456 0.9988 0.3714 Tube-Side hi (BTU/hr-ft 2.&deg;F) 861.71 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.F) 9.08 Tube Wall Resistance (hr-ft1 2.F/BTU, 0.00029413 Overall Fouling (hr.ft 2-F/BTU) 0.08885517 U Overall (BTU/hr-ft2.IF)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.36 1,009.35 21.86 96,218 0.9204 96,218** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment c Page No. o4 of -Air Mass Velocity (Lbm/hr-ft').
Tube Fluid Velocity (ft/sec), Air Density at Inlet T, Other Properties at Average T 16:19:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, MAX FF 04/24/02 M.Extrapolation Calculation for Row 2(Dry)II I.Air-Side Tube-Side Mass Flow (lbm/hr) 102,652.78 36,020.1 Inlet Temperature (0 F) 144.25 120.31 Outlet Temperature 
(&deg;F) 140.69 122.8.Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 142.47 121.5&#xfd;Skin Temperature (0 F) 131.58 123.4", Velocity *** 4,338.90 2.3 Reynold's Number 971** 17,11.Prandtl Number 0.7256 3.575c Bulk Vise (lbm/ft'hr) 0.0489 1.326(Skin Visc (ibm/rtfhr) 1.303(Density (Ibm/fl 3) 0.0623 61.687(Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr-ft 0.F) 0.0162 0.370(** Reynolds Number Outside Range of Equation Applicability 5 7 3 3 9 6 6 Tube-Side hi (BTU/hr-ft 2.&deg;F) 850.70 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2"&deg;F) 9.06 Tube Wall Resistance (hr-ft 2.&deg;F/BTU' 0.00029413 Overall Fouling (hr'ft 2-&deg;F/BTU) 0.08885517 U Overall (BTU/hr'ft 2.&deg;F)Effective Area (IW)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.35 1,009.35 20.82 91,443 0.9205 91,443.1 Extrapolation Calculation for Row 3(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature 
('F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftfhr)
Skin Visc (lbm/ft-hr)
Density (lbm/fl 3)Cp (BTU/lbm.'F)
K (BTU/hr-ft.&deg;F)
Air-Side 102,652.78 140.69 137.31 0.0203 0.0203 139.00 128.62 4,338.90 975*1 0.7259 0.0487 0.0627 0.2402 0.0161 Tube-Side 36,020.13 117.90 120.31 119.10 120.92 2.33 16,719 3.6683 1.3579 1.3348 61.7255 0.9988 0.3697 Tube-Side hi (BTU/hr-ft 2-0 F) 840.18 j Factor 0.0070 Air-Side ho (BTU/hrft2-&deg;F) 9.05 Tube Wall Resistance (hr.ft 2.&deg;F/BTUJ 0.00029413 Overall Fouling (hr'ft2-&deg;F/BTU) 

==0.0 8885517==
U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft')LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.34 1,009.35 19.83 86,919 0.9206 86,919** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment c Page No. e of C1.*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 16:19:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, MAX FF 04/24/02 Extrapolation Calculation for Row 4(Dry)Air-Side 102,652.78 Tube-Side 36,020.13 Mass Flow (lbm/hr)Inlet Temperature (OF) 137.31 115.6(Outlet Temperature (OF) 134.09 117.9(Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 135.70 116.7.Skin Temperature (OF) 125.82 118.5(Velocity *** 4,338.90 2.3: Reynold's Number 979** 16,34 Prandtl Number 0.7262 3.7595 Bulk Visc (lbm/ft.hr) 0.0485 Skin Visc (lbm/ftrhr) 1.365k Density (lbm/ft 3) 0.0630 61.761l Cp (BTU/lbm'&deg;F) 0.2402 0.998k K (BTU/hr'ft'F) 0.0160 0.368*** Reynolds Number Outside Range of Equation Applicability
*)5 7 7 9.Tube-Side hi (BTU/hr ft2.&deg;F) 830.15 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.&deg;F) 9.03 Tube Wall Resistance (hr-ft 2.&deg;F/BTU' 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.08885517 U Overall (BTU/hr.ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.33 1,009.35 18.89 82,633 0.9208 82,633 NAM1 Extrapolation Calculation for Row 5(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number*Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ftbhr)
Density (Ibm/fl 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr'ft'&deg;F)
Air-Side 102,652.78 134.09 131.03 0.0203 0.0203 132.56 123.15 4,338.90 983*, 0.7265 0.0483 0.0634 0.2402 0.0160 Tube-Side 36,020.13 113.41 115.60 114.51 116.19 2.32 15,996 3.8505 1.4193 1.3963 61.7948 0.9988 0.3681 Tube-Side hi (BTU/hr-ft 2 1-F) 820.59 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.&deg;F) 9.02 Tube Wall Resistance (hr-ft 2.F/BTU' 0.00029413 Overall Fouling (hr.ft 2-&deg;F/BTU) 0.08885517 U Overall (BTU/hr-ft 2&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.33 1,009.35 17.99 78,570 0.9209 78,570** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment C.Paec No. tL of(Air Mass Velocity (Lbm/hr'fti), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 16:19:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, MAX FF 04/24/02 I Extrapolation Calculation for Row 6(Dry)ii II ....Mass Flow (Ibmlhr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbni/ftihr)
Skin Vise (lbm/ftrhr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-fti'F)
Air-Side 102,652.78 131.03 128.12 0.0203 0.0203 129.57 120.62 4,338.90 987**0.7267 0.0481 0.0637 0.2402 0.0159 Tube-Side 36,020.13 111.34 113.41 112.38 113.99 2.32 15,665 3.9401 1.4493 1.4264 61.8260 0.9988 0.3674 Tube-Side hi (BTU/hr.ft 2.&deg;F) 811.46 j Factor 0.0070 Air-Side ho (BTU/hr'ft 2-.F) 9.00 Tube Wall Resistance (hr-ft 2.F/BTU' 0.00029413 Overall Fouling (hr.ft 2.F/BTU) 0.08885517 U Overall (BTU/hrft 2Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.32 1,009.35 17.14 74,719 0.9210 74,719** Reynolds Number Outside Range of Equation Applicability t =6 Extrapolation Calculation for Row 7(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/1bm'&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 102,652.78 128.12 125.35 0.0203 0.0203 126.74 118.20 4,338.90 991**0.7269 0.0479 0.0640 0.2402 0.0158 Tube-Side 36,020.13 109.36 111.34 110.35 111.91 2.32 15,352 4.0284 1.4788 1.4561 61.8551 0.9988 0.3667 Tube-Side hi (BTU/hrfi.
IF)j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU, Overall Fouling (hrft 2 0.&deg;F/BTU)U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)802.75 0.0070 8.99 0.00029413

==0.0 8885517==
4.31 1,009.35 16.33.....71,067 0.9211 71,067** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment 
, Page No. c -_ of cj-*** Air Mass Velocity (Lbm/hr-ft), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 16:19:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, MAX FF 04/24/02 U'Extrapolation Calculation for Row 8(Dry)II I._Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Air-Side 102,652.78 125.35 122.72 0.0203 0.0203 124.04 115.91 4,338.90 994**0.7271 Tube-Side 36,020.13 107.48 109.36 Tube-Side hi (BTU/hr-ft 2.0 F) 794.45 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.98 Tube Wall Resistance (hr-ft 2 2.&deg;F/BTU, 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.08885517 108.42 109.92 2.32 15,056 4.1154 Bulk Visc (lbm/ft-hr) 0.0477 1.507 Skin Visc (lbm/ft-hr) 1.485: Density (Ibm/Ift 3) 0.0643 61.882" Cp (BTU/Ibm-'F) 0.2402 K (BTU/hr'ft.-F) 0.0158 0.366(** Reynolds Number Outside Range of Equation Applicability 8 2 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.30 1,009.35 15.56 67,603 0.9212 67,603 k~w. Is Extrapolation Calculation for Row 9(Dry)II II Air-Side Tube-Side Mass Flow (lbm/hr) 102,652.78 36,020.1.Inlet Temperature (IF) 122.72 105.7'Outlet Temperature (IF) 120.22 107.4 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 121.47 106.5 Skin Temperature (OF) 113.73 108.0 Velocity *** 4,338.90 2.3: Reynold's Number 998** 14,77" Prandtl Number .... 0.7273 4.201 Bulk Visc (lbmift-hr) 0.0476 1.536: Skin Visc (lbm/ft-hr) 1.513'Density (lbm/ft 3) 0.0645 61.907: Cp (BTU/Ibm-&deg;F) 0.2402 0.998'K (BTU/hr'ft-&deg;F) 0.0157 0.365** Reynolds Number Outside Range of Equation Applicability 3 0 8 9 3 2 7 0 3 9 5 9 3 Tube-Side hi (BTU/hrlft2-&deg;F) 786.53 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.97 Tube Wall Resistance (hr-ft 2.&deg;F/BTUQ 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.08885517 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.30 1,009.35 14.83 64,316 0.9213 64,316 Calculation No. 97-199 Revision No. BOO Attachment c, Page No. ej of c,_*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 16:19:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03 @ 104 F, 5% PLUG, MAX FF 04/24/02 B. II ExtraDolation Calculation for Row 1O(Dry)II Air-Side Mass Flow (ibm/hr) 102,652.78 Inlet Temperature (IF) 120.22 Outlet Temperature (IF) 117.83 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 119.02 Skin Temperature (IF) 111.65 Velocity *** 4,338.90 Reynold's Number 1,001 Prandtl Number 0.7275 Bulk Visc (lbmr/t.hr) 0.0474 Skin Visc (lbm/ft-hr)
Density (lbm/ft 3) 0.0648 Cp (BTU/Ibm'&deg;F) 0.2402 K (BTU/hr'ft-'F) 0.0157 Tube-Side 36,020.13 103.99 105.70 104.85 -106.23 2.32 14,513 4.285?1.5643 1.5421 61.9311 0.9989 0.3646 Tube-Side hi (BTU/hr-ftl 2.F) 778.97 j Factor 0.0069 Air-Side ho (BTU/hr'ft 2"&deg;F) 8.95 Tube Wall Resistance (hr-ftl.&deg;F/BTU' 

==0.0 0029413==
Overall Fouling (hr.ft 2.&deg;F/BTU) 0.08885517 U Overall (BTU/hr-f2-&deg;'F)
Effective Area (ft')LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.29 1,009.35 14.13 61,198 0.9214 61,198 Calculation No. 97-199 Revision No. BOO Attachment C Pagte No. c ofc*** Air Mass Velocity (Lbrn/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Inlet Air Flowrate Calculator 
-1(2)VY03A Total P: P=Dry Bulb T OUT: T=Specific Hum.: W =H20 Vap P: Pv = (W*Rv*P)/(Ra+(W*Rv) 
=Dry Air P: Pa = P -Pv=Dry Air rho OUT: rho a = (144/Ra)*(Pa/(459.67+T) 
=Dry Air rho IN: rho a = (144/Ra)*(Pa/(459.67+T) 
=Dry Bulb T IN: T=Outlet Air Flow: V =Rv =Ra =14.315 psia Inlet Air Flow 117.83 F 27779 acfm 0.020273629 0.451874527 psia 85.778 (ft-lbf)/(Ibm-R) 53.352 (ft-lbf)/(Ibm-R) 13.86312547 psia 0.0648 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 26400 cfm Calculation No. 97-199 Revision No. BOO Attachment c Page No. _c, of cl.
CornEd CALCULATION NO.97-199 REVISION NO. BOO PAGE NO. D1 of D10 Attachment "D" Proto-Hx Calc. Report for 1(2)VY03A (CSCS=1041F 
@ Design FF, 10% Reduced Airflow)II E-FORM I 16:07:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 04/24/02 ComEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03@104 F, 5%PLUG, 10%REDUCED Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 31,066.00 acfm 180.00 gpm Inlet Dry Bulb Temp 150.00 OF 105.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature 108.80 OF 117.70 OF Outlet Wet Bulb Temp 84.00 OF Outlet Relative Humidity %Tube Fluid Name Fresh Water Tube Fouling Factor 0.001500 Air-Side Fouling 0.000000 Design Heat Transfer (BTU/hr) 1,108,000 Atmospheric Pressure 14.315 Sensible Heat Ratio 1.00 Performance Factor (% Reduction) 0.000 Heat Exchanger Type Counter Flow Fin Type Circular Fins Fin Configuration LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in) 108.000 Fin Pitch (Fins/Inch) 10.000 Fin Conductivity (BTU/hr.-ft-F) 128.000 Fin Tip Thickness (inches) 0.0120 Fin Root Thickness (inches) 0.0120 Circular Fin Height (inches) 1.452 Number of Coils Per Unit 2 Number of Tube Rows 10 Number of Tubes Per Row 24.00 Active Tubes Per Row 23.00 Tube Inside Diameter (in) 0.5270 Tube Outside Diameter (in) 0.6250 Longitudinal Tube Pitch (in) 1.400 Transverse Tube Pitch (in) 1.410 Number of Serpentines 1.000 Tube Wall Conductivity (BTU/hrlft-&deg;F) 225.00 Calculation No. 97-199 Revision No. BOO Attachment
__Page No. n of o_,
16:07:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/24/02 ComEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03@104 F, 5%PLUG, 10%REDUCED Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfim)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (&deg;F)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfm) 25,210.00 Tube Inlet Temp (IF) 104.00 Air Inlet Temp (IF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (IF) 0.00 Atmospheric Pressure 14.315 Calctlation No. 97-199 Revision No. BOO Attachment b Page No. Dy of 16:07:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03@104 F, 5%PLUG, 10%REDUCED 04/24/02 M Extrapolation Calculation Summary II IL _ I I Air-Side Mass Flow (ibm/hr) 93,159.45 Inlet Temperature 
(&deg;F) 148.00 Outlet Temperature (0 F) 113.05 Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Visc (Ibm/ftrhr)
Density (Ibm/fl 3)Cp (BTU/lbm 0'F)K (BTU/hr-ft'&deg;F)
Tube-Side 36,020.13 104.00 126.64 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr.ft2.&deg;F)
Tube Wall Resistance (hr- ft 2.F/BTU'Overall Fouling (hr-ft 2-&deg;F/BTU)U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 2650655==
10,093.49 814,593 814,593 kv, Extrapolation Calculation for Row l(Dry)II Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ftrhr)
Density (Ibm/fl 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 93,159.45 148.00 142.95 0.0203 0.0203 145.47 130.56 3,937.64 878**0.7253 0.0491 0.0621 0.2402 0.0163 Tube-Side 36,020.13 123.37 126.64 125.01 127.41 2.33 17,663 3.4543 1.2853 1.2576 61.6324 0.9989 0.3717 Tube-Side hi (BTU/hrft 2.&deg;F) 865.61 j Factor 0.0073 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.52 Tube Wall Resistance (hr-ft 2.&deg;F/BTU, 0.00029413 Overall Fouling (hr-ft 2.F/BTU) 0.02650655 U Overall (BTU/hr-ft 2 -F)Effective Area (Wt 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.74 1,009.35 20.32 117,794 0.9248 117,794** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachnment Page No. _ of D,,-** Air Mass Velocity (Lbriihr-ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 16:07:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03@ 104 F, 5%PLUG, 10%REDUCED 04/24/02 a'Extrapolation Calculation for Row 2(Dry)II it -1 Air-Side 93,159.45 Tube-Side 36,020.13 Mass Flow (lbm/hr)Inlet Temperature 
('F)Outlet Temperature 
('F)Inlet Specific Humidity Outlet Specific Humidity Average Temp ("F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft hr)Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr'ft'&deg;F) 142.95 138.33 0.0203 0.0203 140.64 126.98 3,937.64 883**0.7258 0.0488 120.38 123.37 121.87 124.10 2.33 17,160 3.5652 1.3230 1.2960 61.6824 0.9988 0.3707 Tube-Side hi (BTU/hr.fl 2.&deg;F) 852.29 j Factor 0.0073 Air-Side ho (BTU/hr'ftl 2"F) 8.50 Tube Wall Resistance (hr ft 2.&deg;F/BTU , 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft')LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.72 1,009.35 18.63 107,614 0.9250 107,614 0.0626 0.2402 0.0161** Reynolds Number Outside Range of Equation Applicability L\W. .Extrapolation Calculation for Row 3(Dry)II I.Mass Flow (lbmrhr)Inlet Temperature 
("F)Outlet Temperature 
("F)Inlet Specific Humidity, Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
("F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbrn/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/fl 3)Cp (BTU/lbm'&deg;F)
K (BTUihr.ft.&deg;F)
Air-Side 93,159.45 138.33 134.11 0.0203 0.0203 136.22 123.71 3,937.64 888*4 0.7262 0.0485 0.0630 0.2402 0.0160 Tube-Side 36,020.13 117.65 120.38 119.01 121.08 2.33 16,704 3.6718 1.3591 1.3329 61.7269 0.9988 0.3697 Tube-Side hi (BTU/hr-ft 2"&deg;F) 840.07 j Factor 0.0072 Air-Side ho (BTU/hr-ft 2-&deg;F) 8.48 Tube Wall Resistance (hr-ft2-&deg;F/BTU, 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.70 1,009.35 17.09 98,368 0.9252 98,368** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment 0 Page No. 1)5 of b.*** Air Mass Velocity (Lbm/hr'ft'), rTube Fluid Velocity (ft/sec):
Air Density at Inlet [, Other Properties at Average Tr 16:07:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03@104 F, 5%PLUG, 10%REDUCED 04/24/02 W I Extrapolation Calculation for Row 4(Dry)II I. *1 Air-Side Mass Flow (lbm/hr) 93,159.45 Inlet Temperature (0 F) 134.11 Outlet Temperature (0 F) 130.25 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp ('F) 132.18 Skin Temperature (0 F) 120.71 Velocity *** 3,937.64 Reynold's Number 893**Prandtl Number 0.7265 Bulk Visc (Ibm/ft hr) 0.0483 Skin Visc (Ibm/ft-hr)
Density (ibmn/fl 3) 0.0634 Cp (BTU/Ibm-0 F) 0.2402 K (BTU/hr'ft-'F) 0.0160 Tube-Side 36,020.13 115.14 117.65 116.39 118.31 2.32 16,291 3.7740 1.3935 1.3682 61.7667 0.9988 0.3688 Tube-Side hi (BTU/hr.fl 2.0 F) 828.84 j Factor 0.0072 Air-Side ho (BTU/hr-ft 2-F) 8.46 Tube Wall Resistance (hr ftl 2-F/BTU' 0.00029413 Overall Fouling (hr-ft 2'-F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.69 1,009.35 15.68 89,961 0.9253 89,961** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)II I-Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ftrhr)
Density (lbm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr'ft-&deg;F)
Air-Side 93,159.45 130.25 126.71 0.0203 0.0203 128.48 117.97 3,937.64 897**0.7268 0.0480 0.0638 0.2402 0.0159 Tube-Side 36,020.13 112.86 115.14 114.00 115.77 2.32 15,917 3.8715 1.4263 1.4019 61.8023 0.9988 0.3680 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft 2-&deg;F)Tube Wall Resistance (hr-ftl 2.F/BTU.Overall Fouling (hr-ft 2-&deg;F/BTU)U Overall (BTU/hr-ft2.'F)
Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)818.54 0.0072 8.44 0.00029413

==0.0 2650655==
5.67 1,009.35 14.38 82,310 0.9254 82,310** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment
_k Page No. D&#xfd; of pi.;*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 16:07:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03@104 F, 5%PLUG, 10%REDUCED 04/24/02 Extrapolation Calculation for Row 6(Dry)II 1.3 Air-Side Mass Flow (lbm/hr) 93,159.45 Inlet Temperature (OF) 126.71 Outlet Temperature (OF) 123.48 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 125.10 Skin Temperature (OF) 115.46 Velocity *** 3,937.64 Reynold's Number 901 **Prandtl Number 0.7270 Bulk Visc (ibm/ft-hr) 0.0478 Skin Visc (lbm/ft-hr)
Density (Ibm/fl 3) 0.0642 Cp (BTU/lbm-'F) 0.2402 K (BTU/hr'ft-PF) 0.0158 Tube-Side 36,020.13 110.76 112.86 111.81 113.45 2.32 15,577 3.9644 1.4574 1.4340 61.8342 0.9988 0.3672 Tube-Side hi (BTU/hr-ft2-&deg;F) 809.07 j Factor 0.0072 Air-Side ho (BTU/hr ft2.&deg;F) 8.43 Tube Wall Resistance (hr-ft 2.&deg;F/BTU' 0.00029413 Overall Fouling (hrft 2-&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.66 1,009.35 13.20 75,343 0.9255 75,343** Reynolds Number Outside Range of Equation Applicability x~,r Extrapolation Calculation for Row 7(Dry)II I. *1 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number-Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft'hr)
Density (lbm/ft 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft-&deg;F)
Air-Side 93,159.45 123.48 120.52 0.0203 0.0203 122.00 113.17 3,937.64 905"-0.7273 0.0476 0.0645 0.2402 0.0157 Tube-Side 36,020.13 108.84 110.76 109.80 111.32 2.32 15,268 4.0527 1.4870 1.4645 61.8628 0.9988 0.3665 Tube-Side hi (BTU/hr-ft 2.F) 800.38 j Factor 0.0072 Air-Side ho (BTU/hr-fVl-&deg;F) 8.41 Tube Wall Resistance (hr-ft 2-&deg;F/BTU, 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.64 1,009.35 12.12 68,993 0.9257 68,993** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment
_Page No. D of _kL,*** Air Mass Velocity (Lbmn/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 16:07:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03@104 F, 5%PLUG, I0%REDUCED 04/24/02 Extrapolation Calculation for Row 8(Dry)II I. -__I Air-Side Tube-Side Mass Flow (lbm/hr) 93,159.45 36,020.1.Inlet Temperature (0 F) 120.52 107.0 Outlet Temperature (OF) 117.81 108.8, Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 119.17 107.9 Skin Temperature (OF) 111.06 109.3 Velocity *** 3,937.64 2.3: Reynold's Number 908** 14,98i Prandtl Number 0.7275 4.136: Bulk Visc (Ibm/ftrhr) 0.0474 1.514'Skin Visc (lbmr/fthr) 1.493, Density (lbmnft 3) 0.0648 61.888 Cp (BTU/lbm-'F) 0.2402 0.998'K (BTU/ihr-ft-F) 0.0157 0.3651** Reynolds Number Outside Range of Equation Applicability 3 9 4 7 7 2 6 5 9 4 5 9 8 Tube-Side hi (BTU/hr.ft2-&deg;F) 792.39 j Factor 0.0072 Air-Side ho (BTU/hr.ft 2 l-F) 8.40 Tube Wall Resistance (hr-ft2-0 F/BTU, 0.00029413 Overall Fouling (hr-ft 2-'F/BTU) 0.02650655 U Overall (BTU/hr.ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.63 1,009.35 11.12 63,202 0.9258 63,202'WI. .1 Extrapolation Calculation for Row 9(Dry)II Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbmi/ft)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 93,159.45 117.81 115.32 0.0203 0.0203 116.57 109.13 3,937.64 911*0.7276 0.0473 0.0651 0.2402 0.0156 Tube-Side 36,020.13 105.48 107.09 106.28 107.58 2.32 14,730 4.2-156 1.5412 1.5208 61.9116 0.9989 0.3652 Tube-Side hi (BTU/hr-ft2-&deg;F) 785.06 j Factor 0.0072 Air-Side ho (BTU/hr.ft 2-F) 8.39 Tube Wall Resistance (hr-ft2-&deg;F/BTU, 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr.ft 2 .F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.62 1,009.35 10.22 57,917 0.9258 57,917** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment D Page No. D),Y of t)/-*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 16:07:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils VY03@104 F, 5%PLUG, 10%REDUCED 04/24/02 Extrapolation Calculation for Row 10(Dry)Mass Flow (lbmlhr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftfhr)
Skin Visc (Ibm/ftdhr)
Density (ibm/fl 3)Cp (BTU/lbm-'F)
K (BTU/hr'f1'&deg;F)
Air-Side 93,159.45 115.32 113.05 0.0203 0.0203 114.18 107.36 3,937.64 914**0.7278 0.0471 0.0653 0.2402 0.0156 Tube-Side 36,020.13 104.00 105.48 104.74 105.94 2.32 14,497 4.2904 1.5660 1.5466 61.9325 0.9989 0.3646 Tube-Side hi (BTU/hr-ft 2.&deg;F) 778.32 j Factor 0.0072 Air-Side ho (BTU/hr-ft 2.-F) 8.38 Tube Wall Resistance (hr-ft 2 1-F/BTU, 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr.ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.61 1,009.35 9.38 53,090 0.9259 53,090** Reynolds Number Outside Range of Equation Applicability Calculation No. 97-199 Revision No. BOO Attachment D Page No. DI of jj.Air Mass Velocity (Lbmihr-tV).
Tube Fluid Velocity (ft/sec);
Air Density at Inlet 'r, Other Properties at Average T Inlet Air Flowrate Calculator 
-1 (2)VY03A Total P: P=Dry Bulb T OUT: T=Specific Hum.: W =H20 Vap P: Pv = (W*Rv*PY(Ra+(W'Rv) 
=Dry Air P: Pa = P -Pv =Dry Air rho OUT: rho a = (144/Ra)*(Pa/(459.67+T) 
=Dry Air rho IN: rho a = (144/Ra)*(Pa/(459.67+T) 
=Dry Bulb T IN: T=Outlet Air Flow: V =Rv =Ra =14.315 psia Inlet Air Flow 113.05 F 25210 acfm 0.020273629 0.451874527 psia 85.778 (ft-lbf)/(Ibm-R) 53.352 (ft-lbf)/(Ibm-R) 13.86312547 psia 0.0653 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 23760 cfm Calculation No. 97-199 Revision No. BOO Attachment D Page No. D),o of D1, Commonwealth Edison Company Nuclear Operations Division NEP-12-02LA Revision 4 LASALLE CALCULATION SITE APPENDIX -LASALLE SITE CALCULATION TITLE PAGE PAGE NO. i Go iEd CALCULATION NO: 97-199 DESCRIPTION CODE (C018):M03 LASALLE STATION DISCIPLINE CODE (CO 1I): M SUnit I ] Unit 2 '- Unit 0 SYSTEM CODE (C01 1): VY ELEVATION (C016): TITLE: VY Cooler Thermal Performance Model -1(2) VY03ASafety Related M Regulatory Related [] Augmented Quality [] Non-Safety Related REFERENCE NUMBERS: (COII Panel)Type Number Type Number AEDV CHRN PAL PROG PROJ ID COMPONENT EPN: (C014 Panel) DOCUMENT NUMBERS: (C012 Panel)EPN Component Doc Sub Document Number Assoc.Type Type Type Calc.1(2) VY03A Hi5 [9 __ _ -o , Yes] No E"'] Yes:] No YeC No____ ___ ____ ___ ____ _ _ ____ ___ __ _ ___ ____ ___ __ ] Yesfj No REMARKS: REV. REVISING APPROVED DATE NO. ORGANIZATION B B ry~s'n Commonwealth Edison Company NEP-12-02LA Nuclear Operations Division Revision 4 LASALLE CALCULATION SITE APPENDIX -LASALLE SITE List of Attachments (cont.)CALCULATION NO. 97-199 Project No: PAGE NO. ii REVISION SUMMARIES REV: 13 ]Pand (Only RP.iN Pags hIlkd) []cr"] ip (All C.kaiwatiun Pa&#xfd;pi h REVISION 

==SUMMARY==
, Calculation revised to add additional sensitivity computer runs to assess effect of reduced inlet air flow rates on the total heat lIja transferred.
V rVp,. , ,% &,,,, I ,,v , ' V .W ", 4? AlSl O4Itkd*iwi 
..- P v , /a d c'd.Electronic Calculation Data Files: iProgram Verion. File nrame min)Electronic File Date for Rev. A of this Calculation is still valid, no new files are applicable.
Prepared by: Brian L. Davenport
_-- .Print 'ign Date Reviewed by: UOtearw %<? ,'--.. 92. 2 /Y- Z2 Print Sign Date Type of Review: 0 Detailed [] Alternate 
'Test Supplemental R i re" [d YES (NEP-12-05 documentation attached) NO.Wpervisor DO ANY ASSUMTNS INTII S CALCUAlON RFWRE LA R VERIFICATION 
[]YES NO Tracked by: REV: r-' PbrW (Orly Re.-%W Pap l d) -]Ca-PbM Irfded)REVISION 

==SUMMARY==
: Electronic Calculation Data Files: (Program Name. Vctllum. File name exwhsize'dat'hiouv:
mini Prepared by: Print Sign Date Reviewed by: Print Sign Date Type of Review% ] Detailed Alernatest Supplemental Review Required YES (NEP-12-05 documentation attached)
NO Supervisor.fANY A-SSMPTIONS IN 11 US CAWLIIATION REQ)URE LAITR VFRIHCMTIOCN 
[ YES [N.rackcd by:
PROTO-POWVER CORPORATION CALCULATION TITLE SHEET Commonwealth Edison CLIENT: PROJECT: LaSalle Station GL 89-13 Heat Exchanger Testing Program CALCULATION TITLE: CALCULATION NO.: VY Cooler Thermal Performance Model -- 1(2)VY03A 97-199 FILE NO.: 31-003 COMPUTER CODE & VERSION (if applicable):
PROTO-HX T M , Version 3.01 REV TOTAL NO. OF ORIGINATOR/DATE VERIFIER/DATE APPROVAL/DATE PAGES A 203 Lloyd Philpot /Mendboye 7/ / " V Pa~ H- a Form No.: P1050101 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALCNO. 97-199 REv A PAG&#xfd;E..&#xfd;'-'
GROTON, CONNECTICUT ORIGINATOR L. Philpot IDATE 7/7/98 VERIFIED 3Y M. Aboye J013 NO. 31-003 CLIENT Commonwealth Edison PROJIET LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I(2)VY03A Revision History Revision Revision Description A Original Issue Form No.: P1050102 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO. 97_199 [REVA PAGE .4 frD#.GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED RY M. Aboye JOB No. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A CALCULATION VERIFICATION FORM REVIEW METHOD: EXTENT OF VERIFICATION:
Approach Checked: N/A Ej Complete Calculation:
9 Logic Checked: [7 N/A []Arithmetic Checked: N/A ED Revised areas only: El Alternate Method El N/A (Attach Brief Summary)Computer Program Used El N/A g Other (describe below): Q](Attach Listing)Other N/A [-*Errors Detected *Error Resolution
*Other Comments*Extra References Used*(Attach extra sheets if needed)CALCULATION FOUND TO BE VALID AND SCORRECT AND REASONABLE:
IDV Signature:
pr.-. Initials: fA-Printed Name: h 6 P. -X t AP-S vi 6-Date: -1 -I'S Form No.: P1050103 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION cAcNo. 97-199 REV A PAGE-i'"Q b GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERiFIED fY M. Aboye 10o so 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VY03A TABLE OF CONTENTS C A LC U LA T IO N T IT L E SH EET .................................................................................................
i C A LC U LA T IO N R EV ISIO N H IST O RY ...................................................................................
ii C A LC U LA TIO N V ER IFIC A TIO N SH E ET .............................................................................
iii TA BLE O F C O N TEN TS .............................................................................................................
iv LIST O F A TTA C H M EN TS ........................................................................................................
vi Total Number of Pages in Preface of Calculation:
6 1. PU R PO SE ...................................................................................................................................
1 2. BA C K G R O U N D ........................................................................................................................
1 3. D ESIG N IN PU TS ......................................................................................................................
2 4. A PPR O A C H ...............................................................................................................................
5 5. A SSU M PTIO N S .........................................................................................................................
5 6. A N AL Y SIS .................................................................................................................................
6 S6.1 Tube Pitch ..........................................................................................................................................
6 6.2 Coill Configuration 
.............................................................................................................................
6 6.3 Sensible Heat Ratio ............................................................................................................................
7 6.4 Derivation of Benchm arking Inputs ..............................................................................................
7 6.5 M odel Benchm arking .......................................................................................................................
10 6.6 Effective Coil Finned Length .....................................................................................................
14 6.7 Extrapolation Conditions 
.................................................................................................................
14 6.8 Therm al M argin Assessm ent .......................................................................................................
16 6.9 Lim iting Cooling W ater Flow Analysis .....................................................................................
17 6.10 Im pact of M issing Fins ..................................................................................................................
17 6.11 Fouling Sensitivity Analysis .....................................................................................................
18 7. RE SU LT S .................................................................................................................................
18 7.1 M odel Benchm arking .......................................................................................................................
18 7.2 Cooler Therm al M argin Results ...................................................................................................
19 7.3 Lim iting Cooling W ater Flow Rate Analysis ............................................................................
20 7.4 Impact of M issing Fins ....................................................................................................................
21 7.5 Fouling Sensitivity Analysis ........................................................................................ 
....... 21 Form No.: P1050104 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 V*Li OF PROTO-POWER CORPORATION CALCNO.97199 REV A PAGE -O GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye1 JOB NO 31-003 CLIENT Commonwealth Edison PROJEcT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A 8. C O N C L U SIO N S ......................................................................................................................
22 9. R EFER EN C ES .........................................................................................................................
22 24 Total Number of Pages in Body of Calculation:
Form No.: P1050104 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 Vi', O Ix PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE I, +GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLE[NT Commonwealth Edison ROJEC' LaSalle Station GL 89-13 Heat Exchanger TestingVY Cooler Thermal Performance Model -- I(2)VY03A LIST OF ATTACHMENTS Attachment Subject Matter Total Pages A Attachment A to Proto-Power Calculation 97-199 Rev. A: 11 Design Input Data -- Selected References B Attachment B to Proto-Power Calculation 97-199 Rev. A: 2 Cooler Inspection Photographs 
-- IVY03A C Attachment C to Proto-Power Calculation 97-199 Rev. A: 9 PROTO-HXTM Reports -- Initial Benchmark Case D Attachment D to Proto-Power Calculation 97-199 Rev. A: 2 Excerpt from Compact Heat Exchangers, Kays and London E Attachment E to Proto-Power Calculation 97-199 Rev. A: 17 PROTO-HXTm Reports -- Final Benchmark Case F Attachment F to Proto-Power Calculation 97-199 Rev. A: 9 PROTO-HXTm Reports -- Thermal Margin Assessment (Clean)G Attachment G to Proto-Power Calculation 97-199 Rev. A: 9 PROTO-HXrm Reports -- Thermal Margin Assessment (Service)H Attachment H to Proto-Power Calculation 97-199 Rev. A: 18 Derivation of Moist Air Properties I Attachment I to Proto-Power Calculation 97-199 Rev. A: 25 PROTO-HXTlm Reports -- Limiting Flow Analysis J Attachment J to Proto-Power Calculation 97-199 Rev. A: 43 PROTO-HXTM Analytical Uncertainty Analysis K Attachment K to Proto-Power Calculation 97-199 Rev. A: 4 Comparing Surface Areas of Spiral and Circular Fins L Attachment L to Proto-Power Calculation 97-199 Rev. A: 5 Walkdown Data for Coil Physical Dimensions M Attachment M to Proto-Power Calculation 97-199 Rev. A: 17 PROTO-HXTM Reports -- Fouling Sensitivity Analysis N Attachment N to Proto-Power Calculation 97-199 Rev. A: 2 PROTO-HXTM Model Database Disk (plus disk)""1" .... C..aklatun.iI (total ItuIHuLLt ot p.agcoI. 203 .Form No.: P1050104 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 Commonwealth Edison Company Nuclear Operations Division NEP-12-02LA Revision 4 LASALLE CALCULATION SITE APPENDIX -LASALLE SITE 0List of Attachments (cont.)____ ___ ___ ___ ____ ___ ___ ___ ____ ___ ___ ___ ____ ___ ___ ___ ___ Project No: CALCULATION NO. 97-199 REV. NO. B PAGE NO. ix of ix ATTACHMENTS SUBJECT MATTER TOTAL PAGES 0,k,,. (not used) P .Y\ P Attachment P. to Calculation 97-199, Rev. B.Sensitivity Computer Runs for Reduced Inlet Air 28 Flow Rates \ * *'-'&#xa2;'
PROTO-POWER CORPORATION CALCNO. 97- 199 REV A PAGE 1 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJIE- LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A 1. PURPOSE The purpose of this calculation is to develop a thermal performance analysis model for the Commonwealth Edison (ComEd) LaSalle Station SE cubicle area coolers I (2)VY03A.
This model can be used for the analysis of heat exchanger thermal performance test data as part of the LaSalle Station GL 89-13 heat exchanger testing program or for any other engineering analysis subject to the limitations itemized at the end of this section.Once developed, the model is used to identify the thermal margin of the heat exchanger at specified performance conditions as follows: " at LaSalle Station Reference Conditions as currently defined in the LaSalle Station design and licensing basis; and" at lower service water flow rates (with increased fouling) to support service water system re-balancing efforts.The thermal performance model documented in this calculation has been created and used with PROTO-HX, Version 3.01. The model can be used with previous versions of PROTO-HX and produce identical results as long as the following restriction is upheld:* Air coils analyzed in Version 3.0 or earlier can be analyzed only in non-condensing modes of operation.
Current limitations of use for PROTO-HX are established by the limits on fluid properties included within the software.
Fluid properties contained within PROTO-HX are currently limited to the following temperature ranges:* Air: 32-320&deg;F* Water: 32-5007F 2. BACKGROUND LaSalle Station is in the process of implementing a heat exchanger thermal performance monitoring program and a service water system flow balancing program in response to the requirements of NRC Generic Letter 89-13. Development of an analytical model in PROTO-HXTM, Version 3.01, will allow timely analysis of data resulting from the test program and will ensure the limiting flow requirements for the coolers are adequately defined.
PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 2 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB No 31-003 CLIEN Commonwealth Edison PROJECr LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A 3. DESIGN INPUTS The thermal performance model is developed using PROTO-HX T M , Version 3.01. PROTO-HX T M was developed and validated in accordance with Proto-Power's Nuclear Software Quality Assurance Program (SQAP). This program meets the requirements of 10CFR50 Appendix B, I OCFR2 1, and ANSI NQA- 1, and was developed in accordance with the guidelines and standards contained in ANSIIIEEE Standard 730/1984 and ANSI NQA-2b-1991.
PROTO-HXI T M Version 3.01 was verified and approved for use as documented in Reference (1).The design inputs for this calculation consist of the heat exchanger design basis performance requirements (Tablel), performance specifications (Table 2) and construction details (Table 3)provided by the heat exchanger manufacturer data sheet (Attachment A) or other design documents as referenced.
Construction details give the necessary information for model construction while performance specifications are used to benchmark the model.VY cooler thermal performance in this calculation will be. assessed only with respect to the nominal accident conditions (i.e., design basis LOCA) with no tubes plugged. Condensing modes of operation and tube plugging margins are not addressed.
Table 1: LaSalle Station Reference Conditions Parameter Value Reference*
Heat Rate -- 1(2)VYOI3A (BTU/hr) 722,217 2 Atmospheric Pressure (in-w.g.) 
-0.4 4 Air-Side Inlet Temperature 
-- Dry Bulb (&deg;F) 148 4 Fan Volumetric Flow Rate (cfm) 26,400 18,19 Tube-Side Flow Rate (gpm) 180 5 Tube-Side Inlet Temperature 
(&deg;F) 100 6*Selected references included as Attachmuent A
PROTO-POWER CORPORATION CALCNO. 97-199 REv A PAGE 3 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB No 31-003 CLIENT Commonwealth Edison PROJEcT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A Table 2: Vendor Specified Performance Parameter Value Reference*
Air-Side Fouling Factor (Design) 0 Assumption (1)Air-Side Entering Fluid Flow Rate (scfm) 25,420 7 Air-Side Inlet Dry Bulb Temperature (OF) 150 7 Air-Side Inlet Wet Bulb Temperature (OF) 92 7 Air-Side Outlet Dry Bulb Temperature 
(&deg;F) 108.8 7 Air-Side Outlet Wet Bulb Temperature (OF) 84.0 7 Tube Side Fouling Factor (Design) 0.0015 8 Tube Side Fluid Type Service Water (Fresh) 9,10 Tube Side Fluid Flow Rate, Total (gpm) 180 7 Tube Side Inlet Temperature (OF) 105 7 Tube Side Outlet Temperature (OF) 117.7 7 Design Q (BTU/hr) 1,108,000 7*Selected references included as Attachment A
PROTO-POWER CORPORATION CALCNO. 97-199 REV A PAGE 4 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye Jo1 No. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VY03A Table 3: Construction Details Parameter Value Reference")
Heat Exchanger Type and relative direction of Tube- Carrier Air Coil 7,11 side and Air flow. Counter flow Fin Type Spiral 7,8 Coil Finned Length (in) 111.00 -- specified (2) 7 108.00 -- effective (2) (4) 20 Fin Pitch (fins/in) 10.0 7 Fin Material ASTM B209 Aluminum 7 Fin Conductivity (BTU/hr-ft-&deg;F) 128 16 Fin Thickness (in) 0.012 7 Fin Height (in) 1.452 20 Number of Coils per Unit 2 7 Number of Tube Rows 10 7 Number of Tubes per Row 24 7 Number of Plugged Tubes 0 Tube Outside Diameter (in) 0.625 (3) 7 Tube Wall Thickness (in) 0.049 7 Tube Inside Diameter (in) 0.527 7 Longitudinal (horizontal)
Tube Pitch (in) Unavailable 
-see Section 6 -Transverse (vertical)
Tube Pitch (in) 1.410 20 Tube Layout Staggered 20 Number of Serpentines 1 (i.e., "Full Circuiting")
7 Tube Wall Material SB75 Copper 7 Tube Wall Conductivity (BTU/hr-ft-&deg;F) 225 12 Sensible Heat Ratio I (Section 6.3)Notes: (I) Selected references included as Attachment A (2) The Reference (7) coil finned length will be used for benchmarking to vendor performance data per Section 6.0. The Reference (20) effective coil finned length will be used for all subsequent analyses.(3) The Reference (7) tube OD is within the tolerance of Reference (20) and will be used in lieu of the Reference (20) value.(4) Two tubes in the first row of I VY03A are missing fins over a tube length of 5 1/4" per Reference (3) (addressed in Section 6.10).
PROTO-POWER CORPORATION CALC NO- 97-199 REV A PAGE 5 OF 24 GROTON, CONNECTICUT ORUGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JO0 NO 31-003 CLIENT Commonwealth Edison r'ROJEcT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A 4. APPROACH This calculation utilizes plant/vendor fabrication specifications provided in Section 3.0 to develop a thermal performance prediction model for the 1(2)VY03A cooler. The calculation then benchmarks the model by comparing the heat transfer rate calculated by PROTO-HXTM Version 3.01 with the manufacturer's specifications for thermal performance.
The Colburn j-factor vs. Reynolds Number relationship is adjusted as necessary to meet the manufacturer's performance specifications.
After the model is benchmarked, it will be used to determine the margin between the available and required heat removal rates and to establish a revised limiting flow rate in support of service. water system re-balancing efforts.5. ASSUMPTIONS
: 1. The fouling factor specified in Reference (8) is for the tube-side only and design air-side fouling is zero. This is typical for air coils of this type and application.
Future validation of this assumption is not required.2. The slope of the "Colburn j-factor vs. Reynolds Number" curve is the same for the current coil and the standard coil represented by curve "CF-9.05-3/4 J-A" in the PROTO-HXTM "h-configurations" Library. This assumption is based on physical similarities between the VY coolers and the standard configuration represented by "CF-9.05-3/4 J-A" as elaborated in Section 6, below. The model benchmarking process described in Section 6 brings the model into precise agreement with the vendor performance data making initial configuration selection immaterial.
The only difference caused by initial configuration selection that would be detectable in analysis results is when analyses are performed over a very wide range (orders of magnitude) of air-side Reynolds numbers. A wide range of Reynolds numbers causes the slight variation in slopes of the j-factor equations of different configurations to become more obvious. Given the fixed fan flow rate and a relatively tight band of normal operating and Reference conditions, along with the fact that benchmarking conditions are extremely close to Reference conditions, such wide variations in Reynolds numbers are not anticipated.
Future validation of this assumption is not required.3. The vendor-supplied performance specifications of Reference (7) (included as Attachment A) are considered to be an accurate reflection of the as-built performance of the cooler. Future validation of this assumption is not required.4. The VY cooler spiral fin geometry is closely approximated by the PROTO-HXTM circular fin configuration.
This is due to the relatively tight fin pitch configuration resulting in a PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 6 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A negligible difference in fin/tube outside surface area. This assumption is supported in Attachment K. Future validation of this assumption is not required.5. In transitioning from the original vendor specified inlet air temperature of 150&deg;F to the current licensing limit of 148&deg;F, the inlet air vapor density is assumed to have remained unchanged.
This increases the inlet relative humidity causing a slight reduction in the air mass flow rate. Future validation of this assumption is not required.6. ANALYSIS 6.1 Tube Pitch The longitudinal (horizontal) tube pitch is not directly available from the coil data sheet or Reference (20). It can be estimated based on the geometry of the coil. Per Reference (7), the coil stack depth is 14.00 inches. Dividing the stack depth evenly between 10 tube rows yields a longitudinal (horizontal) tube pitch of 1.400 inches.6.2 Coil Configuration The coil configuration for modeling cooler 1(2)VY03A is selected based on the physical characteristics of the coil. There are no coils in the PROTO-HXTM library that exactly match the configuration of cooler 1(2)VY03A.
The configuration "CF-9.05-3/4 J-A" shown in Figure 1 provides the closest match based on similarities of layout geometry:
staggered tube rows, identical fin thickness, similar fin height and similar fin pitch. The "CF-9.05-3/4 J-A" configuration also represents a relatively compact coil which correlates well to the VY coils as evidenced in the coil photographs included as Attachment B.PROTO-HXTM does not include spiral fin configurations in the analytical methodology employed.
However, for the given fin pitch, the difference in calculated fin surface area between the VY cooler spiral fin configuration and the PROTO-HXTM1 circular fin configuration is negligible.
The negligible difference is illustrated further in Attachment K using a simplified area comparison.
PROTO-POWER CORPORATION CALC NO. 97-199 REv A PAGE 7 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB No.31-003 CLIENT Commonwealth Edison IROJECt LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I(2)VY03A Fizure I Coil Confiuuration CF-9.05-3/4 J-A a 1,463 wwww uo 77 4J Itt1W 111111111111111ll11 Ln 190.774A 1.75 CF-9,05- 2/4J-A 6.3 Sensible Heat Ratio The Sensible Heat Ratio (SHR) is used only when one of the "Constant Heat Load" calculation and/or extrapolation methods of PROTO-HXTM is used (i.e., "Constant Heat and Cold Inlet Temperature" or "Constant Heat and Hot Outlet Temperature").
The SHR can be assigned any value between 0 and 1 and represents the fraction of the total specified (constant) heat load that is due to sensible cooling alone. An input of 1.0 in the SHR field tells PROTO-HXTM that the specified constant heat is 100% sensible heat with no condensation occurring.
Use of any value less than 1.0 presumes some knowledge as to what fraction of the specified heat load is due to condensation (i.e., latent heat transfer).
The value of SHR currently in the model is 1.0, but like any other model input, the SHR can be changed at any time.6.4 Derivation of Benchmarking Inputs The PROTO-HXTM model is benchmarked using the performance data provided by the cooler manufacturer.
In order to benchmark the model, the vendor specified conditions must be converted into appropriate units for PROTO-HXTM input. The only input requiring adjustment is the specified air-side flow rate of 25,420 scfm. PROTO-HXTM requires air-side flow rate to be given at actual inlet air conditions (units of acfin).
PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 8 OF 24 GROTON, CONNECTICUT ORIGINAToR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB No. 31-003 CLIEN'T Commonwealth Edison PROJECt LaSalle Station GL 89-13 Heat Exchanger Testing T=rLE VY Cooler Thermal Performance Model -- 1(2)VY03A The correction of scfrn to acfin is made as follows (holding mass flow rate constant for the defining case):_(60rain.)
mi = (scfm) x (pP,,d) x&#xfd;f where:= (acfm) x (P,)60 min Slhr )Equation (1)rh = mass flow (lbm/hr)scfm = volumetric flow rate at standard conditions (ft 3/min)Psid = standard density of 0.075 lbm/fl 3 acfm = volumetric flow rate at specified (non-standard) conditions (ft 3/min)Pactu = density of dry air at specified inlet temperature and humidity (lbm/ft 3)Rearranging terms yields the following correction factor for converting scfm to inlet acfm: (acfm) = (scfm) x (Padual)Equation (2)Local Standard Atmospheric Pressure To derive the dry air density for the inlet air conditions, the amount of moisture in the air and the local atmospheric pressure must be accounted for. Per Reference (13), local atmospheric pressure was accounted for by specifying a flow at standard density (25,420 scfin) as well as an actual flow (26,400 acfmn at 70'F and 40% relative humidity at site elevation).
The difference between the two flow rates will provide the assumed air density as follows: (W f) =X(scfm) )(acfm-)-(25,420)0.07500 26,400 0.0722 1b 3 The local atmospheric pressure is found by iterative solution using Reference (14) as shown in Attachment H. Pressure input is varied with the specified temperature and humidity conditions held constant until a dry air density of 0.0722 Ibm/ft 3 is reached.
PROTO-POWER CORPORATION CALC NO. 97-199 V A PAGE 9 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot IDATE 7/7/98 VERIFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A-The result of the iterative process is as follows: Given per Reference (13)Dry Bulb Temperature:
Relative Humidity: 70.00&deg;F 40.00 %Derived above Dry Air Density: Derived per Attachment H Specific Humidity: Atmospheric Pressure: Dry Air Pressure: Vapor Pressure: Vapor Density: 0.07220 lbm/ftA3 0.00638 lbmv/lbma 14.3150 psia 14.1697 psia 0.1453 psia 0.00046 lbm/ftA3 The result is that an atmospheric pressure of 14.315 psia at 70'F and 40% relative humidity will give the requisite air density.Actual Air Flow Rate The next step is to define the actual air flow rate at the inlet conditions included by the vendor in the Reference (7) performance specification (Table 2). The moist air conditions corresponding to the vendor specified performance conditions are as follows: Given per Reference (7)Dry Bulb Temperature:
Wet Bulb Temperature:
Derived above Atmospheric Pressure: 150.00&deg;F 92.00&deg;F 14.315 psia Derived per Attachment H Relative Humidity: Specific Humidity: Dry Air Pressure: Vapor Pressure: Dry Air Density: Vapor Density: 12.18%0.02034 lbmv/lbma 13.8617 psia 0.4533 psia 0.06137 lbm/ftA3 0.001248 lbm/ftA3 PROTO-POWER CORPORATION CALC NO 97-199 REV A PAGE I0 OF 24 GROTON, CONNECTICUT ORIGIN "I'OR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A The actual volumetric flow rate at vendor specified inlet conditions is then calculated as: (acfm) = (scfm) x 'S"d) -(Pactuai)(25,420) x = 31,066 ftmm 0.06137 in Summary of PROTO-HXTM Inputs for Model Benchmarking Tube-Side Flow Rate Tube-Side Inlet Temperature Air-Side Flow Rate Air-Side Inlet Temperature 
-- Dry Bulb Air-Side Inlet Temperature 
-- Wet Bulb Atmospheric Pressure 180 gpm 105 0 F 31,066 acfm 150OF 92 0 F 14.315 psia 6.5 Model Benchmarking Model benchmarking is performed to compare thermal performance as predicted by the model to thermal performance specified by the cooler vendor. A significant impact on the model predicted performance is the outside (air-side) heat transfer coefficient.
The benchmarking process adjusts the model correlation for outside heat transfer coefficient to match vendor performance data.An extensive source of information pertaining to the outside heat transfer coefficient for air coolers is provided by Reference (15). This widely-recognized publication provides heat transfer correlations for specific coil configurations.
The format used in Reference (15), and subsequently adopted by other researchers, is to provide a plot of the Colbum j-factor vs. Reynolds Number for each configuration.
Alternatively, to permit modeling of coils which do not adequately fit the library configurations and for which no test data correlation is available, PROTO-HXTM allows the generation of a coil unique formulation for outside heat transfer coefficient.
This is done through establishing a unique Colburn j-factor for the coil.Reference (15) defines the Colburn j-factor as follows.Let: Cpa =Specific heat of air (Btu/Ibm-0 F)Thermal conductivity of air (Btulhr-ft-&deg;F)
PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 11 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot jI)ATE 7/7/98 VERIFIED BY M. Aboye Jo01 NO.31-003 CLIENT Commonwealth Edison FROIECt LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I(2)VY03A ma Absolute viscosity of air (lbm/fl-hr) ra = Density of air (lbJ/ft3)Amin= Minimum air-side flow area (in 2)Aj = Frontal Area (in 2)DH = Hydraulic diameter (fit)do= Tube outside diameter (in)i = Colburn j-Factor NC= Number of coils per unit NL = Number of active tube rows Qa = Specified air flow rate (acfin)SL = Longitudinal Tube Pitch (in)ST = Transverse Tube Pitch (in)The Prandtl Number for air, Pra (a dimensionless parameter), is given by: Pr, -Cpa Pa Equation (3)k., The mass flow rate of air per coil, Ma (ibn/hr), is calculated based on the input total air flow and the number of coils per unit: M 6 0-pQa Equation (4)Nc PROTO-POWER CORPORATION CACNO. 97-199 REV A PAGE 12 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JoB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A The bulk-stream mass flux, G (lbm / hr-ft 2), is: G= 144 M, AMIN Equation (5)The Colburn j-factor is defined in terms of the Stanton Number, Sta, as: 1=St. Pr.' C 0 Pr,'3 Equation (6)Therefore, the outside heat transfer coefficient, ho (ttu/hr-ft 2_oF), may be defined in terms of thej-factor:= I G cpa Pr,'Equation (7)Per Reference (15), the j-factor for the various coil configurations tested are provided as functions of the Reynolds Number based on hydraulic diameter, DH(in)::" =f(Re.)where: Re, G GDi'Jo Equation (8)The standard air-side configuration for coil type CF-9.05-3/4 J-A, provided in PROTO-HXTM's Library, was initially selected based on the physical similarities between the present coil and that represented by CF-9.05-3/4 J-A as described in Section 6.2. However, the heat transfer rate under design operating conditions using the standard configuration was slightly greater than the value specified by the manufacturer (see performance run in Attachment C). For this reason, a new curve relating the Colburn j-factor and Reynolds Number was generated according to the following procedure: " The slope of the linear standard curve was calculated." A new curve, parallel to the standard curve, was defined such that the new j-intercept is slightly lower.
PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 13 OF 24 GROTON, CONNECTICUT ORIGINA [OR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VY03A* A design performance run was then executed using the new Colburnj-factor versus Reynolds Number curve, and the resulting heat transfer rate was compared to the manufacturer's value.* The above two steps were repeated until the calculated heat transfer rate closely matched the manufacturer's value.The resulting relationship between Reynolds Number and Colburn j-Factor is represented by the following table and associated equation: Table 4: Reynolds Number and Colburn j-Factor Reynolds Number Colburn j-Factor (Standard)
Colburn j-Factor (Custom)1000 0.009 0.00695 8000 0.0044 0.00340 j = e[-2.5939 
-0.3438 *Ln(Re)]Equation (9)Equation (9) was added to the PROTO-HXTM Library for use in conjunction with Area Coolers 1(2)VY03A.
As noted in Assumption (2) and implemented above, the slope of the "Colbum j-factor vs.Reynolds Number" curve is assumed to be the same for cooler 1(2)VY03A and the standard coil represented by curve CF-9.05-3/4 J-A in the PROTO-HXTM "h-configurations" Library. This assumption is considered reasonable based on the following: " there are only minor variations in the slope of different j-factor correlations; and," there is only a slight variation in the air-side Reynolds Number between anticipated test conditions and the extrapolated accident conditions.
The only variation is expected to be caused by air inlet temperature variations (i.e., volumetric flow rate in cfm will be nearly constant, while air flow in acfm will vary with temperature and inlet humidity).
An excerpt from Reference (15), illustrating the j-factor relationship with Reynolds number, is included as Attachment D.
PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 14 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A 6.6 Effective Coil Finned Length Reference (20) identified the fact that the fined coil length exposed to air flow was less than that specified by the coil vendor in Reference (7). Model benchmarking used the vendor specified length to be consistent with the vendor specified performance.
The effective length is entered into the model after benchmarking to be used for all subsequent analysis.
An effective coil finned length of 108.00 inches is used per Reference (20).6.7 Extrapolation Conditions The LaSalle Station Reference Conditions defined in Table 1 are slightly different than the vendor specified performance conditions listed in Table 2 and require conversion to units for input into PROTO-HX T M.Air-Side Pressure Air-side pressure should account for the local elevation above sea level. Chapter 26, Table IA, of Reference (16) provides elevation and standard atmospheric pressure data for the local area around La Salle.Interpolating between data points to derive the pressure associated with the elevation of the VY coolers given by Reference (17) provides the following:
Elevation (feet above sea level)682 738 698 Pressure (psia)14.337 14.308 14.329 Reference (16)Reference (16)Interpolation between above points at VY elevation Per Reference (4), the coil pressure is -0.4 inches of water gauge. Using the density of water at 60'F, the specified pressure is calculated as illustrated below: Coil Pressure (inwg)-0.4 Water Density (lbm/ft 3)62.36445 Coil Pressure (psig)-0.014 Atm Pressure (psia)14.329 Coil Pressure (psia)14.315 This pressure matches the pressure derived from the original coil specification in Section 6.4.
PROTO-POWER CORPORATION CALCNO. 97-199 REV A PAGE 15 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thenrial Performance Model -- 1(2)VY03A Air-Side Flow Rate In order for PROTO-HXTM to calculate the air mass flow rate for a given extrapolation condition, the inlet dry bulb temperature, total pressure, and relative humidity or wet bulb temperature must be specified.
The inlet dry bulb temperature and pressure for the LaSalle Station Reference Conditions are listed in Table 1. The inlet relative humidity is adjusted by holding the vapor density constant from the vendor specified condition to the LaSalle Station Reference Condition (i.e., 148&deg;F in lieu of 150'F).Given per Section 6.4 Vapor Density: 0.001248 lbm/ftA3 Reference Condition Dry Bulb Temperature:
148.00 0 F Atmospheric Pressure:
14.315 psia Derived per Attachment H Wet Bulb Temperature:
91.6 0 F Relative Humidity:
12.76 %Since fans are constant volume equipment, the air volumetric flow rate of 26,400 cfm specified in References (18) and (19) remains the same for all coil outlet conditions.
The air mass flow rate through the coil, however, will vary with the temperature of the air going through the fan (i.e., at coil outlet temperature).
Deriving the inlet air flow rate for input to PROTO-HXTM requires an iterative solution as follows:* take an initial guess at the coil outlet air temperature at the same specific humidity as the coil inlet;* calculate the dry air density at the selected coil outlet air temperature;
* calculate the coil inlet air flow rate by multiplying the fan capacity (cfm) by the ratio of the coil outlet dry air density to the coil inlet dry air density (to maintain constant mass flow across the coil) [Equation (2)];* run the model with the inlet air flow rate derived above;* check the predicted coil outlet air temperature; and* repeat the process (substituting the predicted coil outlet air temperature for the initial guess)until the coil outlet air temperature does not change from one iteration to the next PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 16 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECr LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A The iteration process described above was completed twice for this model for a clean (f = 0.0)and service (f = design) condition with results as follows: Clean: (cfmi.) = (cfmo.0) x (pin)(0.066345159)
-(26,400) x = 28,445(Fan Temperature 
= 104.31)(0.061575103)
(0.066128241)
-(26,400) x ( 5 = 28,352 (Fan Temperature 
= 106.16)(0.061575103)
Service: (cfmin) =(cfmo&deg;,) x (Pin)Summary of PROTO-HXTM Inputs for Extrapolation to Reference Conditions The Extrapolation conditions are defined as the vendor data sheet conditions without high energy line break modified for ultimate heat sink temperature and room limiting temperature per the LaSalle Station UFSAR Reference (4).The required PROTO-HXTM inputs for these conditions are as follows: Tube-Side Flow Rate Tube-Side Inlet Temperature Air-Side Flow Rate Air-Side Inlet Temperature 
-- Dry Bulb Air-Side Inlet Humidity Atmospheric Pressure 180 gpm IOO&deg;F (varies with temperature) 148 0 F 12.76%14.315 psia 6.8 Thermal Margin Assessment The available thermal margin is defined as the difference between the available and the required heat removal rates at reference conditions.
The maximum available heat removal rate is calculated using the benchmarked PROTO-HXTM model and the inlet conditions defined in Section 6.7 with zero fouling. By comparing the available heat removal rate calculated with zero fouling (ce.~an) to the required heat removal rate, the maximum available margin is determined.
A similar comparison is made between the required heat load to the available heat load at design fouling conditions (qservice)"
PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 17 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED HY M. Aboye JOB No 31-003 CLIENT Commonwealth Edison PRIoECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A For the purposes of this thermal margin assessment, thermal margin is defined as follows: Margin (BTU / hr) = q available 
-q required Margin (%) q available q required x 100 q required Equation (10)Equation (11)where: qavailable 
= the predicted heat capacity of the cooler at the specified conditions (BTU/hr)qrequired 
= the heat capacity required of the cooler to fulfill design basis requirements (BTU/hr)6.9 Limiting Cooling Water Flow Analysis In support of the LaSalle Station efforts to re-balance the CSCS Equipment Cooling Water System, specification of a minimum acceptable cooling water flow to the VY coolers is desired.For conservatism, the design fouling factors associated with the limiting flow analysis are increased to 0.002 on both the tube and air sides of the cooler. Increasing the design fouling factors increases the fouling margin of the cooler at the reduced flow rates.Limiting flows are established by iterating with the performance model. The cooling water flow rate is incrementally reduced with each iteration until the target thermal margin of approximately 30% with the increased design fouling factors is achieved.6.10 Impact of Missing Fins Reference (3) identified the fact that two of the tubes in the front row of 1VY03A are missing fins for a tube length of 5.25 inches leaving an adjusted finned tube length of 102.75 inches.This reduces the heat transfer surface area for the first row. To assess the impact of this configuration, an additional iteration is made with the model. Since PROTO-HXTM does not allow the specification of different lengths by tube row, a comparison of the thermal performance capability of a coil with proper finned length to that of a coil with the adjusted finned length is required.
This is done by running the model with a revised value for coil finned length. The results of the PROTO-HXTM analysis of this configuration is then compared to the results with the effective coil finned length defined in Section 6.6. By focusing only on the heat transfer results tabulated for the first row, a difference in thermal performance attributable to the shorter PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 18 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot "ATE 7/7/98 VERIFIEDBY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJECr LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Then-ral Performance Model -- 1(2)VY03A coil finned length can be identified.
By pro-rating the differences identified to account for the fact that only 2 of the 24 tubes in the first row are affected, an estimation of the net effect is obtained.6.11 Fouling Sensitivity Analysis To assess the sensitivity of the 1(2)VY03A coolers to tube-side fouling accumulations, a series of iterations are performed.
With each iteration, the design tube-side fouling factor is incrementally increased from a value of 0.0000 to 0.0040 while the air-side fouling factor is held constant at the revised level of 0.002. The heat removal capability resulting from each fouling increment is compared to the required heat load to assess the thermal margin. Thermal margin is calculated using Equations (10) and (11).7. RESULTS 7.1 Model Benchmarking The first model case was based on the standard CF-9.05-3/4 J-A configuration available from the PROTO-HX T M library. The results of this initial benchmarking case are presented in Table 5.The PROTO-HXTM reports associated with the initial benchmark case are included as Attachment C.Table 5: Initial Benchmark Case -Standard CF-9.05-3/4 J-A Configuration Design q(1 1  PROTO-HX T M  Percent Cooler (BTU/hr) Predicted q (BTU/hr) Difference 1(2)VY03A 1,108,000 1,157,626 
+ 4.48%(I) Heat rate specified by cooler vendor Based on the results of the initial benchmark case with the standard CF-9.05-3/4 J-A configuration, another case was completed using a customized Colbum J-Factor.
This case demonstrated adequate benchmarking of the model to the vendor specified performance.
A subsequent comparison run was made following the adjustment of the coil finned length to match the length identified in Reference 
: 20. The results of the final benchmarking cases are presented in Tables 6 and 7. The PROTO-HXTM reports associated with the final benchmarking cases are included as Attachment E. 
[ PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 19 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECr LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A Table 6: Final Benchmark Case -- Customized Colburn J-Factor Design q PROTO-HX T M  Percent Cooler (BTU/hr) ") Predicted q (BTU/hr)(2)
Difference 1(2)VY03A 1,108,000 1,108,052 
+ 0.0047%(1) Heat rate specified by cooler vendor (2) With specified coil finned length per Reference 7 (benchmarking basis)Table 7: Final Benchmark Case -- Effective Coil Finned Length Design q PROTO-HX T M  Percent Cooler (BTU/hr) ") Predicted q (BTU/hr)(2) Difference 1(2)VY03A 1,108,000 1,103,074 
-0.44%(1) Heat rate specified by cooler vendor (2) With effective coil finned length per Reference 20 (subsequent analysis basis)7.2 Cooler Thermal Margin Results Prior to defining margin, the predicted heat transfer capacity of the cooler (qavailable) is defined.The predicted heat transfer capacities at LaSalle Station Reference Conditions for both clean (zero fouling) and service (design fouling) conditions are summarized in Table 8.Table 8: Heat Transfer Capacity Heat Transfer Capacity Conditions (BTU/hr)Nominal (dry) --clean (f = 0.0000) 1,148,793 Nominal (dry) -- service (f = 0.00 15) 1,096,666 The thermal margin assessment relates the predicted capacity of the cooler at clean and service conditions to the required capacity under reference conditions.
The comparison is provided in Table 9. The PROTO-HXTM reports associated with the thermal margin assessment are included as Attachments F and G for zero and design fouling conditions, respectively.
PROTO-POWER CORPORATION CALC NO. 97-199 IEV A PAGE 20 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIET Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing T ITLE VY Cooler Thermal Performance Model -- 1 (2)VY03A Table 9: Thermal Margin at LaSalle Station Reference Conditions qrequired qavai'able Margin Margin Cooler Fouling (BTU/hr) (BTU/hr) (BTU/hr) (%)1(2)VY03A zero (clean) 722,217 1,148,793 426,576 59.06%1(2)VY03A design (service) 722,217 1,096,666 374,449 51.85%7.3 Limiting Cooling Water Flow Rate Analysis The limiting cooling water flow analysis calculated the lowest possible cooling water flow that would provide a thermal margin of approximately 30% for the 1(2)VY03A coolers. The results of the iterations to identify the limiting flow rate are summarized in Table 10. The PROTO-HXTM reports associated with the limiting flow analysis are included as Attachment I.Table 10: Limiting Cooling Water Flow Rate at LaSalle Station Reference Conditions Limiting qrequir. qavailable Margin Margin Cooler Flow Rate (BTU/hr) (BTU/hr) (BTU/hr) (%)1(2)VY03A 72.5 gpm 722,217 938,124 215,907 29.90%The uncertainty in the analytical methodology used to identify the limiting flow for 1(2)VY03A is presented in Attachment J. The result of the uncertainty assessment is that the uncertainty in the PROTO-HXTM extrapolated heat transfer rate ranges from +/- 3.71 to +/- 4.09% for the ranges of cooling water flow evaluated.
An uncertainty of+/- 4.50% is used to conservatively bound the analysis of Attachment J. The adjusted thermal margin is calculated using Equation (11) after subtracting the uncertainty from the available heat rate. The results are presented in Table 11 below.Water Flow Rate at LaSalle Station Reference Conditions PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 21 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE. 7/7/98 Vr.RIFIED BY M. Aboye JOB NO 31-003 CLIENT Corn-ionwealth Edison PROJECr LaSalle Station GL 89-13 Heat Exchanger Testing lihE VY Cooler Thermal Performance Model -- 1(2)VY03A 7.4 Impact of Missing Fins The assessment of the impact of missing fins in IVY03A was made at the limiting flow condition defined in the previous section (i.e., at 72.5 gpm). The results of the analysis are as follows: IVY03A Row #1 with nominal length of 108.00" at 72.5 gpm: IVY03A Row # 1 with adjusted length of 102.75" at 72.5 gpm: Difference between two cases at 72.5 gpm: Adjustment for impact of 2 out of 24 tubes (i.e., 2 twenty-fourths):
Total coil with nominal length of 108.00" at 72.5 gpm: Total coil with estimate with missing fins at 72.5 gpm: Overall impact of missing fins (%) at 72.5 gpm: 123,422 BTU/hr 121,197 BTU/hr 2,225 BTU/hr 185.4 BTU/hr 938,124 BTU/hr 937,938.6 BTU/hr-0.020%The missing fins on two of the 24 tubes in the first row of 1VY03A appear to have a negligible affect on the overall thermal performance of the cooler.The PROTO-HXTM reports associated with the assessment are included in Attachment I.7.5 Fouling Sensitivity Analysis The results of the fouling sensitivity analysis are included in Table 12. The PROTO-HXTM reports associated with the fouling sensitivity analysis and a graphical presentation of the results are included as Attachment M. It should be noted that neither the Table below or the figure in Attachment M have taken analytical uncertainty into account since the intent of this exercise is to assess the change in thermal margin (i.e., the slope of the curves in Attachment M). Analytical uncertainty treated as a bias on the results will have a negligible effect on the slope of the curves.Consideration of uncertainty would, however, change the point at which a thermal margin of 0%is reached.
PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 22 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot IDATE 7/7/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJEcr LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VY03A Table 12: Fouling Sensitivity Analysis -1(2)VY03A at 72.5 gpm Air-Sidef Tube-Sidef Required q Available q %Margin 0.0020 0.0000 722,217 1,002,563 38.82%0.0020 0.0010 722,217 969,164 34.19%0.0020 0.0020 722,217 938,124 29.90%0.0020 0.0030 722,217 907,127 25.60%0.0020 0.0040 722,217 879,956 21.84%8. CONCLUSIONS A model for the LaSalle County Station Units I & 2 SE Cubicle Area Coolers was developed using PROTO-HX T M Version 3.01. The model was benchmarked and validated using the performance specifications provided by the cooler vendor. The close correlation with vendor specified and model predicted thermal performance confirms that the models are to be considered acceptable for use in the GL 89-13 heat exchanger testing program and related performance analyses.The available thermal margin for the coolers has been defined for the nameplate rated flow of 180 gpm and for a reduced flow rate of 72.5 gpm in support of service water system re-balancing efforts. Inclusion of a conservative assessment of the uncertainty in the analytical methods of PROTO-HXTM has provided high confidence in the thermal margins defined by the model for all cases.The model database is saved under file name vy-03a.phx, with a file size of 1,277,952 bytes, and a file date and time of 7/6/98 at 6:21:52 pm. The saved database is set up to run the 72.5 gpm case with adjusted design fouling factors of 0.002 air-side and 0.002 tube-side.
The database file is included as Attachment N.9. REFERENCES
: 1. Heat Exchanger Thermal Performance Modeling Software Program PROTO-HXTM Version 3.01 Software Validation and Verification Report (SVVR) SQA No. SVVR-93948-02, Revision E, dated 11/5/97 2. LaSalle Calculation L-00 1077, Revision 2, RHR Pump A Cubicle Cooler Ventilation System PROTO-POWER CORPORATION CALC NO. 97-199 REV A PAGE 23 OF 24 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED B'Y M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison ,ROJEcr LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A 3. Procedure LTS-200-19, Revision 4, performed on cooler IVY03A on 6/12/98 4. LaSalle Station Updated Final Safety Analysis Report, Table 3.11-8, Harsh Environment Zone H6 -- Bounding Environmental Conditions Inside the ECCS Cubicles (Attachment A)5. LaSalle Station Updated Final Safety Analysis Report, Section 9.2. 1, ECCS Equipment Cooling Water System (excerpt -Attachment A)6. LaSalle Station Updated Final Safety Analysis Report, Section 9.2.6, Ultimate Heat Sink (excerpt -Attachment A)7. Drawing Number 28SW404543, "CSCS Equipment Area Cooling Coils," original issue, 7/21/76 (Attachment A)8. LaSalle Calculation L-000581, Revision 0, Evaluation of the CSCS Cubicle Area Coolers Operation with a Reduced Cooling Water Inlet Temperature
: 9. Piping and Instrumentation Drawing M-87, Sheet 3, "CSCS Equipment Cooling Water System," Revision F dated 5/4/88 10. Piping and Instrumentation Drawing M-134, Sheet 3, "CSCS Equipment Cooling Water i System," Revision F dated 5/25/82 11. Bahnson Drawings 2605-1-11,12,13, & 14 (Attachment A)12. Standards of the Tubular Exchanger Manufacturers Association (TEMA), Seventh Edition, 1988 13. Specification Number J-2582, Heat Exchange Coils and Cabinets, La Salle County -Units 1 and 2, Revision 1, dated 1/16/75 (excerpt -Attachment A)14. Proto-Power Calculation 96-069, Revision -, Fluid Properties 
-Moist Air -Range 80 to 300&deg;F 15. Compact Heat Exchangers, W.M. Kays and A.L. London, McGraw Hill, Third Edition, 1984. (excerpt -Attachment C)
PROTO-POWER CORPORATION CALCNO. 97-199 REV A PAGE 24 OF 24 V/YA-L-GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/7/98 VERIFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY03A 16. 1997 ASHRAE Handbook -- Funddmentals, inch pound Edition, American Society of Heating, Refrigerating and Air Conditioning Engineers, Inc., Atlanta, GA (excerpt -Attachment A)17. Drawing M-1366, Sheet 1, "Reactor Building Ventilation System -- Elevation 694'-6" East," Revision H dated 4/29/83 18. Drawing M-1464, "CSCS Equipment Cooling System," Revision B dated 5/12/88 19. Drawing M-1465, "CSCS Equipment Cooling System," Revision B dated 5/12/88 20. Coil Walkdown Data, CoinEd NDIT No. LS-0847 dated 7/6/98 (Attachment L)
Attachment A to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

A Rev: A Page 1 of 11 Reke~re~nce.
4.LSCS-UFSAR TABLE 3.11-8 HARSH ENVIRONMENT ZONE H6 -BOUNDING ENVIRONMENTAL CONDITIONS INSIDE THE ECCS CUBICLES (EXCLUDING LPCS/RCIC CUBICLE) IN THE REACTOR BUILDING WHEN THE ECCS EQUIPMENT IS OPERATING The maximum cubicle temperature is '148"F, 90% relative humidity and at atmospheric pressure for the duration of 100 days. The total number of hours the cubicle is at 148*F will be -22,110 hours (-921 days). The .100 days accident conditions are included.Radiation:
I x 107 rads ganmma (integrated)
Pressure: 
-0.4 inch W.G.NOTE: The bounding radiation dose I (normal service radiation dose integrated over 40 years + accident does + 10% margin on the accident dose per IEEE 323-1974, Section 6.3.2.5).Proto-Power Calc: 97-199 

==Attachment:==

A Rev: A Page 2 of 11 TABLE 3.11-8 REV. 6 -APRIL 1990 
' LSCS-UFSAR
: 4. RHR pump seal cooler ('A' and 'B' RHR pumps only) -.20 gpm 5. LPCS pump motor cooling coil -,.4 gpm 6. northwest cubicle area cooling coil -150 gpm 7. southwest cubicle area cooling coil -150 gpm 8. northeast cubicle area cooling coil -200 gpm 9. southeast cubicle area cooling coil -180 gpm 10. emergency makeup to fuel pool -50.gpm minimum 11. containment flood -300 gpm maximum.b. System classifications are as shown in Section 3.2. All portions of this system are protected from the effects of tornados, missiles, pipe whip, and flooding.c. To meet single failure criteria, the CSCS-ECWS for each unit is designed as three independent subsystems, one of which is shared between units (Drawing Nos. M-87 and M-134).d. Strainers are provided to prevent plugging of cooled component heat transfer passages.
All strainers include provisions for backwashing without significantly affecting system operation.
Organic fouling of heat transfer surfaces will be minimized by the chemical feed system which will treat the service water tunnel inlet flow-with oxidizing biocides.
However, the chemical feed system should not be considered auxiliary equipment required for the CSCS-ECW systems to perform their function.
Therefore, the operability of the-CSCS-ECW systems should not be tied to the operability of the chemical feed system. Connections and isolation valves are also provided immediately upstream and downstream of each cooled component for injection and circulation of biocidal agents, if necessary.
: e. To detect leakage of radioactivity to the environment, radiation monitors are installed in the CSCS-ECWS immediately downstream of cooled components that contain radioactive fluids. The CSCS-ECWS discharge lines from these components are capable of remote manual isolation from the main control room.f. Design of system piping and components is based on a 40-year life.Exterior surfaces of all buried system piping is protected by bituminous coatings and wrappings and provisions for cathodic protection are installed where such protection is found to be required based on electrical potential measurements.
The design of all system piping includes a corrosion allowance of at least 0.08 inches.Proto-Power Caic: 97-199 

==Attachment:==

A Rev: A Page 3 of 11 9.2-2 REV. 10 -APRIL 1994 -
LSCS-UFSAR the normally closed portions the integrity and operability are checked.9.2.6 Ultimate Beat Sink The ultimate heat sink (UHS) provides sufficient cooling water to permit the safe shutdown and cooldown of the station for 30 days with no makeup for both normal and accident conditions.
9.2.6.1 Design Bases 9.2.6.1.1 Safety Design Bases The ultimate heat sink has the following design bases: a. to provide sufficient water volume permitting a safe shutdown and cooldown of the station for 30 days with no water makeup for both normal operating and accident conditions -lhemaximum permissible water temperature&#xfd;supplied t6 the &#xfd;plant is taken as 1000 F;b. to withstand the most severe postulated natural phenomenon as discussed in Chapter 2.0;c. to withstand the postulated site-related incidents as discussed in Subsection 2.5.5; and d. to provide water for fire protection equipment.
A more detailed physical description of the ultimate heat sink is provided in Sections 2.4 and 2.5.9.2.6.1.2 Power Generation Design Bases The ultimate heat sink, as a safety system, is not used during normal plant operations.
Therefore, the ultimate heat sink has no power generation bases.9.2.6.2 System Description In the unlikely event that the main dike is breached, the cooling lake for the La Salle County Station is designed to hold 460 acre-feet of water with a surface area of 83 acres. This remaining water constitutes the ultimate heat sink for the station, and has a depth of approximately 5 feet and a top water elevation established at 690 feet. Figures 2.4-4 and 9.2-1 illustrate the physical layout and area capacity of the ultimate heat sink.9.2.6.3 Safety Evaluation The station's ultimate water requirements (Units 1 and 2) in gpm are summarized below.Proto-Power Caic: 97-199 

==Attachment:==

A Rev: A Page 4 of II REV. 0 -APRIL 1984 9.2-18 
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91-!99.

==Attachment:==

A Rev: A' Page 6 of 11.'k % .'M~-100-13 
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==Attachment:==

A Rev: A Page 7 of 11 PANE LEFT HtAND W4'T ALL Oii(NhiOUS2V
'(IOC-100 
'I GENERAL QUALITY ASSURANCE PROCEDURE LARGNTPL UmDy I TITLE & APPROVAL PAGE SM. , ,-................
i NXwVT To % %ON 1% %0 %W"SAFETY RELATED ITEMS ARE PART OF THIS SPECIFICATION" Client CECO Specification Title Specification Number Project Identification Heat Exchange Coils and Cabinets J-2582 La Salle County -Units 1 and 2 4266-00/4267-00 Project Number Mechanical/HVAC Department REV DATE PREPARER 11 APPROVER IPURPOSE OF ISSUE 1 1-16-75 PN.KeAq&#xfd;L-I ( r;&#xfd;4&#xfd;&#xfd;w&#xfd;Issue to CECO for bids.Proto-P~,wer Ca.c: 97-199 Attachrr Rev: A ent: A Page 8 of 11 4I U Function or Service ...........
Equipment Numbers .............
Safety related or Nonsafety related (SR or NSR)...........
403. PERFORMANCE DATA (HEAT EXCHANGE Auxiliary Primary CSCS Eqpt. CSCS Eqpt. CSCS Eqpt--Control Electric Contain- Area Area Area Room Equipment ment Vent., Cooling Cooling Cooling OVCO2AA OVEOIAA IVP03AA IVYOIA 1VYO3A IVY04A OVC02AB OVEOAB IVP03AB 1VY02A 2VY03A 2VY04A 2VPO3AA 2VYOIA J 2VP03AB 2VYO2A 403.-00 COIL CABINETS)I Mode of Operation 
.............
: a. Entering Air Dry Bulb ...... (-F)b. Entering Air Wet Bulb ...... (OF)c. Leaving Air Dry Bulb ....... (OF)d. Leaving Air Wet Bulbi ...... (OF)e. Actual Air Quantity at 70 0 F, 40% RH and Site Elevation 3...................... (ft /min)f. Standard Air Quantity at .075-lb/ft 3............. (Std ft 3/jniri)g. Cooling Medium .................
: h. Evaporator Refrigerant Tempera-, ture ....................... (OF)i. Entering Water Temperature.(*F)
: j. Maximum Water Quantity(gal/min) k, Minimum Total Heat Exchange Capacity ............... (Btu/h)1. Minimum Sensible Heat Exchange Capacity .............. 
.(B.tu/h)m. Maximum Coil Face Velocity............ (ft/min)SR* Cooling 81.8 63.1 54.3 52.8 26340 25380 R-22 42 797,000 725,000 600 SR Cooling 81.9 63.2 54.9 53.2 31300 30100 R-22 42 936,000 847,000 600 NSR Cooling 135 92 65 63 50000 48150 Chilled Water 46 1200 6.55x10 6 3.63xi0 6 600 SR and ASME IlI Cooling 150 110 110 0*14 0 SR and SR and ASME 111 ASME III Cooling 150 18000 17330 Water 105.150.748,700 748,700 700 26400 25420 Water 105.220.1.1 X1 i. I x 106 0. 0 x L06 700 Cooling 150 110 h8500 7450 dater 105.Z40.19 x 106.19 X 106 700 Add. 1 Add. 1 Add. 1 Add. 1 Add. 1 00 LL 26.1(0 9ttrtVtt I 1997A.SH.AFundaentals, , C'labue 1A Heating and Wind Design Conditions--United States[1ev. Sill, W3JO i La. Long. fl pri= Gates Slatticn 5's,! I3'ulr litcalt.610,WL4.mtheam Brunswick ('oluqneer.
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.Glen~ew, s Mamseaf Molioefluwm poec L&Peoria Rockhard Sptgldd West chicip INDLAU E"O~svilie Fort Wasii Indianmpolis Labyeu4&#xfd; Purdir E~uv PeM, Urissom 418 aoutb Bend Tene Ifaule IOWA Burtlngion 1fesl Pi4nio Pem:s Wine porl  (~nneeryij Wdrodlind 7.1010 26.64 A3(0 12 211 1 6X4; 619M 722.160 .1 1., 3 4 Is 19 .1 [' 1 N29 .4.723110 3319; P3.31 M0 14270 6191 7221911 336"; .844- -I011 W4 1ii 6193 722180 73.37 S1 97 14% 14.617 h19%722137 31.15 81.38 20 14.683 8293 722250 32 33 950) 2.43 14.571 8293 722255 32 52 84.93 397 14 4S6 6193 722170 32.70 83.65 361 14 505 6193 722270 33.92 84.52 1070 14 136 S293 723200 34.35 85.17 6&3 14.357 8293 722070 32.13 $1.20 49 14669 6193 747810 30.97 83 20 233 14 572 8293 722166 30.78 83 28 203 14 588 8293 722130 31.:5 82.40 151 14,615 8293 911790 21.32 15807 912850 19 72 155.07 911820 21.35 15793 911900 20.90 156.43 911760 21.45 15777 911650 21.98 159.35 911860 21.15 157.10 49 14 ,.69 8293 36 14676 6193 16 14.697 6193 66 14.661 6193 10 14.690 8293 148 14.617 6193 449 14.458 8293 E[treme Cind eldest Mnl WS/4&#xa3;1B 1t&-iMWU In fl 
-4 Ileuling D11 Speed 0 4% 1%. 99-61. 0.0. CeanlJI 99.6w 99%i 04 7.5% 5% A Mtilo 14S MOB1 A1W3'3S1AI WSPWO Mx.o qiu_ ... .. .. .. .- ];4".." 2' 22 19 24 ;,g 21 " ' -'(1 12 110 94 35 2.o-1 L. It S 19 q. I9 N 4 4w 11 '2.50 -O, A1 r2 20 ' ) 19 I 15 20 401 Ix 41) 10 "M19 29'0 4% I1 " .18 21 22 19 17 '3 .7 1 16 1. 310 ,; .00 96 9 5 73 I1 2 0 11 3. I5 21 45 19 4"y 5 :90 () 13G : 00 13 .1.7 5 30 34 I8 17 16 19 49 18 49 8 350 10 2250 9 22 2 .S 7 23 27 t6 11 I)' 4j I5 -, 3 310 5 '40 1;16 14 2.9 64 1 23 27 l 1 14 IS 44 16 46 .L0 9 310 99 14 23 61 23 27 19 17 1i 20 46 I. 45 7 320 9 270 100 14 2.7 6.4 21 76 18 16 13 20 1 ) is 38 9 1-40 6 300 97 12 3.6 6.7 15 21 14 12 10 14 42 13 42 5 340 6 270 98 4 3.8.,7: 26 29 20 17 1I. 21 4&#xa3;) !9 4e , 270 9 270 9' 1[8 3.0 5.4 30 34 1I 13 12 16 51 14 5" 4 360 5 300 95 21 2. .6 28 31 17 15 14 18 I5 16 16 4 .340 8 100 99 17 7.7 29 32 16 14 12 16 1.2 24 ;2 4 250 7 240 98 22 7 7,6 59 61 20 18 16 22 73 19 14 5 40 11 60 33 35 1.6 21. 4 61 63 19 16 14 21 76 18 76 7 2.30 12 110 88 58 1.6 I..6&#xa3; 63 23 21 20 21 .74 21 75 5 320 15 60 91 58 1.9 22 59 61 27 25 24 32 76 28 76 6 160 19 50 92 54 1 I5 1A 67 68 20 18 17 21 74 19 74 7 190 10 70 88 40 1.429.0 60 62 26 24 21 25 73 23 73 &#xa3; 270 14 60 87 57 1.43 ,0 60 61 24 22 21 22 74 21 74 4 70 13 60 92 43 4 202 i 2 9 24 21 18 22 37 19 37 6 130 11 320 103 -4 2.7 9.1-5 2 23 21 19 23 30 22 28 7 60 8 280 98 -11 4 8.5 A-12 -6 27 23 21 28 32 23 29 7 360 12 180 96 -20 3.6 9.0 6 15 20 17 14 24 38 20 40 5 280 7 310 &#xa3;03 3 2.7 9.9, 0 5 23 21 18 23 3321 3 2 90 8 350 105 -6 3.2 &.;-1 7 10 10 9 11 I 9 21 2 10 4 10 92 -7 2 7.9.-0 29 25 23 30 36 27 .16 6 50 11 250 9&#xa3; -15 2.3 9.1.3 10 21 I8 15 23 32 20 31 7 360 7 90 100 -3 3.1 7.2-4 3 23 22 19 26 17 23 30 12 240 33 220 97 -10 3.2 8.1 ,.-6 -1 26 23 21 27 24 23 23 10 270 12 230 96 -12 2.8 634-2 3 24 .22 20 27 24 24 27 13 310 12 210 99-1.0 51 1::6-3 4 22 19 17. 23 17 20 25 II 250 30 240 98 -10 3.1 7,?,-5 1 26 22 20 28 18 25 21 12 290 10 2510 96 -II 4 5.9.-8 -3 26 23 20 28 16 24 18 9 290 12 200 97 -14 2.7 6.0"i-6 -1 25 22 20 26 16 23 19 9 290 11 380 96 -12 3.3 6.1 i*-4 2 26 23 20 29 23 24 22 12 330 12 210 97 -10..3.6..1j'. 4 26 23 21 26 18 23 20 9 290 13 200 95 -16 3.1 5.5*.4 2 25 23 21 27 25 24 27 10 270 12 230 97 -II 2.8 5.5-7 0 23 21 19 25 13 23 20 II 290 11 240 96 -14 3.2 7.7 3 9 22 19 17 22 33 20 34 7 320 9 240 97 -4 2.7 85-4 2125 23 20 27 19 24 22 10 250 12 230 95 -t1 3.6 5.2-3 3 24 21 19 25 26 22 27 8 210 11 230 94 -30 2.8 6.8-5 3 22 20 18 24 26 22 27 9 270 12 220 97 -I1 3.8 .?,-3 4 24 21 1g 29 20 24 22 II 270 9 210 96 .S 3.8 7.4.2 3 25 23 20 26 22 23 23 13 230 12 230 95 -10 3.3 5.8 3 5 23 20 Ig 2. 31 21 32 8 150 I 230 96 -10 3.2 7.9 726810 43.57 116.22 2867 13.235 6193 725867 42.55 113.77 4150 12.621 8293 725785 43.52 11207 4741 12.346 8293 727830 46.38 117.02 1437 13.948 8293 726915 43.05 115.87 2995 13.173 8293 727836 47.47 115.80 3317 13.017 8293 725780 42.92 112.60 4478 12.468 6193 724338 38.55 89,85 453 14.457 8293 725340 41.78 87.75 623 14.367 8293 725300 41.9&#xa3; 87.90 673 14.342 6193 72531.6: .39.3S-8.98,97 682. 34337:. 8293 725306 42.08 87.82 653 14.352 8293 744600 41.37 88.68 738 14.308 8293 725440 41,45 90.52 594 14.383 6193 7 25320 40.67 89.69 661 14.347 6193.724396..39.95 91.20 768 14.292 8293 725430 42.20 89 10 741 14.306 6193 724390 39,85 89.67 614 14.373 6193 725305 41.92 88.25 758 14.297 8293 724320 28.05 87.53 387 14.491 6193 725330 41.00 85.20 827 14.262 619.3 724380 39.73 86.27 807 14.272 6193 724396 :40.42 86.93 607 14.376 8293 725335 40.65 86.15 810 14.270 $293 7253350 41 70 86.32 774 14.2R9 6193 724373 3945 87.32 584 14.388 &#xa3;293 725455 40.78 72$450 41.8&#xa3;725460 41.53 725410 42.55 725466 40.62 725485 43.15 725465 41.10 725M70 42 40 726500 43.17 725480 42-54;91.13 699 14.328 8293 91.70 869 14.240 8293 9365 965 14 190 6193 04.18 1105 14 087 8293 93.95 3122 14 109 8293 93.33 1214 14.062 6193 92.45 846 14 251 8293 96.38 1102 14 119 6193 9515 &#xa3;339 13998 8293 9240 879 14.234 6193--4.9-13-51-19-16 t4.4 0-3-4-.10 0 ,6 9 3 I'5 21 25 27 27 29 29 24 27 28 30 19 22 24 23 17 2-3 26 23 24 2 5 27 18 26 28 17 20 21 21 1t 22 23 22 20 22 22 24 16 23 24 24 29 28 29 2!30 31 31 2i 29 3l10 29.11 12 12 14 30 23 9 20 14 13 10 9.1 39 32 2.7 21 26 24 26 19 27 28 28 21 2"i 25 27 18 25 27 i8!4 19 iO 20 12 24 16 II, 37 34 30 9 110 11 20(1 If) 30)0 11 180 II 3A0 12 10 11 .4t1 I1 190 7 320 9 2?11 12 300 14 200 I 320 15i 00 I1 120 14 1O0 Is .t0 32 I0 9 300 13 180 13 360 16 10 13 10 17 200 5 350 9 180 12 360 16 190 12 2',-0 i3 180 98 96 98 46 99 97 98 99 99 96!04!04 10-2-10 4-15 .3.6-25 3.4-17 4.9-12 4.3-23 3.6 I-2 4 18 1.6'-o 6.1.20 34" 6.8 5.4 5.1 4.9 6.8 11.4 6.8 4.7 40 5.9 9'724580 39 55 97.65 1483 13.925 8293 724510 37.77 99.97 2592 13.370 6193 724550 3905 96.77 1066 14.138 8293 724515 37 93 100.72 2890 13 224 8291 724650 39.37 101.70 3688 12.840 6193 8- 4 9.4 6 2.1 5.6 It 1 9.0--9 27 65-I I 2.9 6.6..X WO0' -World Mnerdlngal Orgxnizancn number!at- inhtle Irng. .Iunrtgitnude Hlev -clevkflath.
ft Sldi,' -pressure at msllimn elevarm. psia 138. 4ev bulb trmpennere.
i Proto-P5Werp&4.fIt97-199 

==Attachment:==

A Rev: A Page 10 of 11*U -
I I 11 t (S I.(.9 Physical Properties of Materials Rs~~erv~ct-16 36.3 Table3 Properties of Solids Specific Heat, Density, Thermal Condutivity, Ai:terial Descriplitin I~tlh -&deg;l,"F 11/fl Btlu1 -,-ft -1" Aluminuun (alloy 110) 0.214' 171L' 12V" I'. IllL% iv its P Alurrlh:-'Irna bFi1iie (76% Cu. 22% Zn. 2% At)Asbcaic: Fiber Insulation A-hes. wood Asphalt Bakelite Dell CUtaia Hisioulah tin Brick. building 0.09'0.20" 0 ciji.Sur,-fatce Conditi m (?I1e1C L-i 0 shI led 1 'eif lv r "Pe,p" ofo(r'0.20'0.24-o.221 0.35" 0.056' (122)0.040*0.2'517" 40'132" 91" 123" 581.0.097" 0.0921'0.011- (122)0.43r 9.7" Brass: Red (85% Cu, 15% 'n)Yellow (65% Cu. 35% Za)Brunie Cadmium Carbon (gas reron)Cardboard Cellulose Celirent tportland clinker)Chalk Charcoal (wood)Chrome brick 0.09'" 0.104'0.055" 0.17$0.32" 0.16t" 0.215'0.2d 0. 17b 548" 519'54(y 376" 0.44 0.93"0.03(0h H ighhy pohkhed 69" 0.033-" Hlighly lhilifhicd 1I 'P 32)53.7b 0.0 2 d.0.20" (2) 0. I" 0.04" 0.0331 0.017i 0.48' 0.34, About 250&deg;F 0.03' (392)0.67'3.4" 12(f 143'15" 200 Clay 0.22" 63'Coal 0.3" 90' 0.098' (32)Coal tars 0,35" (0(M) 75" 0.07" Coke (petroleum, powdcred) 0.36k (752) 62" 0.55b (752)Concrete (stote) 0.156h (392) 144" 0.54" Copper (electrlytic) 0.092" 556" 2271 0.0724 ComTnercial.
M,,i ny Cork (granulated) 0.485' 5.4t 0.02 (23)Couion (fiber) 0.3196 95u 0.024" Cryoite (AIFP 3NaF) 0.233b I81" Diamond 0.147" 15 I 27'Earth (dry and packed) 951 0.0-17 0.41'Felt 20.6" 0.03" Fireclay brick 0.198b (212) 112' 0.58b (392) 0.75" At 18321F Fluorspar 2) 0.21' 199, 0.63v Gemrn silver (nickel silver) 0.09' 545' 19" 0.135' Polished Gla: Crown (soda-lime) 0.180 15 0.591 (200) 0.94" Smooth Flint (lead) 0.1 17' 267" 0.79'Heat-resistant 0.20' 139' 0.59' (200)"Woor 0.157b 3.25' 0.022'Gold 0.031? 1208" 172' 0.028 Highly polished Graphite:
Powder 0.165' 0.106'Impervious 0.16'" 1171 75" 0.75" Gypsum 0.259b 78? 0.25" 0.903b On a smooth plate Hemp (fiber) 0.323" 93" Ice. 32TF 0.487" 57.5" r:3 0.95'.-4&deg;F 0.465' 1.410 Iro": Cam 0.12' (212) 450b 27.6"(129) 0.435" Freshly turned Wrought 485h 34 9b 0.94t" Dull, oxidized Lead 0.0309V 707'" 20. 1" 0.28" Gray. oxidized Leather (sole) 62.4b 0.092b lmi"stoac 0.217' 103" 0.54" 0.36" to 0.90 At 145 to 380TF Liaen 0059 Litharge (lead monoxide) 0.O55" 490" Magnesia:
Powdered 0.234" (212) 49.7h 0,35" (1171 light caronate .3f 0.034b Magnesite hbick 0:222" (212) 1iSS 2.2" (400)Magnesium 0.241h 108" 91"u 0.55' Oxidrzd Marble 0.21" 162" 1.51" 0.931h l.ight gray, poilished Nickel, palisteid 0.10 &#xb6;555" 34.4' 0.045n EleCtroplatcd Paint,- White lacquer 0.80" White enamel 0.91' On rogh plate Black lacquer 0.80" Black shellac 63" 0 15" 0.91' "Matte" flrlnh Flat black lacquer 0.96" Alhminuir lacquer 13) 9" On rough plalte Lbta sow cc un " k nown.NfOIr,. I ValueS arer for room lernpetature inlets otberwite.
noted in parrnahcwsc
: 2. (loers indicalc data source ftomIa the of' Referetces.
Proto-Power Caic: 97-199 

==Attachment:==

A Rev: A Page 11 of 11-U Attachment B to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

B Rev: A Page 1 of 2 S I LA SALLE COUNTY STATION HEAT EXCHANGER (WATER TO AIR)DATABASE EQUIPMENT NUMBER/NAME INSPECT DATE B A S E P H 0 T PHOTO STORAGE LOCATION GENERAL APPEARANCE TUBE CONDITION NO VISIBLE DAMAGE OR LEAKS FINS CONDITION DEFECTS C 0 R R E C T I V E RECOMMENDED x===wv= ... mhSSZms*ACT IONS ACTUAL 1vY03C B/C RHR AREA COOLER I 09/08/92 N Y BTN/KAPSNOT VERY CLEAN, NO HXMI DEBRIS MINOR FIN DAMAGE, BUT NO MORE THAN PREVIOUSLY.
NO DIRT OR DEBRIS TRAPPED BETWEEN FINS.NONE NONE NEEDED N/A I vyc%:&#xfd;r&#xfd;i'll /I &#xfd;I~~~~~ V~T 7/n lit .'o Attachment C to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

C Rev: A Page 1 of 9 12:13:55 PROTO-ItX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Data Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/06/98 Air Coil Heat Exchanger Input Parameters Fnleti Dry Bubi  Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side_3-I0W67.0- f 150.00 OF 92.00 OF 108.80 OF 84.00 OF Tube-Side---30_0- gpm 105.00 OF 117.70 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Fresh Water 0.001500 0.000000 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins CF-9.05-3/4J A j = EXP[-2.3333 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F) 111.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

C Rev: A Page 2 of 9 12:13:55 PROTO-HIX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out (&deg;F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (&deg;F)Wet Bulb Temp Out (OF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm) 180.00 Air Flow (acfrn) 31,066.00 Tube Inlet Temp (OF) 105.00 Air Inlet Temp (OF) 150.0 Inlet Relative Humidity (%) 0.00 Inlet Wet Bulb Temp (OF) 92.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

C Rev: A Page 3 of 9 12:13:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/06/98 a Extrapolation Calculation Summary II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbmr/fthr)
Skin Visc (lbm/ft.hr)
Density (IbM/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ftb'F)
Air-Side 114,411.37 150.00 109.56 Tube-Side 89,409.99 105.00 117.96 Tube-Side hi (BTU/hr'ft 2"&deg;F)j Factor Air-Side ho (BTU/hr-ft 2-&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr ft 2.0 F/BTU)U Overall (BTU/hr" ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 2650655==
10,824.91 1,157,626 1,157,626 Extrapolation Calculation for Row l(Dry)ii Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Tlemperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hir)Skin Visc (lbm/ft.hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 114,411.37 150.00 141.57 0.0203 0.0203 145.78 125.02 4,509.16 1,005 0.7253 0.0491 0.0622 0.2402 0.0163 Tube-Side 89,409.99 115.26 117.96 116.61 119.00 5.53 38,835 3.7653 1.3906 1.3592 61.7634 0.9988 0.3689 Tube-Side hi (BTU/hr.ft 2.-F)j Factor Air-Side ho (BTU/hr.ft 2.0 F)Tube Wall Resistance (hr-ft 2-&deg;F/BTU Overall Fouling (hr-ft 2-&deg;F/BTU)U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)1,660.80 0.0090 12.06 0.00029413

==0.0 2650655==
7.70 1,082.49.28.95 241,422 0.8977 241,422 Proto-Power Cale: 97-199 

==Attachment:==

C Rev: A Page 4 of 9*** Air Mass Velocity (Lbm/lhrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:13:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/06/98 Extrapolation Calculation for Row 2(Dry)iI II Mass Flow (Ibm/lr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ftohr)
Skin Visc (lbm/ftdhr)
Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft.
0 F)Air-Side 114,411.37 141.57 134.66 0.0203 0.0203 138.11 121.06 4,509.16 1,014 0.7260 0.0486 0.0630 0.2402 0.0161 Tube-Side 89,409.99 113.05 115.26 114.15 116.14 5.53 37,920 3.8651 1.4242 1.3970 61.8000 0.9988 0.3680 Tube-Side hi (BTU/hr" ft 2'&deg;F) 1,639.05 j Factor 0.0090 Air-Side ho (BTU/hr" ft2.&deg;F) 12.01 Tube Wall Resistance (hr.ftlz-F/BTU 

==0.0 0029413==
Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.67 1,082.49 23.78 197,591 0.8980 197,591 Extrapolation Calculation for Row 3(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fthr)
Skin Visc (lbm/ft-hr)
Density (lbm/ftl 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ftl.F)
Air-Side 114,411.37 134.66 129.01 0.0203 0.0203 131.83 117.82 4,509.16 1,023 0.7265 0.0482 0.0636 0.2402 0.0159 Tube-Side 89,409.99 111.23 113.05 112.14 113.78 5.52 37,176 3.9501 1.4527 1.4293 61.8294 0.9988 0.3673 Tube-Side hi (BTU/hr ft 2-&deg;F) 1,621.18 j Factor 0.0089 Air-Side ho (BTU/hr ft 2-&deg;F) 11.97 Tube Wall Resistance (hr-ft2-0 F/BTU 0.00029413 Overall Fouling (hr- ft 2-&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft2-'F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.65 1,082.49 19.55 161,922 0.8983 161,922 Proto-Power Calc: 97-199 

==Attachment:==

C Rev: A Page 5 of 9*** Air Mass Velocity (Lbn/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:13:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/06/98 M I Extrapolation Calculation for Row 4(Dry)II T I 1 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Vise (Ibm/ft hr)Density (Ibm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 114,411.37 129.01 124.37 0.0203 0.0203 126.69 115.16 4,509.16 1,030 0.7269 0.0479 0.0641 0.2402 0.0158 Tube-Side 89,409.99 109.75 111.23 110.49 111.85 5.52 36,570 4.0221 1.4767 1.4568 61.8531 0.9988 0.3667 Tube-Side hi (BTU/hr'ft 2.&deg;F) 1,606.48 j Factor 0.0089 Air-Side ho (BTU/hr-ft2.&deg;F) 11.94 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr ft 2-F/BTU) 0.02650655 U Overall (BTU/hr'ft2.&deg;F)
Effective Area (ft)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.63 1,082.49 16.08 132,832 0.8985 132,832 m Extrapolation Calculation for Row 5(Dry)11 Air-Side Mass Flow (Ibm/br) 114,411.37 Inlet Temperature (IF) 124.37 Outlet temperature (OF) 120.56 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 122.46 Skin Temperature (OF) 112.98 Velocity *** 4,509.16 Reynold's Number 1,035 Prandtl Number 0.7272 Bulk Visc (lbmr/fthr) 0.0476 Skin Visc (lbm/ft.hr)
Density (lbm/ft 3) 0.0645 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-ft-.F) 0.0157 Tube-Side 89,409.99 108.53 109.75 109.14 110.26 5.52 36,075 4.0828 1.4970 1.4801 61.8722 0.9988 0.3662 Tube-Side hi (BTU/hr-ft 2.-F) 1,594.38 j Factor 0.0089 Air-Side ho (BTU/hr-ft 2-&deg;F) 11.91 Tube Wall Resistance (hr-ftV.&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02650655 U Overall (BTU/hr ft2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.62 1,082.49 13.23 109,063 0.8987 109,063 Proto-Power CaIc: 97-199 

==Attachment:==

C Rev: A Page 6 of 9*** Air Mass Velocity (Lbrnhr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:13:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/06/98 Extrapolation Calculation for Row 6(Dry)II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (Ibm/ft-hr)
Skin Vise (lbm/fr-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 114,411.37 120.56 117.42 0.0203 0.0203 118.99 111.19 4,509.16 1,040 0.7275 0.0474 0.0648 0.2402 0.0157 Tube-Side 89,409.99 107.52 108.53 108.02 108.95 5.52 35,671 4.1338 1.5140 1.4997 61.8877 0.9989 0.3658 Tube-Side hi (BTU/hr'ft 2"&deg;F)j Factor Air-Side ho (BTU/hr'ft 2-&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr" ft 2-&deg;F/BTU)U Overall (BTU/hr ft 2.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)1,584.42 0.0089 11.89 0.00029413

==0.0 2650655==
7.60 1,082.49 10.89 89,612 0.8989 89,612 k Extrapolation Calculation for Row 7(Dry)11:=:=:u Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (ibm/ft hr)Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 114,411.37 117.42 114.85 0.0203 0.0203 116.14 109.72 4,509.16 1,044 0.7277 0.0472 0.0651 0.2402 0.0156 Tube-Side 89,409.99 106.70 107.52 107.11 107.88 5.52 35,339 4.1764 1.5282 1.5162 61.9003 0.9989 0.3655 Tube-Side hi (BTU/hr-ft 2.&deg;F) 1,576.22 j Factor 0.0089 Air-Side ho (BTU/hr-ft 2_-F) 11.87 Tube Wall Resistance (hr-ft2. F/BTU 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (fW)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.59 1,082.49.8.96 73,673 0.8990 73,673 Proto-Power Calc: 97-199 

==Attachment:==

C Rev: A Page 7 of 9*** Air Mass Velocity (Lbrnlhr ft 2-), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:13:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/06/98 MP--Extrapolation Calculation for Row 8(Dry)II T_Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (ibm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hrft'F)
Air-Side 114,411.37 114.85 112.73 0.0203 0.0203 113.79 108.50 4,509.16 1,047 0.7278 0.0471 0.0654 0.2402 0.0155 Tube-Side 89,409.99 106.02 106.70 106.36 106.99 5.52 35,067 4.2121 1.5400 1.5300 61.9106 0.9989 0.3652 Tube-Side hi (BTU/hr-ft 2-&deg;F) 1,569.47 j Factor 0.0089 Air-Side ho (BTU/hr'ft2"&deg;F) 11.86 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02650655 U Overall (BTU/hr.ft 2 0-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.58 1,082.49 7.38 60,599 0.8991 60,599 ffil=Extrapolation Calculation for Row 9(Dry)II II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft'hr)
Skin Visc (lbm/ft-hr)
Density (ibmr/fl 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 114,411.37 112.73 110.99 0.0203 0.0203 111.86 107.51 4,509.16 1,050 0.7279 0.0470 0.0656 0.2402 0.0155 Tube-Side 89,409.99 105.46 106.02 105.74 106.26 5.52 34,844 4.2417 1.5499 1.5415 61.9190 0.9989 0.3650 Tube-Side hi (BTU/hr-ft 2-&deg;F) 1,563.91 j Factor 0.0088 Air-Side ho (BTU/hr-ft 2-&deg;F) 11.85 Tube Wall Resistance (hr-ft2-&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr'ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hrft 2 0-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTUihr)7.58 1,082.49 6.08 49,865 0.8992 49,865 Proto-Power Calc: 97-199 

==Attachment:==

C Rev: A Page 8 of 9*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:13:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/06/98 N Extrapolation Calculation for Row 10(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ft hr)Density (lbm/ffl)Cp (BTU/lbmn'F)
K (BTU/hr-ft 0 F)Air-Side 114,411.37 110.99 109.56 0.0203 0.0203 110.28 106.69 4,509.16 1,053 0.7280 0.0469 0.0657 0.2402 0.0155 Tube-Side 89,409.99 105.00 105.46 105.23 105.66 5.52 34,661 4.2664 1.5580 1.5511 61.9259 0.9989 0.3648 Tube-Side hi (BTU/hr-ftl 2.F) 1,559.33 j Factor 0.0088 Air-Side ho (BTU/hr.ft 2.&deg;F) 11.84 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr. ft 2.F/BTU) 0.02650655 U Overall (BTU/hr.ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.57 1,082.49 5.01 41,046 0.8993 41,046 Proto-Power Calc: 97-199 

==Attachment:==

C Rev: A Page 9 of 9*** Air Mass Velocity (Lbm/hr-ftl), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T Attachment D to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

D Rev: A Page 1 of 2 268 (7Compact Heat~ Exchangers Fig. 10.9 Fmcnd catcuar tubes, sutiaceCF-9.05-314J. (Data cet Jamsofl.)f Tube outside diameter = 0M774 in -19.66 x 10-3m Fin pitch -9.05 per in 356 per m Fin thickiness 
-0.012 in = 0.305 x 10-3 m Fin area/total area -0.835 Flow passage hydraulic A 8 diameter, 4 r,, 0.01681 0.02685 5.131 x 10-3 8.1 79x 10"-C 1 E 0.0445 0.01587 0.02108 ft 13.59 x 103 4,846 x 10" 6.426 x 10"rn Free. flow area/Irontal area, U -0.45 Heat transfur area/total VOlWime. o- 108 354 5 0.572 0.688 0.537 0.572 85.1 61.9 135 108 1t1/ft3 279 203 443 354 m2im3 Nntet. Mini-rruii rree.-flow awea in all ca~e" OCCUIv In the [F.c~tLar,'Vcre to the flow. excepi For 1, in which the minim~rum Arei is in %hte diaqnnals.
Proto-Power Catc: 97-199 

==Attachment:==

D Rev: A Page 2 of 2 Attachment E to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 1 of 17 12:36:35 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/06/98 Air Coil Heat Exchanger Input Parameters FI1neiFdrQy-ulffibt-, Teo-mp-Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 317-06-6&.00-&fiiir 150.00 OF 92.00 OF 108.80 OF 84.00 OF Tube-Side[80.0Y- gpm 105.00 OF 117.70 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F)
Fresh Water 0.001500 0.000000 1,108,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]111.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 2 of 17 12:36:35 PROTO-IHX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (&deg;F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (OF)Wet Bulb Temp Out (OF)..Atmospheric Pressure Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm) 180.00 Air Flow (acfmi) 31,066.00 Tube Inlet Temp (OF) 105.00 Air Inlet Temp (OF) 150.0 Inlet Relative Humidity (%) 0.00 Inlet Wet Bulb Temp (OF) 92.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 3 of 17 12:36:35 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/06/98 11 Extrapolation Calculation Summary II~7T Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbmr/fthr)
Skin Vise (ibm/fu-hr)
Density (lbm/fl 3)Cp (BTU/lbm 0'F)K (BTU/hr'f'&deg;F)
Air-Side 114,411.37 150.00 111.29 Tube-Side 89,409.99 105.00 117.39 Tube-Side hi (BTU/hr ft 2.0 F)j Factor Air-Side ho (BTU/hr-ft 2 -F)Tube Wall Resistance (hr-ft 2-&deg;F/BTU Overall Fouling (hr-ft 2-.F/BTU)U Overall (BTU/hr ft 2.0 F)Effective Area (fl 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 2650655==
10,824.91 1,108,052 1,108,052 m Extrapolation Calculation for Row l(Dry)U Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ftlhr)
Skin Vise (lbm/fthr)
Density (Ibm/fl 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr"ft'&deg;F)
Air-Side 114,411.37 150.00 142.66 0.0203 0.0203 146.33 123.53 4,509.16 1,004 0.7253 0.0491 0.0621 0.2402 0.0163 Tube-Side 89,409.99 115.04 117.39 116.22 118.30 5.53 38,688 3.7810 1.3959 1.3683 61.7694 0.9988 0.3687 Tube-Side hi (BTU/hr-ft2-&deg;F) 1,656.77 j Factor 0.0069 Air-Side ho (BTU/hr'fi2"&deg;F) 9.31 Tube Wall Resistance (hr-ff2.F/BTU 

==0.0 0029413==
Overall Fouling (hr-ft2. F/BTU) 0.02650655 U Overall (BTU/hr'ft2.&deg;F)
Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.48 1,082.49 29.95 210,078 0.9185 210,078 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 4 of 17*** Air Mass Velocity (Lbmlhr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:36:35 PROTO-IIX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/06/98---------------, -~- ------ St Extrapolation Calculation for Row 2(Dry)II 1.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbmlrfthr)
Density (lbm/ft3)Cp (BTU/Ibm-'F)
K (BTU/hr'ft'&deg;F)
Air-Side 114,411.37 142.66 136.46 0.0203 0.0203 139.56 120.24 4,509.16 1,013 0.7259 0.0487 0.0628 0.2402 0.0161 Tube-Side 89,409.99 113.05 115.04 114.05 115.82 5.53 37,880 3.8695 1.4256 1.4012 61.8016 0.9988 0.3680 Tube-Side hi (BTU/hr ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft 2-&deg;F)Tube Wall Resistance (hr-ft 2 .F/BTU Overall Fouling (hr-ft 2-F/BTU)U Overall (BTU/hr. ft 2 -F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)1,637.70 0.0069 9.28 0.00029413

==0.0 2650655==
6.46 1,082.49 25.38 177,423 0.9188 177,423 W -Extrapolation Calculation for Row 3(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ftrhr)
Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ftf'F)
Air-Side 114,411.37 136.46 131.22 0.0203 0.0203 133.84 117.46 4,509.16 1,020 0.7264 0.0484 0.0633 0.2402 0.0160 Tube-Side 89,409.99 111.37 113.05 112.21 113.73 5.52 37,203 3.9470 1.4516 1.4301 61.8283 0.9988 0.3673 Tube-Side hi (BTU/hr-ft2.&deg;F) 1,621.52 j Factor 0.0069 Air-Side ho (BTU/hr.ft 2"&deg;F) 9.25 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-F/BTU) 0.02650655 U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.44 1,082.49 21.52 149,990 0.9190 149,990 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 5 of 17* Air Mass Velocity (Lbm/hr'ft 2 , Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 12:36:35 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/06/98 Extrapolation Calculation for Row 4(Dry)II-n I1 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (ibm/ftRhr)
Skin Visc (lbm/ft-hr)
Density (ibm/fl 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-PF)
Air-Side 114,411.37 131.22 126.79 0.0203 0.0203 129.01 115.12 4,509.16 1,026 0.7268 0.0481 0.0638 0.2402 0.0159 Tube-Side 89,409.99 109.95 111.37 Tube-Side hi (BTU/hr ft 2.F) 1,607.81 j Factor 0.0069 Air-Side ho (BTU/hr-ft 2.F) 9.23 Tube Wall Resistance (hr'ft 2.'F/BTU 0.00029413 Overall Fouling (hr-ft 2 1-F/BTU) 0.02650655 110.66 111.96 5.52 36,633 4.0145 1.4742 1.4553 61.8506 0.9988 0.3668 U Overall (BTU/hr.ft 2.&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.42 1,082.49 18.25 126,904 0.9192 126,904 m Extrapolation Calculation for Row 5(Dry)II Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (oF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fl-hr)
Skin Visc (Ibrn/ft-hr)
Density (lbM/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 114,411.37 126.79 123.04 0.0203 0.0203 124.91 113.13 4,509.16 1,032 0.7271 0.0478 0.0642 0.2402 0.0158 Tube-Side 89,409.99 108.75 109.95 109.35 110.46 5.52 36,154 4.0731 1.4937 1.4772 61.8692 0.9988 0.3663 Tube-Side hi (BTU/hr ft2.&deg;F) 1,596.17 j Factor 0.0069 Air-Side ho (BTU/hr.ft 2.OF) 9.21 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02650655 U Overall (BTU/hr. ft 2--F)Effective Area LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.41 1,082.49 15.48 107,447 0.9193 107,447 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 6 of 17*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:36:35 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/06/98------ -. -.--' II Extrapolation Calculation for Row 6(Dry)II~11 Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (7F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbrn/ft-hr)
Skin Visc (Ibm/fl'hr)
Density (Ibm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr-ft--F)
Air-Side 114,411.37 123.04 119.86 0.0203 0.0203 121.45 111.45 4,509.16 1,037 0.7273 0.0476 0.0646 0.2402 0.0157 Tube-Side 89,409.99 107.73 108.75 108.24 109.18 5.52 35,749 4.1238 1.5106 1.4963 61.8847 0.9988 0.3659 Tube-Side hi (BTU/hr-ft-'&deg;F) 1,586.30 j Factor 0.0069 Air-Side ho (BTU/hr. ft 2-&deg;F) 9.19 Tube Wall Resistance (hr'ft-'&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr' ft 2'F/BTU) 0.02650655 U Overall (BTU/hr'ft 2-'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.40 1,082.49 13.14 91,027 0.9195 91,027 Extrapolation Calculation for Row 7(Dry)II II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbrn/ftihr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ftl)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 114,411.37 119.86 117.16 0.0203 0.0203 118.51 110.02 4,509.16 1,041 0.7275 0.0474 0.0649 0.2402 0.0156 Tube-Side 89,409.99 106.87 107.73 Tube-Side hi (BTU/hr-ft 2.'F) 1,577.92 j Factor 0.0069 Air-Side ho (BTU/hr'ft 2"&deg;F) 9.18 Tube Wall Resistance (hr-ft2.&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr-ft 2.F/BTU) 0.02650655 107.30 108.10 5.52 35,407 4.1676 1.5252 1.5128 61.8977 0.9989 0.3656 U Overall (BTU/hrft 2-&deg;F)Effective Area (ftf)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.39 1,082.49 11.15 77,156 0.9196 77,156 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 7 of 17*** Air Mass Velocity (Lbm/hrftl 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:36:35 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/06/98 Extrapolation Calculation for Row 8(Dry)--1I I.Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (Ibm/ftrhr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr-ft.&deg;F)
Air-Side 114,411.37 117.16 114.87 0.0203 0.0203 116.02 108.81 4,509.16 1,044 0.7277 0.0472 0.0651 0.2402 0.0156 Tube-Side 89,409.99 106.13 106.87 106.50 107.18 5.52 35,119 4.2053 1.5378 1.5270 61.9087 0.9989 0.3653 Tube-Side hi (BTU/hr. ft 2-&deg;F) 1,570.80 j Factor 0.0068 Air-Side ho (BTU/hr ft 2.&deg;F) 9.17 Tube Wall Resistance (hr-ft 2-.F/BTU 0.00029413 Overall Fouling (hr'ft 2-&deg;F/BTU) 0.02650655 U Overall (BTU/hr-ft 2 .F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.38 1,082.49 9.47 65,428 0.9197 65,428 Extrapolation Calculation for Row 9(Dry)II Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftihr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/1bm.&deg;F)
K (BTU/hr-ft'&deg;F)
Air-Side 114,411.37 114.87 112.94 0.0203 0.0203 113.90 107.79 4,509.16 1,047 0.7278 0.0471 0.0654 0.2402 0.0155 Tube-Side 89,409.99 105.51 106.13 105.82 106.41 5.52 34,875 4.2377 1.5485 1.5393 61.9179 0.9989 0.3650 Tube-Side hi (BTU/hr-ft 2-.F) 1,564.76 j Factor 0.0068 Air-Side ho (BTU/hr.ft 2.0 F) 9.16 Tube Wall Resistance (hrft 2 0.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr.ft 2-IF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTUihr)6.38 1,082.49.8.04 55,502 0.9198 55,502 Proto-Power Calc: 97-199 

==Attachment:==

E Air Mass Velocity (Lbmhrft 2  TbhRev: A Page r of 17*** ir assVelcity(Lbnih~ft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:36:35 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/06/98 E Extrapolation Calculation for Row 10(Dry)11 Mass Flow (Ibm/hr)Inlet Temperature (7F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (7F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr-ft-.F)
Air-Side 114,411.37 112.94 111.29 0.0203 0.0203 112.11 106.92 4,509.16 1,050 0.7279 0.0470 0.0655 0.2402 0.0155 Tube-Side 89,409.99 104.99 105.51 105.25 105.74 5.52 34,668 4.2655 1.5578 1.5498 61.9257 0.9989 0.3648 Tube-Side hi (BTU/hr. ft 2-'F) 1,559.62 j Factor 0.0068 Air-Side ho (BTU/hr- ft 2.'F) 9.15 Tube Wall Resistance (hr-fl 2 .F/BTU 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr. ft 2.'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.37 1,082.49 6.83 47,097 0.9198 47,097 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 9 of 17*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:54:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-Effective Coil Length 07/06/98 Air Coil Heat Exchanger Input Parameters 
]1 Fl idiQiffil t ..Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 31.700-a-6Y fffi..150.00 OF 92.00 OF 108.80 OF 84.00 OF Tube-Side[...180100-gpmii 105.00 OF 117.70 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Fresh Water 0.001500 0.000000 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-.F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-&deg;F) 108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 10 of 17 12:54:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000) 7/6/98 ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-Effective Coil Length Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out (&deg;F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Condensate Temperature (TF)Extrapolation Data Tube Flow (gpm) 180.00 Air Flow (acfin) 31,066.00 Tube Inlet Temp (TF) 105.00 Air Inlet Temp (&deg;F) 150.0 Inlet Relative Humidity (%) 0.00 Inlet Wet Bulb Temp ('F) 92.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 11 of 17 12:54:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-Effective Coil Length 07/06/98 Extrapolation Calculation Summary-1 Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft.hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/fl 3)Cp (BTU/lbm-'F)
K (BTU/hr'ft'&deg;F)
Air-Side 114,411.37 150.00 111.46 Tube-Side 89,409.99 105.00 117.35 Tube-Side hi (BTU/hr ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-fl 2.&deg;F)Tube Wall Resistance (hr-fVt2-F/BTU Overall Fouling (hr-ftV.&deg;F/BTU)
U Overall (BTU/hr-ft 2 -F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 2650655==
10,532.34 1,103,074 1,103,074 Extrapolation Calculation for Row l(Dry)II I. 'I Mass Flow (lbm/hr)Inlet Tepiperature (fF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft.hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 114,411.37 150.00 142.75 0.0203 0.0203 146.38 123.61 4,634.41 1,032 0.7253 0.0491 0.0621 0.2402 0.0163 Tube-Side 89,409.99 115.02 117.35 116.19 118.30 5.53 38,677 3.7822 1.3963 1.3683 61.7698 0.9988 0.3687 Tube-Side hi (BTU/hr.ft2.&deg;F) 1,656.59 j Factor 0.0069 Air-Side ho (BTU/hr-ft2-*F) 9.48 Tube Wall Resistance (hr-ft 2-.F/BTU 0.00029413 Overall Fouling (hr-fl 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr-fl2-&deg;F)
Effective Area (f 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.56 1,053.23 30.03 207,516 0.9172 207,516 Proto-Power Cale: 97-199 

==Attachment:==

E Rev: A Page 12 of 17*** Air Mass Velocity (Lbnl/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:54:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-Effective Coil Length 07/06/98-I---N Extrapolation Calculation for Row 2(Dry)_______il Air-Side Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K 114,411.37 142.75 136.61 0.0203 0.0203 139.68 120.34 4,634.41 1,041 0.7259 0.0487 0.0628 0.2402 0.0161 Tube-Side 89,409.99 113.06 115.02 Tube-Side hi (BTU/hur.ft 2 .F) 1,637.72 j Factor 0.0069 Air-Side ho (BTU/hr ft 2-&deg;F) 9.45 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr ft 2.&deg;F/BTU) 0.02650655 114.04 115.85 5.53 37,878 3.8698 1.4257 1.4009 61.8017 0.9988 0.3680 U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.54 1,053.23 25.51 175,692 0.9175 175,692 Extrapolation Calculation for Row 3(Dry)II Mass Flow (Ibmlhr)Inlet Tem.perature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbmr/ft'hr)
Density (lbmrfl 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 114,411.37 136.61 131.41 0.0203 0.0203 134.01 117.58 4,634.41 1,048 0.7264 0.0484 0.0633 0.2402 0.0160 Tube-Side 89,409.99 111.39 113.06 112.22 113.77 5.52 37,207 3.9466 1.4515 1.4295 61.8282 0.9988 0.3673 Tube-Side hi (BTU/hr-ft 2.&deg;F) 1,621.68 j Factor 0.0068 Air-Side ho (BTU/hr-ft 2.`F) 9.42 Tube Wall Resistance (hr-ft 2-.F/BTU 0.00029413 Overall Fouling (hrft2. F/BTU) 0.02650655 U Overall (BTU/hr-ft2-&deg;F)
Effective Area (fl 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.52 1,053.23 21.68 148,890 0.9177 148,890 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 13 of 17*** Air Mass Velocity (Lbm/hr-ft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:54:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-Effective Coil Length 07/06/98 in Extrapolation Calculation for Row 4(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbmrft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 114,411.37 131.41 127.00 0.0203 0.0203 129.21 115.24 4,634.41 1,055 0.7267 0.0481 0.0638 0.2402 0.0159 Tube-Side 89,409.99 109.98 111.39 110.68 112.01 5.52 36,641 4.0136 1.4739 1.4546 61.8503 0.9988 0.3668 Tube-Side hi (BTU/hr ft 2.&deg;F) 1,608.04 j Factor 0.0068 Air-Side ho (BTU/hr ft2. F) 9.40 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr- ft 2-F/BTU) 0.02650655 U Overall (BTU/hr. ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.51 1,053.23 18.43 126,279 0.9179 126,279 Extrapolation Calculation for Row 5(Dry)II Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbmi/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr.ft-&deg;F)
Air-Side 114,411.37 127.00 123.26 0.0203 0.0203 125.13 113.25 4,634.41 1,060 0.7270 0.0478 0.0642 0.2402 0.0158 Tube-Side 89,409.99 108.78 109.98 109.38 110.51 5.52 36,163 4.0720 1.4934 1.4765 61.8688 0.9988 0.3663 Tube-Side hi (BTU/hr-fVl2.F) 1,596.45 j Factor 0.0068 Air-Side ho (BTU/hr ft 2.&deg;F) 9.38 Tube Wall Resistance (hr ft2.&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr-ft 2-F/BTU) 0.02650655 U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.49 1,053.23 15.67 107,176 0.9180 107,176 Proto-Power Cale: 97-199 

==Attachment:==

E Rev: A Page 14 of 17*** Air Mass Velocity (Lbbm/hr-ft 2), Tube Fluid Velocity (ft/sec)&#xfd; Air Density at Inlet T, Other Properties at Average T 12:54:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-Effective Coil Length 07/06/98 M -I Extrapolation Calculation for Row 6(Dry)II Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3 )Cp (BTU/lbma'F)
K (BTU/hr-ft.&deg;F)
Air-Side 114,411.37 123.26 120.08 0.0203 0.0203 121.67 111.56 4,634.41 1,065 0.7273 0.0476 0.0645 0.2402 0.0157 Tube-Side 89,409.99 107.76 108.78 108.27 109.23 5.52 35,759 4.1226 1.5102 1.4955 61.8843 0.9988 0.3659 Tube-Side hi (BTU/hr ft 2.&deg;F) 1,586.58 j Factor 0.0068 Air-Side ho (BTU/hr'ft 2-'F) 9.36 Tube Wall Resistance (hr-ft -&deg;F/BTU 0.00029413 Overall Fouling (hr ft 2-&deg;F/BTU) 0.02650655 U Overall (BTU/hr'ft 2-.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.48 1,053.23 13.33 91,017 0.9182 91,017 w Extrapolation Calculation for Row 7(Dry)___________I U.Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fi-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 114,411.37 120.08 117.37 0.0203 0.0203 118.72 110.13 4,634.41 1,069 0.7275 0.0474 0.0649 0.2402 0.0157 Tube-Side 89,409.99 106.89 107.76 107.32 108.15 5.52 35,417 4.1664 1.5248 1.5120 61.8974 0.9989 0.3656 Tube-Side hi (BTU/hr.ft 2.'F) 1,578.19 j Factor 0.0068 Air-Side ho (BTU/hrft2.&deg;'F) 9.35 Tube Wall Resistance (hr-ft2-&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hr-ft2.&deg;F)
Effective Area (f12)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.47 1,053.23 11.34 77,332 0.9183 77,332 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 15 of 17*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:54:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-Effective Coil Length 07/06/98 Extrapolation Calculation for Row 8(Dry)!I 1.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fr-hr)
Skin Visc (lbm/ft-hr)
Density (ibm/fl 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-fi.&deg;F)
Air-Side 114,411.37 117.37 115.08 0.0203 0.0203 116.23 108.91 4,634.41 1,073 0.7277 0.0472 0.0651 0.2402 0.0156 Tube-Side 89,409.99 106.16 106.89 106.52 107.23 5.52 35,127 4.2042 1.5374 1.5263 61.9084 0.9989 0.3653 Tube-Side hi (BTUihr.ft 2.&deg;F) 1,571.05 j Factor 0.0068 Air-Side ho (BTU/hr ft 2_-F) 9.34 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr. ft 2.&deg;F)Effective Area (ft1)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.46 1,053.23 9.65 65,733 0.9184 65,733 Extrapolation Calculation for Row 9(Dry)11 I.Mass Flow (lbm/hr)Inlet Temiperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ftV)Cp (BTU/lbm.'F)
K (BTU/hr-ft.
0 F)Air-Side 114,411.37 115.08 113.12 0.0203 0.0203 114.10 107.87 4,634.41 1,076 0.7278 0.0471 0.0653 0.2402 0.0156 Tube-Side 89,409.99 105.53 106.16 105.84 106.44 5.52 34,881 4.2368 1.5482 1.5386 61.9176 0.9989 0.3650 Tube-Side hi (BTU/hr-ft 2.&deg;F) 1,564.97 j Factor 0.0068 Air-Side ho (BTU/hr'fl 2-&deg;F) 9.33 Tube Wall Resistance (hrft 2 0-&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-F/BTU) 0.02650655 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.46 1,053.23 8.22 55,895 0.9184 55,895 Proto-Power Calc: 97-199 

==Attachment:==

E Rev: A Page 16 of 17***Air Mass Velocity (Lbmi/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 12:54:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-Effective Coil Length 07/06/98 I'-Extrapolation Calculation for Row 10(Dry)-11 Mass Flow (lbn/hr)Inlet Temperature (fF)Outlet Temperature (1F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ftrhr)
Skin Vise (1bm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-.F)
Air-Side 114,411.37 113.12 111.46 0.0203 0.0203 112.29 106.99 4,634.41 1,079 0.7279 0.0470 0.0655 0.2402 0.0155 Tube-Side 89,409.99 105.00 105.53 105.26 105.78 5.52 34,673 4.2648 1.5575 1.5493 61.9255 0.9989 0.3648 Tube-Side hi (BTU/hr'fl2"&deg;F) 1,559.79 j Factor 0.0068 Air-Side ho (BTU/hrfi2.&deg;F) 9.32 Tube Wall Resistance (hr ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ftt.&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hr-ft 2 .F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.45 1,053.23 7.00 47,543 0.9185 47,543 Proto-Power Cale: 97-199 

==Attachment:==

E Rev: A Page 17 of 17*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet ', Other Properties at Average T Attachment F to Proto-Power Calculation 97-199 Revision A Proto-Power Catc: 97-199 

==Attachment:==

F Rev: A Page 1 of 9 13:38:02 PROTO-IIX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/06/98 Air Coil Heat Exchanger Input Parameters Air-Side Fliiid-Quaniiiyy, 3-1.0-6-600 acriW Inlet Dry Bulb Temp 150.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature 108.80 OF Outlet Wet Bulb Temp 84.00 OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Tube-Side_T8.T07Ugpm 105.00 OF 117.70 OF Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Perfonnance Factor (% Reduction)
Fresh Water 0.001500 0.000000 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft 0.F)Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-&deg;F) 108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

F Rev: A Page 2 of 9 13:38:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Data Date Air Flow (acfin)Air Dry Bulb Temp In (fF)Air Dry Bulb Temp Out (fF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (fF)Wet Bulb Temp Out (fF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Condensate Temperature 
(&deg;F)Extrapolation Data ._Tube Flow (gpm) 180.00 Air Flow (acfin) 28,445.00 Tube Inlet Temp (0 F) 100.00 Air Inlet Temp (0 F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (0 F) 0.00 Atmospheric Pressure 14.315 Input Fouling Factor 0.000000 Proto-Power Calc: 97-199 

==Attachment:==

F Rev" A Page 3 of 9 13:38:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/06/98 a I Extrapolation Calculation Summary 11 I. *1 Air-Side Mass Flow (lbm/hr) 105,113.87 Inlet Temperature (0 F) 148.00 Outlet Temperature (0 F) 104.31 Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ft-'F)
Tube-Side 89,504.32 100.00 112.84 Tube-Side hi (BTU/hrft 2 0.&deg;F)j Factor Air-Side ho (BTU/hr-ftV.
0 F)Tube Wall Resistance (hr-ft2-&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr-ft 2--F/BTU)U Overall (BTU/hr- ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)10,532.34 1,148,793 1,148,793 Extrapolation Calculation for Row l(Dry)II Mass Flow (Ibm/hr)Inlet Temperature (fF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm 0'F)K (BTU/hr-ft-&deg;F)
Air-Side 105,113.87 148.00 138.46 0.0203 0.0203 143.23 114.13 4,257.80 952**0.7256 0.0489 0.0626 0.2402 0.0162 Tube-Side 89,504.32 110.04 112.84 111.44 114.06 5.53 36,957 3.9804 1.4628 1.4254 61.8395 0.9988 0.3671 Tube-Side hi (BTU/hr.ft 2.0 F) 1,618.75 j Factor 0.0071 Air-Side ho (BTU/hr'ft 2 i.F) 8.96 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr.ft 2.&deg;F/BTU)U Overall (BTU/hr.fV2-0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTUihr)7.55 1,053.23 31.54 250,885 0.9214 250,885** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

F Rev: A Page 4 of 9*** Air Mass Velocity (Lbni/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 13:38:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/06/98 Extrapolation Calculation for Row 2(Dry)mm II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft'hr)
Skin Vise (lbm/ft-hr)
Density (Ibm/fP)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 105,113.87 138.46 130.78 0.0203 0.0203 134.62 111.10 4,257.80 962*1 0.7263 0.0484 0.0634 0.2402 0.0160 Tube-Side 89,504.32 107.78 110.04 108.91 111.05 5.53 36,030 4.0932 1.5004 1.4685 61.8754 0.9988 0.3661 Tube-Side hi (BTU/hr ft 2-F) 1,596.04 j Factor 0.0070 Air-Side ho (BTU/hr'ft 2'&deg;F) 8.92 Tube Wall Resistance (hr-ft2.&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.52 1,053.23 25.51 201,932 0.9217 201,932** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/fl'hr)
Skin Vise (Ibm/fl-hr)
Density (lbmr/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft'&deg;F)
Air-Side 105,113.87 130.78 124.59 0.0203 0.0203 127.68 108.66 4,257.80 971*0.7269 0.0480 0.0641 0.2402 0.0159 Tube-Side 89,504.32 105.96 107.78 106.87 108.61 5.52 35,289 4.1878 1.5320 1.5049 61.9036 0.9989 0.3654 Tube-Side hi (BTU/hr-ftV.&deg;F) 1,577.67 j Factor 0.0070 Air-Side ho (BTU/hr.ft2-&deg;F) 8.88 Tube Wall Resistance (hr-fl 2.&deg;F/BTU 0.00029413 Overall Fouling (hr.ft2. F/BTU)U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.49 1,053.23 20.65 162,834 0.9219 162,834** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

F Rev: A Page 5 of 9*** Air Mass Velocity (Lbm/hrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 13:38:02 PROTO-iHX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/06/98 a -Extrapolation CJalculation for Row 4(Dry)II IJ Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ftthr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-fti.F)
Air-Side 105,113.87 124.59 119.59 0.0203 0.0203 122.09 106.68 4,257.80 978**0.7273 0.0476 0.0646 0.2402 0.0157 Tube-Side 89,504.32 104.49 105.96 105.22 106.64 5.52 34,695 4.2668 1.5582 1.5355 61.9260 0.9989 0.3648 Tube-Side hi (BTU/hr-flt'&deg;F) 1,562.80 j Factor 0.0070 Air-Side ho (BTU/ihr ft2.F) 8.86 Tube Wall Resistance (hr ft2. F/BTU 0.00029413 Overall Fouling (hr'ft 2-&deg;F/BTU)U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.46 1,053.23 16.73 131,505 0.9221 131,505** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)11 Mass Flow (ibm/hr)Inlet Temperature (OF)Outlet T'emperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftlhr)
Skin Visc (lbm/ft'hr)
Density (lbm/fV)Cp (BTU/Ibm-'F)
K (BTU/hr-ft.&deg;F)
Air-Side 105,113.87 119.59 115.54 0.0203 0.0203 117.56 105.08 4,257.80 984*, 0.7276 0.0473 0.0651 0.2402 0.0156 Tube-Side 89,504.32 103.30 104.49 103.89 105.05 5.52 34,217 4.3324 1.5799 1.5609 61.9438 0.9989 0.3643 Tube-Side hi (BTU/hr-ft 2-.F) 1,550.75 j Factor 0.0070 Air-Side ho (BTU/hr-ftV-&deg;F) 8.84 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr ft2.&deg;F/BTU)
U Overall (BTU/hr-ft 2.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.44 1,053.23 13.57 106,333 0.9223 106,333** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

F Rev: A Page 6 of 9*** Air Mass Velocity (LbmL/hrft'), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 13:38:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/06/98 Extrapolation Calculation for Row 6(Dry)II I. *1 Air-Side Mass Flow (lbm/hr) 105,113.87 Inlet Temperature (OF) 115.54 Outlet Temperature (OF) 112.27 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 113.91 Skin Temperature (OF) 103.78 Velocity *** 4,257.80 Reynold's Number 989**Prandtl Number 0.7278 Bulk Visc (bmi/ft-hr) 0.0471 Skin Visc (lbm/ft-hr)
Density (lbm/ft 3) 0.0654 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0155 Tube-Side 89,504.32 102.33 103.30 102.82 103.76 5.52 33,833 4.3867 1.5979 1.5821 61.9580 0.9989 0.3639 Tube-Side hi (BTU/hr fl 0-&deg;F) 1,540.98 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.0 F) 8.82 Tube Wall Resistance (hr-ft2. F/BTU 0.00029413 Overall Fouling (hr fl 2-&deg;F/BTU)U Overall (BTU/hr ft 2-.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.43 1,053.23 11.00 86,065 0.9224 86,065** Reynolds Number Outside Range of Equation Applicability I, ,-am &#xfd;1 Extrapolation Calculation for Row 7(Dry)II I. *1 Mass Flow (lbm/hr)Inlet Te~nperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-fr&deg;F)
Air-Side 105,113.87 112.27 109.62 0.0203 0.0203 110.94 102.73 4,257.80 993**0.7280 0.0469 0.0657 0.2402 0.0155 Tube-Side 89,504.32 101.55 102.33 101.94 102.71 5.52 33,523 4.4314 1.6127 1.5996 61.9694 0.9990 0.3635 Tube-Side hi (BTU/hr-ft 2 -F) 1,533.06 j Factor 0.0070 Air-Side ho (BTU/hr ft2.&deg;F) 8.81 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-F/BTU)U Overall (BTU/hr ft 2.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.41 1,053.23 8.93 69,716 0.9225 69,716** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

F Rev: A Page 7 of 9*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 13:38:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/06/98 Extrapolation Calculation for Row 8(Dry)11 ii Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft'hr)
Density (lbm/ft 3)Cp (BTU/Ibm-'F)
K (BTU/hr-fti'F)
Air-Side 105,113.87 109.62 107.47 0.0203 0.0203 108.54 101.88 4,257.80 996**0.7281 0.0467 0.0660 0.2402 0.0154 Tube-Side 89,504.32 100.92 101.55 101.24 101.86 5.52 33,272 4.4682 1.6248 1.6140 61.9785 0.9990 0.3633 Tube-Side hi (BTU/hr-ft2.&deg;F) 1,526.63 j Factor 0.0070 Air-Side ho (BTU/hr'ft 2-&deg;F) 8.80 Tube Wall Resistance (hr-ft 2 l-F/BTU 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU)U Overall (BTU/hr'ft 2 -F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.40 1,053.23 7.25 56,510 0.9226 56,510** Reynolds Number Outside Range of Equation Applicability.S -11 Extrapolation Calculation for Row 9(Dry)11I I.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/fi-hr)
Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 105,113.87 107.47 105.73 0.0203 0.0203 106.60 101.19 4,257.80 999**0.7282 0.0466 0.0662 0.2402 0.0154 Tube-Side 89,504.32 100.41 100.92 100.67 101.18 5.52 33,069 4.4984 1.6348 1.6259 61.9859 0.9990 0.3630 Tube-Side hi (BTU/hr ft 2.0 F) 1,521.42 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2"&deg;F) 8.79 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr- f2-&deg;F/BTU)
U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.39 1,053.23 5.89 45,830 0.9227 45,830** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

F Rev: A Page 8 of 9*** Air Mass Velocity (Lbmilhr-ft 2), rube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 13:38:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/06/98 m Extrapolation Calculation for Row 10(Dry)I.Mass Flow (lbm/hr)Inlet Temperature 
'('F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (1bm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr-fti.F)
Air-Side 105,113.87 105.73 104.31 0.0203 0.0203 105.02 100.63 4,257.80 1,001 0.7283 0.0465 0.0664 0.2402 0.0153 Tube-Side 89,504.32 99.99 100.41 100.20 100.62 5.52 32,905 4.5231 1.6429 1.6357 61.9918 0.9990 0.3629 Tube-Side hi (BTU/hr. ft 2 .F) 1,517.18 j Factor 0.0069 Air-Side ho (BTU/hr. ft2 -F) 8.78 Tube Wall Resistance (hr ft 2 -F/BTU 0.00029413 Overall Fouling (hr. ft 2-F/BTU)U Overall (BTU/hrft2.'1F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.39 1,053.23 4.78 37,184 0.9228 37,184 Proto-Power Calc: 97-199 

==Attachment:==

F Rev: A Page 9 of 9*** Air Mass Velocity (Lbminhr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Attachment G to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

G Rev: A .Page 1 of 9 13:11:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/06/98 Air Coil Heat Exchanger Input Parameters Fl Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperatui Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 150.00 OF 92.00 OF re 108.80 OF 84.00 OF Tube-Side..180 .q 0 gpm 105.00 OF 117.70 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Fresh Water 0.001500 0.000000 1,108,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F) 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

G Rev: A Page 2 of 9 13:11:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In ("F)Air Dry Bulb Temp Out (OF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (OF)Wet Bulb Temp Out (OF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ("F)Tube Temp Out ("F)Condensate Temperature 
("F)Extrapolation Data Tube Flow (gpm) 180.00 Air Flow (acfmn) 28,352.00 Tube Inlet Temp ("F) 100.00 Air Inlet Temp ("F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ("F) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

G Rev: A Page 3 of 9 13:11:36 PROTO-HX 3.01 by Proto-Powver Corporation (SN#PHX-0000)
ComnEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/06/98 Extrapolation Calculation Summary II?L,-- -Mass Flow (ibm/hr)Inlet Temperature (OF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/fl 3)Cp (BTU/lbm-'F)
K (BTU/hr-ftI-F)
Air-Side 104,770.20 148.00 106.16 Tube-Side 89,504.32 100.00 112.28 Tube-Side hi (BTU/hr-ft 2-&deg;F)j Factor Air-Side ho (BTU/hr'ft 2.'F)Tube Wall Resistance (hr-fi 2"&deg;F/BTU Overall Fouling (hr'ft 2"&deg;F/BTU)U Overall (BTU/Ir- ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 2650655==
10,532.34 1,096,666 1,096,666 ED=Extrapolation Calculation for Row l(Dry)II I.Air-Side Tube-Side Mass Flow (lbm/hr) 104,770.20 Inlet Temperature (OF) 148.00 Outlet Temperature (OF) 139.76 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 143.88 Skin Temperature (OF) 118.86 Velocity *** 4,243.88 Reynold's Number 948*" Prandtl Number 0.7255 Bulk Visc (Ibm/ft-hr) 0.0490 Skin Visc (lbm/ft-hr)
Density (lbm/ft 3) 0.0624 Cp (BTU/Ibm'&deg;F) 0.2402 K (BTU/hr'ft'&deg;F) 0.0162 89,504.32 109.87 112.28 111.07 113.33 5.53 36,823 3.9964 1.4681 1.4357 61.8447 0.9988 0.3669 Tube-Side hi (BTU/hr- ft2-&deg;F) 1,614.82 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.94 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr-ft2.&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hr-f2-&deg;OF)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.28 1,053.23 32.63 215,928 0.9215 215,928** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

G Rev: A Page 4 of 9*** Air Mass Velocity (Lbrm/hr'ft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 13:11:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/06/98 0 -Extrapolation Calculation for Row 2(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft hr)Density (lbm/ft3)Cp (BTU/Ibm-'F)
K (BTU/hr.ft.&deg;F)
Air-Side 104,770.20 139.76 132.89 0.0203 0.0203 136.32 115.37 4,243.88 957**0.7262 0.0485 0.0632 0.2402 0.0160 Tube-Side 89,504.32 107.85 109.87 108.86 110.76 5.53 36,012 4.0954 1.5012 1.4727 61.8761 0.9988 0.3661 Tube-Side hi (BTU/hr-ft 2.&deg;F) 1,595.10 j Factor 0.0071 Air-Side ho (BTU/hr'ft 2"&deg;F) 8.90 Tube Wall Resistance (hr.ft2- F/BTU 0.00029413 Overall Fouling (hr-ft 2.F/BTU) 0.02650655 U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.26 1,053.23 27.32 180,133 0.9218 180,133** Reynolds Number Outside Range of Equation Applicability
~Ar Extrapolation Calculation for Row 3(Dry)II Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbrn/ft'hr)
Density (Ibm/fl 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr'ft-'F)
Air-Side 104,770.20 132.89 127.15 0.0203 0.0203 130.02 112.47 4,243.88 965**0.7267 0.0481 0.0638 0.2402 0.0159 Tube-Side 89,504.32 106.17 107.85 107.01 108.62 5.52 35,340 4.1811 1.5297 1.5049 61.9017 0.9989 0.3654 Tube-Side hi (BTU/hr-ftV.&deg;F) 1,578.58 j Factor 0.0070 Air-Side ho (BTU/hr ft 2-F) 8.88 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft2.&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hr. fl 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.24 1,053.23.22.88 150,445 0.9220 150,445** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc. 97-199 

==Attachment:==

G Rev: A Page 5 of 9*** Air Mass Velocity (Lbm/lir-ft-), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 13:11:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/06/98 N Extrapolation Calculation for Row 4(Dry)Air-Side Mass Flow (lbm/hr) 104,770.20 Inlet Temperature (0 F) 127.15 Outlet Temperature (0 F) 122.35 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 124.75 Skin Temperature (0 F) 110.04 Velocity *** 4,243.88 Reynold's Number 971**Prandtl Number 0.7271 Bulk Vise (lbm/ft-hr) 0.0478 Skin Vise (Ibm/ft'hr)
Density (lbm/ft')
0.0643 Cp (BTU/Ibm'0 F) 0.2402 K (BTU/hr-ft.PF) 0.0158 Tube-Side 89,504.32 104.76 106.17 105.46 106.82 5.52 34,782 4.2550 1.5543 1.5327 61.9227 0.9989 0.3649 Tube-Side hi (BTU/hr'ft 2"&deg;F)j Factor Air-Side ho (BTU/hr" ft 2-'F)Tube Wall Resistance (hr- ft 2.F/BTU Overall Fouling (hr'ft 2 'F/BTU)U Overall (BTU/hr-ft 2"&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)1,564.74 0.0070 8.85 0.00029413

==0.0 2650655==
6.23 1,053.23 19.18 125,772 0.9222 125,772** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)II U.Mass Flow (lbmn/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Vise (lbmrft-hr)
Density (Ibm/ftV)Cp (BTU/lbm-0 F)K Air-Side 104,770.20 122.35 118.33 0.0203 0.0203 120.34 108.01 4,243.88 977*-0.7274 0.0475 0.0648 0.2402 0.0157 Tube-Side 89,504.32 103.58 104.76 104.17 105.32 5.52 34,318 4.3184 1.5753 1.5567 61.9401 0.9989 0.3644 Tube-Side hi (BTU/hr.ft 2.&deg;F) 1,553.14 j Factor 0.0070 Air-Side ho (BTU/hr'Rft 2"F) 8.83 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ftV-&deg;F/BTU) 

==0.0 2650655==
U Overall (BTU/hr ft 2-.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.24 1,053.23 16.08 105,231 0.9223 105,231** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

G Rev: A Page 6 of 9*** Air Mass Velocity (Lbrihr-ft 2), Tube Fluid Velocity (ftlsec);
Air Density at Inlet T, Other Properties at Average T 13:11:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/06/98 Extrapolation Calculation for Row 0(Dry)II 1.Air-Side Mass Flow (Ibm/hr) 104,770.20 Inlet Temperature 
(&deg;F) 118.33 Outlet Temperature (IF) 114.97 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 116.65 Skin Temperature (IF) 106.31 Velocity *** 4,243.88 Reynold's Number 982*1 Prandtl Number 0.7276 Bulk Visc (lbrn/ft-hr) 0.0473 Skin Visc (lbmr/fthr)
Density (Ibrn/ffl) 0.0651 Cp (BTU/Ibm-'F) 0.2402 K (BTU/hr'ftP'F) 0.0156 Tube-Side 89,504.32 102.60 103.58 103.09 104.05 5.52 33,931 4.3727 1.5933 1.5772 61.9544 0.9989 0.3640 Tube-Side hi (BTU/hr-ft 2-&deg;F)j Factor Air-Side ho (BTU/hr ft 2-&deg;F)Tube Wall Resistance (hr-ft 2-&deg;FfBTU Overall Fouling (hr. ft 2.&deg;F/BTU)U Overall (BTU/hr ft 2.&deg;F)Effective Area (f)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)1,543.40 0.0070 8.81 0.00029413

==0.0 2650655==
6.20 1,053.23 13.49 88,105 0.9225 88,105** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)II 1.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft'hr)
Density (Ibm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ft--F)
Air-Side 104,770.20 114.97 112.16 0.0203 0.0203 113.56 104.89 4,243.88 986*1 0.7278 0.0471 0.0655 0.2402 0.0155 Tube-Side 89,504.32 101.77 102.60 102.19 103.00 5.52 33,609 4.4189 1.6085 1.5948 61.9662 0.9990 0.3636 Tube-Side hi (BTU/hr ft'2"F) 1,535.25 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2"&deg;F) 8.80 Tube Wall Resistance (hr-ft 2.0 F/BTU 0.00029413 Overall Fouling (hr-ft2.0 F/BTT) 0.02650655 U Overall (BTU/hr-ft 2-IF)Effective Area (W)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.49 1,053.23.11.32 73,809 0.9226 73,809** Reynolds Number Outside Range of Equation Applicability Proto-power Calc: 97-199 

==Attachment:==
.
G Rev: A Page 7 of 9*** Air Mass Velocity (Lbnv'hrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 13:11:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/06/98*Extrapolation Calculation for Row 8(Dry)Air-Side Tube-Side Mass Flow (lbm/hr) 104,770.20 89,504.32 Tube-Side hi (BTU/hr-ft 2-&deg;F) 1,528.40 Inlet Temperature (IF) 112.16 101.08 j Factor 0.0070 Outlet Temperature (IF) 109.80 101.77 Air-Side ho (BTU/hr'ftV-&deg;F) 8.79 Inlet Specific Humidity 0.0203 Tube Wall Resistance (hr-ft 2.0 F/BTU 0.00029413 Outlet Specific Humidity 0.0203 Overall Fouling (hr-ft 2 l-F/BTU) 0.02650655 Average Temp (IF) 110.98 101.43 Skin Temperature (IF) 103.69 102.11 U Overall (BTU/hr'ft 2.F) 6.18 Velocity *** 4,243.88 5.52 Effective Area (ft 2) 1,053.23 Reynold's Number 990** 33,339 LMTD 9.50 Prandtl Number 0.7280 4.4583 Total Heat Transferred (BTU/hr) 61,863 Bulk Visc (lbm/ft-hr) 0.0469 1.6216 Skin Visc (lbm/ft-hr) 1.6098 Surface Effectiveness (Eta) 0.9227 Density (lbmr/ft) 0.0657 61.9761 Sensible Heat Transferred (BTU/hr) 61,863 Cp (BTU/lbm-&deg;F) 0.2402 0.9990 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft-.F) 0.0155 0.3633 Heat to Condensate (BTU/hr)** Reynolds Number Outside Range of Equation Applicability (Extrapolation Calculation for Row 9(Dry)Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ftP)Cp (BTU/Ibm.&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 104,770.20 109.80 107.82 0.0203 0.0203 108.81 102.69 4,243.880.7281 0.0468 0.0660 0.2402 0.0154 Tube-Side 89,504.32 100.50 101.08 100.79 101.37 5.52 33,114 4.4918 1.6326 1.6226 61.9842 0.9990 0.3631 Tube-Side hi (BTU/hr.ft 2-&deg;F) 1,522.65 j Factor 0.0070 Air-Side ho (BTU/hr-ft2.&deg;F) 8.78 Tube Wall Resistance (hr-ft 2'.F/BTU 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02650655 U Overall (BTU/hr ft 2 0-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.18 1,053.23 7.97 51,871 0.9228 51,871** Reynolds Number Outside Range of Equation Applicability V Proto-Power Calc: 97-199 

==Attachment:==

G Rev: A Page 8 of 9* Air Mass Velocity (Lbm/lhrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 13:11:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#PII X-0000)CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/06/98 M Extrapolation Calculation for Row 1O(Dry)ml II Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft&deg;F)
Air-Side 104,770.20 107.82 106.16 0.0203 0.0203 106.99 101.85 4,243.88 995**0.7282 0.0466 0.0661 0.2402 0.0154 Tube-Side 89,504.32 100.01 100.50 100.26 100.74 5.52 32,925 4.5201 1.6419 1.6335 61.9911 0.9990 0.3629 Tube-Side hi (BTU/hr-ft-'&deg;F) 1,517.83 j Factor 0.0070 Air-Side ho (BTU/hr'ft' 2.F) 8.77 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr ft 2 0-F/BTU) 0.02650655 U Overall (BTU/hr'ft 2.'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.17 1,053.23 6.69 43,508 0.9228 43,508** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

G Rev: A Page 9 of 9*** Air Mass Velocity (Lbrnhr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Attachment H to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

H Rev: A Page 1 of 18 Moist Air Properties Equations for calculating moist air properties are compiled and/or derived in Proto-Power Calculation 96-069, Reference (1), relying on References (2) and (3) as the principal sources of information.
This attachment summarizes the equations pertinent to the moist air conditions calculated for heat exchanger model development.
The applicable material has been extracted from Reference (1) leaving equation numbering as it appears in Reference (1) for ease of cross reference.
: 1. NOMENCLATURE ma = Mass of Dry Air, Ibm mv = Mass of Water Vapor, Ibm P = Atmospheric Pressure, lbf/in 2 Pa = Dry Air Pressure, lbf/in 2 PS = Saturated Air Pressure, lbf/in2 P, = Water Vapor Pressure, lbf/in 2 R. = Gas constant of Dry Air R, = Gas constant of Water Vapor T = Dry Bulb Temperature, 'F Tw = Wet Bulb Temperature, 'F V = Moist air Volume, ft 3 W = Moist air Specific Humidity xv= Mole Fraction of Water Vapor in Moist Air xS= Mole Fraction of Water Vapor in Saturated Air* = Moist Air Relative Humidity p = Moist air Density, ibm/ft 3 Pa = Dry Air Density, lbm/fi3 p, = Water Vapor Density, ibm/ft 3 2. REFERENCES (1) Proto-Power Calculation 96-069, Fluid Properties 
-Moist Air -Range 8&deg;F to 300'F, Revision -, dated 12/2/96 (2) Heating Ventilating, and Air Conditioning Analysis and Design, F. C. McQuiston and J. D.Parker, Second Edition, John Wiley & Sons, Inc., 1982 (3) ASHRAE Handbook 1981 Fundamentals, American Society of Heating, Refrigerating and Air Conditioning Engineers, Inc., 1982 Proto-Power Calc: 97-199 

==Attachment:==

H Rev: A Page 2 of 18 
: 3. MOIST AIR DENSITY For dry air: P = P-Pr.Equation [4]Equation [5]L144) P__ __" 1 ?"-) (459.67 + T)where: Rl = 53.352 (ft-lbf)/(Ibm-0 R)For water vapor: (144 _ P, pv= tR (459.67 +T)where: R, = 85.778 (ft-Ibf)/(lbm-"R)
For moist air: Equation [6]P =p. +P, 4. SATURATED WATER VAPOR PRESSURE P,(T)=a+bT+cT 2 +dT 3 +eT 4 4+Ts Where;a = 0.02358607 b = 0.001007276 c = 0.00001888033 d = 0.0000003775047 e = 4.871208E-10 f= 2.109071E-I 1 Equation [7]Equation [8]Proto-Power Calc: 97-199 

==Attachment:==

H Rev: A Page 3 of 18 
: 5. WATER VAPOR PRESSURE f(T,) =a + bT, + cT, 2 + dT,&#xfd;3 + e T,.' +fT P, (P, T, T) = [(2 T,, .- T- 2800)f(T)] 
-P(T,, -T)(Tr, -2800)Equation [9]Equation [10]Where: a = 0.02358607 b = 0.00 1007276 c = 0.00001888033 d = 0.0000003775047 e = 4.871208E-10 f= 2.109071E-11 WR, P R. +(wR,)Equation [ 11]6. MOIST AIR SPECIFIC HUMIDITY ma Pa Equation [12]Where: I P, V mv R, (459.67 + T)S Pa V ma =R(459.67 
+ T)Equation [13]Equation [ 14]7. MOIST AIR RELATIVE HUMIDITY X, Ps Equation [15]Proto-Power Calc: 97-199 

==Attachment:==

H Rev: A Page 4 of 18 6 Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Moist Air Relative Humidity: Saturated Air Pressure: Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Specific Humidity: Equation Coefficients:
> o 0 00 Given Dry Bulb and Relative Humidity RH =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =Pv = RH*Ps Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T))
Rho = Rho a + Rho v =W = Rho v/Rhoa =a-b=C=d=e=f=,,.Cc o e~t.. I' &#xfd;i 0it .14.315 70 40 0.363236046 0.145294418 14.16970558

==0.0 72204994==
0.000460501

==0.0 72665495==
0.006377682 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-1 0 2.109071 E-1 1 psia OF psia psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 Equation [8]Equation [15]Equation [4]Equation [5]Equation [6]Equation [7]Equation [12]
Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Wet Bulb Temperature:
Wet Bulb Temp. Function: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Specific Humidity: Moist Air Relative Humidity: Equation Coefficients:
Given Dry Bulb and Wet Bulb Temperatures P =14.315 T =150 Tw 92.00 F(Tw) = a+(b*Tw)+(c*Tw 2)+(d*Tw 3)+(e*Tw 4)+(f*Tw 5) = 0.743918919 Pv = (((2*Tw-T-2800)*F(Tw))-P*(Tw-T))/(Tw-2800) 
= 0.453253224 Pa =P -Pv = 13.86174678 Rho a = (144/53.352)*(Pa/(459.67+T)) 
= 0.061367004 Rho v = (144/85.778)*(Pv/(459.67+T)) 
= 0.001248052 Rho = Rho a + Rho v = 0.062615056 Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) = 3.721743953 W = Rho v / Rho a 0.020337508 RH = Pv/Ps = 12.17852 a = 2.358607E-02 b = 1.007276E-03 C = 1.888033E-05 d = 3.775047E-07 e = 4.871208E-10 f = 2.109071 E-1 1 psia OF OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Equation [9]Equation [10]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [12]Equation [15]0>0-0 0 0 3 .'- Col-I 6 Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Wet Bulb Temperature:
Wet Bulb Temp. Function: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Specific Humidity: Moist Air Relative Humidity: Equation Coefficients:
Given Dry Bulb and Wet Bulb Temperatures"., 14.315 T =148 Tw 91.60 F(Tw) = a+(b*Tw)+(c*Tw 2)+(d*Tw 3)+(e*Tw 4)+(f*Tw 5) = 0.734713202 Pv = (((2*Tw-T-2800)*F(Tw))-P*(Tw-T))/(Tw-2800) 
= 0.451915914 Pa =P -Pv = 13.86308409 Rho a = (144/53.352)*(Pa/(459.67+T)) 
= 0.061574919 Rho v = (144/85.778)*(Pv/(459.67+T)) 
= 0.001248465 Rho = Rho a + Rho v = 0.062823384 Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) = 3.541336347 W = Rho v / Rho a= 0.020275546 RH = Pv/Ps 12.76117 a = 2.358607E-02 b = 1.007276E-03 C = 1.888033E-05 d = 3.775047E-07 e = 4.871208E-10 f = 2.109071 E-1 I psia OF 'OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Equation [9]Equation [10]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [12]Equation [15]C 0 0 00 7 O.j~ 1/c~ 5>&L~o,~ e cc Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Moist Air Relative Humidity: Saturated Air Pressure: Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Specific Humidity: Equation Coefficients:
CD -0 C 0 0 Given Dry Bulb and Relative Humidity RH =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5)Pv = RH*Ps Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =W = Rho v / Rho a =a=b=C=d=e=f=14.315 148 12.76 3.541336347 0.451874518 13.86312548

==0.0 61575103==
0.001248351

==0.0 62823454==
0.020273629 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071 E-1 1 psia OF psia psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 Equation [8]Equation [15]Equation [4]Equation [5]Equation [6]Equation [7]Equation [12]0 00 t Moist Air Properties Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
-- Given Dry Bulb and Specific Humidity T=W=Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv/Ps =a=b=C=d=e=f=14.315 104.31 0.020273629 0.451874518 13.86312548

==0.0 66345159==
0.001345057

==0.0 67690216==
1.080650628 41.81504238 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-11 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Inlet Air Flow 28445.13627 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]0. 0 0 D Co C2.CD 0 l7-oo co I (00-A .7t 0 ( &#xfd;(C1eo~)
1'Moist Air Properties 
-- Given Dry Bulb and Specific Humidity Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
P =W _Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv /Ps =14.315 106.16 0.020273629 0.451874518 13.86312548

==0.0 66128241==
0.001340659

==0.0 67468901==
1.14119985 39.59644034 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-1 0 2.109071 E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft3 psia Inlet Air Flow 28352.13395 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]-01 0 00 ( -S .~C~a a.', Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
Given Dry Bulb and Specific Humidity W=Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv /Ps =a=b=C=d=e=f=14.315 106.85 0.020273629 0.451874518 13.86312548 0.0660477 0.001339027

==0.0 67386726==
1.164520875 38.80347081 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071 E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Inlet Air Flow 28317.60212 Equation [11]Equation [41 Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]-0 0 00-;4 O LA- H e- -&#xfd; C o V a t)
Moist Air Properties Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
-- Given Dry Bulb and Specific Humidity W =.Pv = (W*Rv*P)/(Ra+(W*Rv))
Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*Ts) =RH = Pv /Ps =a=b=C=d=e=f=14.315 111.85 0.020273629 0.451874518 13.86312548

==0.0 65469875==
0.001327312

==0.0 66797187==
1.34613727 33.56823468 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-1 0 2.109071E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Inlet Air Flow 28069.86274 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]0 0 HO S 6"" Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity:> Equation Coefficients:
0" 0 00 oo .Given Dry Bulb and Specific Humidity W=_Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv/Ps 14.315 112.24 0.020273629 0.451874518 13.86312548

==0.0 65425229==
0.001326407

==0.0 66751636==
1.361275803 33.19492765 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-1 0 2.109071E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 IbM/ft3 psia Inlet Air Flow 28050.72119 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15](GAS Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
00-0 00'"a ('UQ ole Given Dry Bulb and Specific Humidity T=W=Pv (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho= Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5)RH = Pv /Ps =a=b=C=d=e=f=14.315 109.52 0.020273629 0.451874518 13.86312548

==0.0 65737878==
0.001332745

==0.0 67070623==
1.258679377 35.90068496 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 pbsm/ft psia Inlet Air Flow 28184.76775 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]9)C 9 vX.9L C'b' /r",)PI 0.i~ 0.0-,
Moist Air Properties 
-- Given Dry Bulb and Specific Humidity Total Pressure:
P =Dry Bulb Temperature:
T =Specific Humidity:
W =Water Vapor Pressure:
Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Dry Air Pressure:
Pa =P -Pv =Dry Air Density: Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Water Vapor Density: Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Moist Air Density: Rho = Rho a + Rho v =Saturated Air Pressure:
Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =Moist Air Relative Humidity:
RH -Pv /Ps =Equation Coefficients:
a =14.315 110.72 0.020273629 0.451874518 13.86312548

==0.0 65599577==
0.001329941

==0.0 66929518==
1.303089954 34.6771546 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-1 0 2.109071E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Inlet Air Flow 28125.47196 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]00 01 0 b C d e f (!&#xfd;&#xfd; Y\&#xfd;lr -/r-o i-\ _&#xfd;~1~r'.-.-4 Af C / (.)o/ci Moist Air Properties 
-- Given Dry Bulb and Specific Humidity Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients: ( o CD-0 00 W=_Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*Ts) =RH Pv /Ps =a=b=C=d=e=f=14.315 111.85 0.020273629 0.451874518 13.86312548

==0.0 65469875==
0.001327312

==0.0 66797187==
1.34613727 33.56823468 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-1 0 2.109071E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 psia Inlet Air Flow 28069.86274 Equation [11]Equation [4]Equation [5]Equation [61 Equation [7]Equation [8]Equation [15]pz~ C)
Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
0 0>oo CD 0 00 Given Dry Bulb and Specific Humidity T=W=Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) -RH = Pv/Ps a=b=C=d=e=f=14.315 112.97 0.020273629 0.451874518 13.86312548

==0.0 65341825==
0.001324716

==0.0 66666541==
1.390006231 32.50881239 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Inlet Air Flow 28014.9622 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]('C, el, el&#xfd; ( I Aro .x S 73- , E- 9 A ", -&#xfd;e -:-_r7 i 62, Moist Air Properties Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity:~Equation Coefficients:
0 c o> 0 0 0 00-- Given Dry Bulb and Specific HumidityPv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv/Ps a=b=C=d=e=f=14.315 113.96 0.020273629 0.451874518 13.86312548

==0.0 65229055==
0.00132243

==0.0 66551484==
1.429802188 31.60398842 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-11 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Inlet Air Flow 27966.61254 Equation [11]Equation. 
[4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]6Ok/- 46 rts 0047'~/
Attachment I to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 1 of 25 15:35:4 1 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 180 gpm Case 07/06/98 Air Coil Heat Exchanger Input Parameters FileQt Dry Bbi-, Tempaf --.......Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 150.00 OF 92.00 OF 108.80 OF 84.00 OF Tube-Side 1-8uO-0-gpm 105.00 OF 117.70 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr'ft.
0 F)Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr ft.&deg;F)Fresh Water 0.002000 0.002000 1,108,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 2 of 25 15:35:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 180 gpm Case Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (OF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm) 180.00 .9 Air Flow (acfmn) 28,318.00 Tube Inlet Temp (IF) 100.00 Air Inlet Temp (IF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (OF) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 3 of 25 15:35:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 180 gpm Case 07/06/98 U".Extrapolation Calculation Summary II 1. *Air-Side Mass Flow (lbm/hr) 104,644.56 Inlet Temperature (0 F) 148.00 Outlet Temperature (OF) 106.85 Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft.hr)
Skin Visc (lbmr/f.hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Tube-Side 89,504.32 100.00 112.00 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr ft 2.&deg;F)Tube Wall Resistance (hr-ft 2 0-F/BTU Overall Fouling (hr-ft 2.0 F/BTU)U Overall (BTU/hr ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 3734207==
10,532.34 1,077,246 1,077,246 w.Extrapolation Calculation for Row l(Dry)_____II Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Air-Side 104,644.56 148.00 140.18 0.0203 0.0203 144.09 120.35 4,238.79 946**0.7255 0.0490 Tube-Side 89,504.32 109.71 112.00 110.86 113.00 5.53 36,742 4.0060 1.4714 Tube-Side hi (BTU/hr-ft 2 l-F)j Factor Air-Side ho (BTU/hr ft 2.F)Tube Wall Resistance (hr-ft2- F/BTU Overall Fouling (hr-ft2.&deg;F/BTU)
U Overall (BTU/hr ft2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)1,612.69 0.0071 8.93 0.00029413

==0.0 3734207==
5.88 1,053.23 33.07 204,818 0.9215 204,818 Skin Vise (lbm/ft-hr) 1.4404 Density (lbm/ft 3) 0.0624 61.8479 Cp (BTU/Ibm 0'F) 0.2402 0.9988 K (BTU/hr"ft-'F) 0.0162 0.3668** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 4 of 25*** Air Mass Velocity (ILbn/hr-ft 2), Tube Fluid Velocity (ft/sec)&#xfd; Air Density at Inlet T, Other Properties at Average T 15:35:41 PROTO-IHX 3.01 by Proto-Power Corporation (SN#PH4X-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 180 gpm Case 07/06/98 a Extrapolation Calculation for Row 2(Dry)II I. ~1 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbmf/t 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ftf.F)
Air-Side 104,644.56 140.18 133.57 0.0203 0.0203 136.87 116.78 4,238.79 955**0.7261 0.0485 0.0631 0.2402 0.0161 Tube-Side 89,504.32 107.78 109.71 108.74 110.57 5.53 35,970 4.1007 1.5030 1.4755 61.8777 0.9988 0.3661 Tube-Side hi (BTU/hr-ft 2.&deg;F) 1,593.93 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2-&deg;F) 8.90 Tube Wall Resistance (hrft 2 0.&deg;F/BTU 0.00029413 Overall Fouling (hr ft 2-&deg;F/BTU) 0.03734207 U Overall (BTU/hr.ft 2-F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.86 1,053.23 28.00 172,828 0.9218 172,828** Reynolds Number Outside Range of Equation Applicability
\1W, Extrapolation Calculation for Row 3(Dry)II I. 'I Air-Side Tube-Side Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ftf.F) 104,644.56 133.57 128.00 0.0203 0.0203 130.79 113.76 4,238.79 963**0.7266 0.0482 0.0637 0.2402 0.0159 89,504.32 106.14 107.78 106.96 108.52 5.52 35,322 4.1835 1.5305 1.5064 61.9024 0.9989 0.3654 Tube-Side hi (BTU/hr ft 2.&deg;F) 1,578.04 j Factor 0.0070 Air-Side ho (BTU/hr-ftl 2.F) 8.87 Tube Wall Resistance (hrft 2 E-&deg;F/BTU 0.00029413 Overall Fouling (hr- ft 2-F/BTU) 0.03734207 U Overall (BTU/hr ft 2-IF)Effective Area (ft)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.,85 1,053.23 23.71 145,975 0.9220 145,975** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 5 of 25*** Air Mass Velocity (Lbm/hr-ft2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:35:4 1 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 180 gpm Case 07/06/98 Is Extrapolation Calculation for ROw 4(Dry)II 11 Air-Side Tube-Side Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbml/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-'F) 104,644.56 128.00 123.28 0.0203 0.0203 125.64 111.21 4,238.79 969*, 0.7270 0.0478 0.0642 0.2402 0.0158 89,504.32 104.76 106.14 105.45 106.78 5.52*' 34,778 4.2556 1.5545 1.5333 61.9229 0.9989 0.3649 Tube-Side hi (BTU/hr ft 2-F) 1,564.58 j Factor 0.0070 Air-Side ho (BTU/hr'ft 2-&deg;F) 8.85 Tube Wall Resistance (hr-ft 2.F/BTU 0.00029413 Overall Fouling (hr'ft 2"&deg;F/BTU) 0.03734207 U Overall (BTU/hr'ft 2" 0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.83 1,053.23 20.09 123,397 0.9222 123,397** Reynolds Number Outside Range of Equation Applicability w.Extrapolation Calculation for Row 5(Dry)II II Mass Flow (lbmihr)Inlet Temnperature 
(&deg;F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fl-hr)
Skin Visc (lbm/flthr)
Density (Ibm/fl 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ftl-F)
Air-Side 104,644.56 123.28 119.30 0.0203 0.0203 121.29 109.06 4,238.79 975*A 0.7273 0.0476 0.0646 0.2402 0.0157 Tube-Side 89,504.32 103.60 104.76 104.18 105.31 5.52 34,320 4.3181 1.5752 1.5567 61.9400 0.9989 0.3644 Tube-Side hi (BTU/hr-ft2-IF) j Factor Air-Side ho (BTU/hr-ft 2.'F)Tube Wall Resistance (hr-ft 2.F/BTU Overall Fouling (hr ft2-&deg;F/BTU)
U Overall (BTU/hr ft 2-OF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)1,553.17 0.0070 8.83 0.00029413

==0.0 3734207==
5.8-2 1,053.23 17.03 104,384 0.9224 104,384** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 6 of 25*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:35:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIHX-0000)
ComEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 180 gpm Case 07/06/98 Extrapolation Calculation for Row 6(Dry)II 1i Mass Flow (ibm/lr)Inlet Temperature 
(&deg;F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Air-Side 104,644.56 119.30 115.92 0.0203 0.0203 117.61 107.24 4,238.79 980**0.7276 0.0473 Tube-Side 89,504.32 102.61 103.60 103.10 104.07 5.52 33,935 4.3722 1.5931 1.5770 Tube-Side hi (BTU/hr-ft 2.&deg;F) 1,543.49 j Factor 0.0070 Air-Side ho (BTU/lh-ft 2-&deg;F) 8.81 Tube Wall Resistance (hr-ft2-&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr- ft 2" 0 F/BTU) 0.03734207 U Overall (BTU/hr'ft-'&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.81 1,053.23 14.44 88,354 0.9225 88,354 Density (Ibm/ft 3) 0.0650 61.9543 Cp (BTU/Ibm'&deg;F) 0.2402 0.9989 K (BTU/hr-ft'&deg;F) 0.0156 0.3640** Reynolds Number Outside Range of Equation Applicability II Extrapolation Calculation for Row 7(Dry)II II Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbM/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr.ft-.F)
Air-Side 104,644.56 115.92 113.06 0.0203 0.0203 114.49 105.70 4,238.79 984**0.7278 0.0471 0.0653 0.2402 0.0156 Tube-Side 89,504.32 101.77 102.61 102.19 103.01 5.52 33,609 4.4188 1.6085 1.5946 61.9662 0.9990 0.3636 Tube-Side hi (BTU/hrlft 2.&deg;F) 1,535.29 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2-.F) 8.80 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr ft 2 0-&deg;F/BTU) 0.03734207 U Overall (BTU/hr'ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.80 1,053.23 12.24 74,823 0.9226 74,823** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 7 of 25*** Air Mass Velocity (Lbrn/hr-ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 15:35:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 180 gpm Case 07/06/98 Extrapolation Calculation for Row 8(Dry)I I I' 'II Mass Flow (lbmlhr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ftrhr)
Density (Ibm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr'ft'&deg;F)
Air-Side 104,644.56 113.06 110.64 0.0203 0.0203 111.85 104.39 4,238.79 987*1 0.7279 0.0470 0.0656 0.2402 0.0155 Tube-Side 89,504.32 101.06 101.77 101.42 102.11 5.52 33,335 4.4589 1.6218 1.6098 61.9762 0.9990 0.3633 Tube-Side hi (BTU/hr'ft 2"&deg;F) 1,528.33 j Factor 0.0070 Air-Side ho (BTU/hr'ft 2.&deg;F) 8.78 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr- ft 2'&deg;F/BTU) 0.03734207 U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.79 1,053.23 10.39 63,392 0.9227 63,392** Reynolds Number Outside Range of Equation Applicability
-~------------- 
-.1 II Extrapolation Calculation for Row 9(Dry)II I. 'I Air-Side Mass Flow (Ibm/hr) 104,644.56 Inlet Temperature (0 F) 110.64 Outlet Temperature (0 F) 108.59 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 109.61 Skin Temperature (7F) 103.28 Velocity *** 4,238.79 Reynold's Number 990*4 Prandtl Number 0.7281 Bulk Visc (Ibm/ft-hr) 0.0468 Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3) 0.0659 Cp (BTU/Ibm-'F) 0.2402 K (BTU/hr'fti-F) 0.0154 Tube-Side 89,504.32 100.46 101.06 100.76 101.36 5.52 33,103 4.4934 1.6331 1.6228 61.9846 0.9990 0.3631 Tube-Side hi (BTU/hr.ft 2.'F) 1,522.43 j Factor 0.0070 Air-Side ho (BTU/hr.ft 2 -F) 8.77 Tube Wall Resistance (hr-ft 2 -F/BTU 0.00029413 Overall Fouling (hr-ft 2-F/BTU) 0.03734207 U Overall (BTU/hr ft 2.'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.79 1,053.23 8.81 53,727 0.9228 53,727** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 8 of 25*** Air Mass Velocity (Lbm!hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:35:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHIX-0000)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 180 gpm Case 07/06/98 Is I Extrapolation Calculation for Row 1IJ(Dry)II II *1 I Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft hr)Density (Ibm/fl 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hrft-'F)
Air-Side 104,644.56 108.59 106.85 0.0203 0.0203 107.72 102.35 4,238.79 993**0.7282 0.0467 0.0661 0.2402 0.0154 Tube-Side 89,504.32 99.95 100.46 100.21 100.71 5.52 32,906 4.5229 1.6429 1.6340 61.9917 0.9990 0.3629 Tube-Side hi (BTUihr'ft 2'&deg;F) 1,517.42 j Factor 0.0070 Air-Side ho (BTU/hr- ft 2'&deg;F) 8.77 Tube Wall Resistance (hr ft 2'&deg;F/BTU 0.00029413 Overall Fouling (hr' ft 2'&deg;F/BTU) 0.03734207 U Overall (BTU/hr'ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.78 1,053.23 7.48 45,549 0.9229 45,549** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 9 of 25*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:57:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 72.5 gpm Case 07/06/98 Air Coil Heat Exchanger Input Parameters Flifdl-Qe--aiDy iuy, Tmlp Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Air-Side 33-1-,66.00 actiff 150.00 OF 92.00 OF 108.80 OF 84.00 OF Tube-Side---r8~0.0 gpm 105.00 OF 117.70 OF Fresh Water 0.002000 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-flt&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ftl.F) 108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 10 of 25 14:57:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils ALimiting Flow Analysis -- 72.5 gpm Case Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (aefin) 28,070.00 Tube Inlet Temp ('F) 100.00 Air Inlet Temp ('F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ('F) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 11 of 25 14:57:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 72.5 gpm Case 07/06/98 Extrapolation Calculation Summary Mass Flow (Ibmlhr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/th-hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-fr' 0 F)Air-Side 103,728.12 148.00 111.85 Tube-Side 36,050.35 100.00 126.02 Tube-Side hi (BTU/hr. ft 2.&deg;F)j Factor Air-Side ho (BTU/hr'ft 2"&deg;F)Tube Wall Resistance (hirft 2 0-F/BTU Overall Fouling (hr-ft 2"&deg;F/BTU)U Overall (BTU/hr ft 2.`F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 3734207==
10,532.34 938,124 938,124 Extrapolation Calculation for Row l(Dry)11~1 Mass Flow (lbm/hr)Inlet TeMperature (fF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft'hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 103,728.12 148.00 143.24 0.0203 0.0203 145.62 131.24 4,201.67 936*.0.7253 0.0491 0.0621 0.2402 0.0163 Tube-Side 36,050.35 122.59 126.02 124.30 126.80 2.23 16,832 3.4788 1.2936 1.2646 61.6438 0.9988 0.3714 Tube-Side hi (BTU/hr ft 2-&deg;F) 834.45 j Factor 0.0071 Air-Side ho (BTU/hr fi 2-'F) 8.89 Tube Wall Resistance (hr-ftl-&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr-ft 2-.F/BTU) 0.03734207 U Overall (BTU/hr--ft 2&deg;F)Effective Area (ft)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTUihr)Heat to Condensate (BTU/hr)55-3 1,053.23 21.19 123,422 0.9219 123,422** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 12 of 25 Air Mass Velocity (Lbmnhr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:57:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 72.5 gpm Case 07/06/98 Extrapolation Calculation lor Row z(Dry)II.4 H'Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ftihr)
Density (lbm/ft 3)Cp (BTU/1bm-'F)
K (BTU/hr'-f-&deg;F)
Air-Side 103,728.12 143.24 138.79 0.0203 0.0203 141.02 127.51 4,201.67 942*, 0.7258 0.0488 0.0625 0.2402 0.0162 Tube-Side 36,050.35 119.38 122.59 120.98 123.36 2.23 16,322 3.5979 1.3341 1.3049 61.6964 0.9988 0.3704 Tube-Side hi (BTU/hr ft 2"&deg;F) 820.85 j Factor 0.0071 Air-Side ho (BTU/hr" ft 2-&deg;F) 8.87 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-0 FiBTU) 0.03734207 U Overall (BTU/hr'ft 2"&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.51 1,053.23 19.91 115,582 0.9220 115,582** Reynolds Number Outside Range of Equation Applicability Z]&#xfd;_Extrapolation Calculation for Row 3(Dry)71 Mass Flow (lbm/hr)Inlet Temnperature (fF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr" ft -F)Air-Side 103,728.12 138.79 134.62 0.0203 0.0203 136.70 124.03 4,201.67 947**0.7261 0.0485 0.0630 0.2402 0.0161 Tube-Side 36,050.35 116.37 119.38 117.87 120.14 2.23 15,849 3.7157 1.3739 1.3447 61.7443 0.9988 0.3693 Tube-Side hi (BTU/hr.ft 2.0 F) 808.06 j Factor 0.0071 Air-Side ho (BTU/hr'ft2-&deg;F) 8.85 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2.F/BTU) 0.03734207 U Overall (BTUihrft 2 0.'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.49 1,053.23 18.72 108,279 0.9222 108,279** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 13 of 25*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:57:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 72.5 gpm Case 07/06/98 NO Extrapolation Calculation for Row 4(Dry)11 II I.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Visc (lbml/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 103,728.12 134.62 130.71 0.0203 0.0203 132.66 120.76 4,201.67 952**0.7265 0.0483 0.0634 0.2402 0.0160 Tube-Side 36,050.35 113.55 116.37 114.96 117.11 2.23 15,410 3.8319 1.4130 1.3839 61.7881 0.9988 0.3683 Tube-Side hi (BTU/hr-ftV.&deg;F) 796.02 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2."F) 8.83 Tube Wall Resistance (hr ft 2"&deg;F/BTU 0.00029413 Overall Fouling (lirft 2 l-F/BTU) 0.03734207 U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.48 1,053.23 17.59 101,473 0.9224 101,473** Reynolds Number Outside Range of Equation Applicability w Extrapolation Calculation for Row 5(Dry)II Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft'hr)
Skin Visc (lbm/ft'hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 103,728.12 130.71 127.04 0.0203 0.0203 128.87 117.70 4,201.67 957*, 0.7268 0.0480 0.0638 0.2402 0.0159 Tube-Side 36,050.35 110.91 113.55 112.23 114.28 2.23 15,003 3.9463 1.4514 1.4224 61.8281 0.9988 0.3673 Tube-Side hi (BTU/hr ft 2 0.F) 784.69 j Factor 0.0071 Air-Side ho (BTU/hr ft 2.&deg;F) 8.81 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.03734207 U Overall (BTU/hrft2.&deg;IF)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.46 1,053.23 16.54 95,126 0.9225 95,126** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 14 of 25*** Air Mass Velocity (Lbni/hrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:57:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 72.5 gpm Case 07/06/98 Extrapolation Calculation for Row 6(Dry)i!I.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fr-hr)
Skin Visc (lbm/fr-hr)
Density (lbm/fl 3)Cp (BTU/1bm-'F)
K (BTU/hrff 0 F)Air-Side 103,728.12 127.04 123.60 0.0203 0.0203 125.32 114.82 4,201.67 961*0.7270 0.0478 0.0642 0.2402 0.0158 Tube-Side 36,050.35 108.43 110.91 109.67 111.62 2.23 14,624 4.0586 1.4889 1.4602 61.8646 0.9988 0.3664 Tube-Side hi (BTU/hr ft 2.&deg;F) 774.02 j Factor 0.0070 Air-Side ho (BTU/hrfl-'f.F) 8.80 Tube Wall Resistance (hr-ft 2-F/BTU 0.00029413 Overall Fouling (hr-ft 2_-F/BTU) 0.03734207 U Overall (BTU/hr ft 2 -F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.44 1,053.23 15.56 89,203 0.9226 89,203** Reynolds Number Outside Range of Equation Applicability
\4 R-- -.----.I1 Extrapolation Calculation for Row 7(Dry)II*1 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (ibm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft--F)
Air-Side 103,728.12 123.60 120.38 0.0203 0.0203 121.99 112.13 4,201.67 965**0.7273 0.0476 0.0645 0.2402 0.0157 Tube-Side 36,050.35 106.11 108.43 107.27 109.12 2.23 14,272 4.1689 1.5256 1.4972 61.8981 0.9989 0.3655 Tube-Side hi (BTU/hr ft2.&deg;F) 763.98 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.0 F) 8.78 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr. fl 2-F/BTU) 0.03734207 U Overall (BTU/hr. ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.4-3 1,053.23 14.63 83,674 0.9227 83,674** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 15 of 25*** Air Mass Velocity (Lbm/hr.ft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:57:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 72.5 gpm Case 07/06/98 m Extrapolation Calculation for Row 8(Dry)1.Air-Side Mass Flow (Ibm/hr) 103,728.12 Inlet Temperature (OF) 120.38 Outlet Temperature (OF) 117.35 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 118.86 Skin Temperature (OF) 109.60 Velocity *** 4,201.67 Reynold's Number 969*" Prandtl Number 0.7275 Bulk Visc (lbm!ft-hr) 0.0474 Skin Visc (lbm/ftrhr)
Density (lbm/ft 3) 0.0649 Cp (BTU/lbm.&deg;F) 0.2402 K (BTU/hr'tf'&deg;F) 0.0157 Tube-Side 36,050.35 103.93 106.11 105.02 106.78 2.22 13,945 4.2767 1.5615 1.5334 61.9287 0.9989 0.3647 Tube-Side hi (BTU/hr ft 2 -F) 754.53 j Factor 0.0070 Air-Side ho (BTU/hr ft2. F) 8.77 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr ft 2.&deg;F/BTU) 0.03734207 U Overall (BTU/hr-ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.42 1,053.23 13.77 78,509 0.9229 78,509** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 9(Dry)11 Mass Flow (lbm/hr)Inlet Te~mperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/fl 3)Cp (BTU/lbn'&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 103,728.12 117.35 114.51 0.0203 0.0203 115.93 107.22 4,201.67 973**0.7277 0.0472 0.0652 0.2402 0.0156 Tube-Side 36,050.35 101.88 103.93 102.91 104.57 2.22 13,640 4.3821 1.5964 1.5687 61.9568 0.9990 0.3639 Tube-Side hi (BTU/hr.ft2.&deg;F) 745.64 j Factor 0.0070 Air-Side ho (BTU/hr ft2.-F) 8.75 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr ft2.&deg;F/BTU) 

==0.0 3734207==
U Overall (BTU/hr ft 2-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.40 1,053.23 12.95 73,683 0.9230 73,683** Reynolds Number Outside Range of Equation Applicability Proto-Power Cale: 97-199 

==Attachment:==

I Rev: A Page 16 of 25*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:57:09 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 72.5 gpm Case 07/06/98 E Extrapolation Calculation for Row 10(Dry)II II IL_ i Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fl-hr)
Skin Visc (lbm/fthr)
Density (lbMn/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 103,728.12 114.51 111.85 0.0203 0.0203 113.18 104.99 4,201.67 977*1 0.7278 0.0470 0.0655 0.2402 0.0155 Tube-Side 36,050.35 99.96 101.88 100.92 102.51 2.22 13,356 4.4848 1.6303 1.6031 61.9826 0.9990 0.3631 Tube-Side hi (BTU/hr'ftt 2'F) 737.27 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2"&deg;F) 8.74 Tube Wall Resistance (hr'ft 2 "&deg;F/BTU 0.00029413 Overall Fouling (hr- ft 2 0'F/BTU) 0.03734207 U Overall (BTU/hrft 2 0.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.39 1,053.23 12.19 69,171 0.9231 69,171** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 17 of 25*** Air Mass Velocity (Lbn/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:34:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow @Reduced Finned Length 07/06/98 Air Coil Heat Exchanger Input Parameters FleitiDrynBiuy, Temp hIlet Dry Bulb Temnp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperatur Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 3-1706W..0 -acffiui 150.00 OF 92.00 OF e 108.80 OF 84.00 OF Tube-Side......1807u.-0 gpmn 105.00 OF 117.70 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Fresh Water 0.002000 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-OF) 102.750 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 18 of 25 17:34:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 ComEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow @,Reduced Finned Length Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfmi) 28,051.00 Tube Inlet Temp ('F) 100.00 Air Inlet Temp ('F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ('F) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 19 of 25 17:34:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow @Reduced Finned Length 07/06/98 FL_ I Extrapolation Calculation Summary 11 It Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftlhr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr.ft-&deg;F)
Air-Side 103,657.91 148.00 112.24 Tube-Side 36,050.35 100.00 125.78 Tube-Side hi (BTU/hr ft2-&deg;F)j Factor Air-Side ho (BTU/hr'ft 2-&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr'ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 3734207==
10,020.35 927,356 927,356 Extrapolation Calculation for Row l(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbmrftlhr)
Density (Ibm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft'&deg;F)
Air-Side 103,657.91 148.00 143.33 0.0203 0.0203 145.66 131.25 4,413.36 983*4 0.7253 0.0491 0.0621 0.2402 0.0163 Tube-Side 36,050.35 122.42 125.78 124.10 126.68 2.23 16,800 3.4859 1.2961 1.2660 61.6471 0.9988 0.3714 Tube-Side hi (BTU/hr.ft 2-F) 833.71 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.&deg;F) 9.18 Tube Wall Resistance (hr-ft 2-F/BTU 0.00029413 Overall Fouling (hr'ft 2-&deg;F/BTU) 0.03734207 U Overall (BTU/hr.ft2-IF)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.64 1,002.04.21.44 121,197 0.9196 121,197** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 20 of 25*** Air Mass Velocity (Lbmihr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:34:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow @Reduced Finned Length 07/06/98-II Extrapolation Calculation for Row 2(Dry)II II Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (7F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbmrft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr 0 t-.F)Air-Side 103,657.91 143.33 138.94 0.0203 0.0203 141.13 127.59 4,413.36 989*.0.7257 0.0488 0.0625 0.2402 0.0162 Tube-Side 36,050.35 119.26 122.42 120.84 123.29 2.23 16,300 3.6033 1.3359 1.3057 61.6987 0.9988 0.3703 Tube-Side hi (BTU/hr'ftV-0 F) 820.34 j Factor 0.0070 Air-Side ho (BTU/hr'ft 2"&deg;F) 9.16 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr ft 2.&deg;F/BTU) 0.03734207 U Overall (BTU/hr'ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.62 1,002.04 20.18 113,692 0.9197 113,692** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)If Air-Side Mass Flow (lbm/hr) 103,657.91 Inlet Temperature (0 F) 138.94 Outlet Temperature 
(&deg;F) 134.83 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 136.88 Skin Temperature (0 F) 124.15 Velocity *** 4,413.36 Reynold's Number 994*, Prandtl Number 0.7261 Bulk Visc (lbm/fthr) 0.0485 Skin Visc (Ibm/ft-hr)
Density (ibm/fl 3) 0.0630 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr"flt.F) 0.0161 Tube-Side 36,050.35 116.30 119.26 117.78 120.12 2.23 15,834 3.7195 1.3752 1.3449 61.7458 0.9988 0.3693 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr'fl 2.&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr'ft'-&deg;F/BTU)
U Overall (BTU/hr-ftl 2-F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)807.75 0.0070 9.14 0.00029413

==0.0 3734207==
5.60 1,002.04 19.00 106,688 0.9199 106,688** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 21 of 25*** Air Mass Velocity (Lbm/hr.ft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:34:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow @Reduced Finned Length 07/06/98:ii Extrapolation Calculation for Row 4(Dry)II I.Air-Side Mass Flow (lbm/hr) 103,657.91 Inlet Temperature (IF) 134.83 Outlet Temperature (OF) 130.97 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 132.90 Skin Temperature (IF) 120.92 Velocity *** 4,413.36 Reynold's Number 1,000"*Prandtl Number 0.7264 Bulk Visc (lbrn/ft-hr) 0.0483 Skin Vise (lbrn/ft-hr)
Density (lbm/ft 3) 0.0634 Cp (BTU/lbm'&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0160 Tube-Side 36,050.35 113.51 116.30 114.90 117.14 2.23 15,402 3.8342 1.4138 1.3836 61.7889 0.9988 0.3683 Tube-Side hi (BTU/hr-ft 2.&deg;F) 795.87 j Factor 0.0070 Air-Side ho (BTU/hr ft 2.&deg;F) 9.12 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr ft 2-&deg;F/BTU) 0.03734207 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.59 1,002.04 17.89 100,150 0.9201 100,150** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)II Mass Flow (Ibm/hr)Inlet Tqmperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft hr)Density (Ibm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 103,657.91 130.97 127.34 0.0203 0.0203 129.15 117.88 4,413.36 1,004 0.7267 0.0481 0.0638 0.2402 0.0159 Tube-Side 36,050.35 110.90 113.51 112.21 114.33 2.23 14,999 3.9473 1.4517 1.4217 61.8284 0.9988 0.3673 Tube-Side hi (BTU/hr.ft2-.F) j Factor Air-Side ho (BTU/hrft 2 0-IF)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2 0-F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)784.67 0.0069 9.10 0.00029413

==0.0 3734207==
5;-5 7 1,002.04 16.85 94,041 0.9202 94,041 Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 22 of 25*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:34:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow @Reduced Finned Length 07/06/98 M -01 Extrapolation Calculation for Row 6(Dry)11 p.Air-Side Mass Flow (lbm/hr) 103,657.91 Inlet Temperature (OF) 127.34 Outlet Temperature (IF) 123.93 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 125.64 Skin Temperature (IF) 115.03 Velocity *** 4,413.36 Reynold's Number 1,009 Prandtl Number 0.7270 Bulk Visc (lbm/ft-hr) 0.0478 Skin Visc (lbrnIft-hr)
Density (ibm/fl 3) 0.0641 Cp (BTU/Ibm-0 F) 0.2402 K (BTU/hr-ft-'F) 0.0158 Tube-Side 36,050.35 108.45 110.90 109.67 111.70 2.23 14,625 4.0585 1.4889 1.4590 61.8646 0.9988 0.3664 Tube-Side hi (BTU/hr. ft 2.'F) 774.12 j Factor 0.0069 Air-Side ho (BTU/hr'ft 2"&deg;F) 9.09 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr- ft 2.F/BTU) 0.03734207 U Overall (BTU/hr ft2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.55 1,002.04 15.87 88,332 0.9203 88,332 Extrapolation Calculation for Row 7(Dry)1i II ll Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (ibm/fl 3)Cp (BTU/1bm."F)
K (BTU/hr.ft-&deg;F)
Air-Side 103,657.91 123.93 120.73 0.0203 0.0203 122.33 112.36 4,413.36 1,014 0.7272 0.0476 0.0645 0.2402 0.0157 Tube-Side 36,050.35 106.14 108.45 107.30 109.22 2.23 14,276 4.1677 1.5253 1.4957 61.8978 0.9989 0.3656 Tube-Side hi (BTU/hr.ft2.
0 F) 764.17 j Factor 0.0069 Air-Side ho (BTU/hr-ft 2.&deg;F) 9.07 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr-ft2. F/BTU) 0.03734207 U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.54 1,002.04.14.95 82,993 0.9205 82,993 Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 23 of 25*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:34:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow @Reduced Finned Length 07/06/98 m Extrapolation Calculation for Row 8(Dry)iI II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbnm/ft-hr)
Skin Visc (Ibm/ft'hr)
Density (lbmr/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-PF)
Air-Side 103,657.91 120.73 117.72 0.0203 0.0203 119.23 109.84 4,413.36 1,018 0.7275 0.0474 0.0648 0.2402 0.0157 Tube-Side 36,050.35 103.98 106.14 105.06 106.89 2.22 13,951 4.2747 1.5608 1.5316 61.9282 0.9989 0.3647 Tube-Side hi (BTU/hr ft2.&deg;F) 754.79 j Factor 0.0069 Air-Side ho (BTU/hr'ft 2-OF) 9.06 Tube Wall Resistance (hr-ft2.0 F/BTU 0.00029413 Overall Fouling (hr-ft 2-F/BTU) 0.03734207 U Overall (BTU/hr'ft 2"&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.52 1,002.04 14.09 77,998 0.9206 77,998 Extrapolation Calculation for Row 9(Dry)II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbrn/ft.hr)
Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr.fl.&deg;F)
Air-Side 103,657.91 117.72 114.90 0.0203 0.0203 116.31 107.47 4,413.36 1,022 0.7277 0.0472 0.0651 0.2402 0.0156 Tube-Side 36,050.35 101.94 103.98 102.96 104.70 2.22 13,648 4.3794 1.5955 1.5666 61.9561 0.9989 0.3639 Tube-Side hi (BTU/hr. ft 2..F) 745.95 j Factor 0.0069 Air-Side ho (BTU/hrift2-&deg;F) 9.04 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.03734207 U Overall (BTU/hr-ft 2.IF)Effective Area (fl 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.51 1,002.04 13.28 73,322 0.9207 73,322 Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 24 of 25*** Air Mass Velocity (Lbnmlhrft 2), Tube Fluid Velocity (ft/sec), Air Density at Inlet T, Other Properties at Average T 17:34:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow @Reduced Finned Length 07/06/98--~ -. -~. --~ -~--- .3 Extrapolation Calculation for Row 10(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fti-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 103,657.91 114.90 112.24 0.0203 0.0203 113.57 105.25 4,413.36 1,026 0.7278 0.0471 0.0654 0.2402 0.0155 Tube-Side 36,050.35 100.03 101.94 100.98 102.64 2.22 13,365 4.4816 1.6292 1.6008 61.9818 0.9990 0.3632 Tube-Side hi (BTU/hr-ft 2.'F) 737.61 j Factor 0.0069 Air-Side ho (BTU/hr'ft 2 0'F) 9.03 Tube Wall Resistance (hr-ft 2"&deg;F/BTU 0.00029413 Overall Fouling (hr' ft 2"&deg;F/BTU) 0.03734207 U Overall (BTU/hr ft 2 -F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.50 1,002.04 12.51 68,944 0.9208 68,944 Proto-Power Calc: 97-i99 

==Attachment:==

I Rev: A Page 25 of 25*** Air Mass Velocity (Lbinhr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Attachment J to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 1 of 43 Proto-HX Analytical Uncertainty Calculation
[Circular Fin Air Coil Application]
Purpose The purpose of the following calculation is to evaluate the analytical uncertainty associated with the analysis of test data and the computation of heat transfer rate at a given extrapolation condition.
This calculation focuses only on the parameters that are not measured during the thermal performance test but factor into the analysis of the test results. Test parameter measurement uncertainty is treated separately in the test uncertainty analysis.
The calculation of analytical uncertainty is derived for a typical Air Cooler with "n" tube rows.Governing Heat Transfer Equations Heat transfer calculations associated with a heat exchanger generally reduce to satisfying the following equations:
I) q = U AO LMTD Where: q = Heat transfer rate at test conditions (BTU/hr)U = Overall heat transfer coefficient at test conditions (BTU/hr-&deg;F-ft 
)Ao = Heat transfer surface area referenced to outside (air-side) surface (ft 2)LMTD = Log Mean Temperature Difference at test.conditions (IF)and'2) q = rhcp (T,,. -Ta) = pQcp AT Where: q = Heat transfer rate at test conditions (BTU/hr)rin = Mass flow rate at test conditions (lbm/hr)CP = Specific heat of cooling water at test conditions (Btu/Ilbm-F)= Tube-side inlet temperature at test conditions 
(&deg;F)Too = Tube-side outlet temperature at test conditions (OF)p = Density of tube-side fluid at average bulk temperature at test conditions (lb/f1 3)Q = Volumetric flow rate of tube-side fluid at test conditions (gpm)The first equation is used, in Proto-HX, to evaluate the heat transfer rate from test data. The analytical uncertainties associated with evaluating the fluid properties are usually the only contributors to the overall uncertainty when using this equation.
For a given test condition, the right hand side of the second equation is evaluated such that it matches the measured heat Proto-Power Calc: 97-199 

==Attachment:==

j Rev: A Page 2 of 43 transfer rate, "q". In Proto-HX, this means iterating on fouling factor, and therefore "U", until the heat transfer equation is satisfied.
The following equations are used for this iteration:
I A. LMTD Test 3) R U qTest Where: R = Overall heat transfer thermal resistance at test conditions (hr-&deg;F-ft 2/ BTU)U = Overall heat transfer coefficient at test conditions (BTU/hr-&deg;F-ft 
)A 0  = Outside heat transfer surface area (ft2)LMTD = Log Mean Temperature Difference at test conditions 
('F)q = Heat transfer rate at test conditions (BTU/hr)and 4) Rf=R- R_ -A-)- 1 hor/5  -A hi Where: R = Fouling resistance (hr-&deg;F-ft 2/ BTU)R = Overall heat transfer thermal resistance at test conditions (hr--F-ft 2/ BTU)ho = Outside convection film coefficient at test conditions (BTU/hr-&deg;F-ft 2)rlS = Fin surface effectiveness R, = Wall thermal resistance at test conditions (hr-&deg;F-ft 2/ BTU)Ao = Outside heat transfer surface area (ft)2 Ai = Inside heat transfer surface area (ft2)hi = Inside convection film coefficient at test conditions (BTU/hr-&deg;F-ft 2)These same equations must be satisfied when evaluating the capacity of a heat exchanger at a given fouling condition (i.e., when extrapolating to the limiting thermal condition).
The following equations are used for the extrapolation process: 5) R*=Rf + 1 + Rw*+ (A) I ho
* r7 , Ai hi Where: R* = Overall thermal resistance at extrapolation conditions (hr-&deg;F-ft2/
BTU)Rf = Calculated fouling resistance (hr-&deg;F-ft 2/ BTU)ho, = Outside convection film coefficient at extrapolation conditions (BTU/hr-&deg;F-ft 2)71S = Fin surface effectiveness Rw* = Wall thermal resistance at extrapolation conditions(hr-&deg;F-ft 2/ BTU)A 0  = Outside heat transfer surface area (ft 2)Ai = Inside heat transfer surface area (ft2)Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 3 of 43 Ili* = Inside convection film coefficient at extrapolation conditions (BTU/hr-&deg;F-ft 2)and 6) q* = (I/R*) A, LMTD* = U*Ao LMTD*where: q* = Heat transfer rate at extrapolation conditions (BTU/hr)R* = Overall thermal resistance at extrapolation conditions (hr-oF-fl 2/ BTU)U* = Overall heat coefficient at extrapolation conditions (BTU/hr-&deg;F-fl 2)Ao = Heat transfer surface area referenced to outside surface (ft 2)LMTD* = Log Mean Temperature Difference at extrapolation conditions (fF)Analytical Uncertainty Calculation Methodology The method for calculating the analytical uncertainty associated with this performance analysis method is illustrated as follows: Given a function D = f(A,B,C)The effect on D of slight changes in the independent variables A, B, and C may be calculated by taking the partial derivatives of D with respect to each of the independent variables.
Accordingly, the change in the value of D (i.e., AD) due to changes in each of the independent variables (AA, AB, AC) may be represented by the following equation: AD -DAA + -DAB + DAC 0 A cB dC If AA, AB, AC are the known (or estimated) errors of the independent variables, then the error, AD, associated with the derived value, D, is calculated.
The most probable one standard deviation error representative of AD would be the statistical root mean squared value derived as follows: AD= ii AA + A + -AC) 2 = U 1 O A ) ? ~B) I9 Expressing the uncertainty in terms of a percentage of the value of D is simply a matter of including division by the value of D as follows: UD = D 2 2 + 0 2) AB2 ( D AC 2 2 AY +C\DJ z \D9 Aj Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 4 of 43 The next six sections of this document provide a step by step approach to calculating the analytical uncertainty associated with the six thermal performance equations outlined above.The specific terms to be evaluated from these equations are as follows: 1) Heat transfer area, A, and area uncertainty, UA, 1 2) Test condition heat transfer rate, q and heat transfer uncertainty, Uq 3) Test condition thermal resistance, R and thermal resistance uncertainty, UR 4) Observed overall fouling resistance, Rf fouling resistance uncertainty, URf 5) Extrapolation condition thermal resistance, R* and thermal resistance uncertainty, UR.6) Extrapolation condition heat transfer rate, q* and heat transfer rate uncertainty, Uq.All uncertainty equations used in this calculation are based on the methods of Reference 
[I]. It is assumed that all independent variables in each equation have no influence on each other. For example, in Equation (6), LMTD* and the overall heat transfer coefficient, U*, are independent of each other. More specific assumptions are stated in each section as applicable.
For the rating analysis case (i.e., fouling factor is specified and not calculated from test data), equations 2, 3 and 4 above are not applicable because the uncertainty in the specified fouling factor is zero. The analytical uncertainty calculation, therefore, is reduced to an accounting of area uncertainty from equation 1 and the uncertainty in extrapolation terms per equations 5 and 6.Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 5 of 43 
: 1) Uncertainty in Calculation of Heat Transfer Area (Al)Governing Equation q = U Ao LMTD For Air Coolers with circular fins, the outside tube surface area, the fin surface area and the total outside surface area are given by the following expressions:
AoTob T = ZNT N .. Lcdo(1-0 tFR)Ao.-= 7(ANTNLLC[HFtFT 
+/- (HF+do)j(HF 2-do + (t R2tFRtjj 2 Aolai= r NTNLLC{ do(l- XF tFR) + 2[HFtr +(HF + (t t.) !}where: NT = Number of tubes per row NL = Number of active tube rows Lc = Effective tube (coil) length (in)do = Tube outside diameter (in)X, = Fin pitch (fins/inch)
HF = Fin height (in)tFR = Thickness of fin at root (in)tvr = Thickness of fin at tip (in)For the case where tFR = tFr = tF, the total area equation reduces to the following:
A i,,=r NT NLc {do (1 -AtF)+4IHFtF 
+(HF +d.) (H-2 0 A,,,, =7rNrNLLc do-2dtF+ A[2HFtF+ HF 2 -d 0 2 Proto-Power Calc: 97-199 

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J Rev: A Page 6 of 43 
( Assumptions UNT T 0 UN 1 =0 U) 0 Analysis'A A. 2 2 2 2 2 2( H) Y2 UAo_ (oA0 U 2 ____ +( A&deg;0 UL .+(LAo 0 t UF 1  +(dA&deg; I -whe re (OA, ) (U 1 , _.A cl)YA Y L) A.) d.t~)1~ '&#xfd;t. A,,,. 0 ~ Ho A,, where,0) =-r NTNLL, {(12- tr) -Ad. }A) =-) =rNTNL +tFA 2 HFtFHF do2-f- ) = TrN rN LLA {HF-do}r 2A&deg; =fr-NTNLLcA 
{tF +HF}9HF)Proto-Power Calc: 97-199 

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J Rev: A Page 7 of 43 2)Uncertainty in Calculation of Heat Transfer Rate at Test Conditions Governing Equation qTest =mCp (To -T.)= pQcp AT Assumptions UAT = 0 UQSW = 0 (i.e., temperature and flow rate in the governing equation are measured values with no analytical uncertainites)
Analysis Uq.\2 2, 2 U 22 22 2 2 Uqte 1 , _ Oq ) t ( O +() Q +qte + q, T UATH q test ) st) z. ) qtest) c T Uq -cA)2  U Y2 (,Ur Y[ )Proto-Power Calc: 97-199 

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J Rev: A Page 8 of 43 3)Uncertainty in Calculation of Thermal Resistance at Test Conditions Governing Equation I A. LMTDTest U q "rest Assumptions ULMTD is negligible Analysis UR =[C OR+ (, R )I C LLMTD)~+ C ( D 2 Cq)c ]Y2 UR LMTDrAO R + C -A.LMTD 12U, C )2]Y q 2)t UA^ (Evaluated in Section 1)Uqt (Evaluated in Section 2)Proto-Power Calc: 97-199 

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J Rev: A Page 9 of 43 4)Uncertainty in Calculation of Fouling Factor at Test Conditions Governing Equation Rf =R-ho r]-Rw-( -Ai hio'eff-Rw (. ) IA Where, hoxff = effective outside film coefficient 
= (ho) x (in.Assumptions
'2 2 C e~o)( -U) &#xa3;9i UA.(i.e., the uncertainty in dimensions is negligible compared to the thermal resistance and convection coefficient uncertainties)
Analysis URf k R f) 2 , h2 2 R f d R .oReff2+( ORf )2UR)2(R J h 2Luj V2l+;R w IR dl'KL 9 RW Rf)UR = (UR, + n---'-T 2  (2_UR 2 , +A- (U2(A-2l Rf [- R) ho.),, +  UR (Evaluated in Section 3)Proto-Power Calc: 97-199 

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J Rev: A Page 10 of 43 5)Uncertainty in Calculation of Heat Transfer Resistance at Extrapolation Conditions Govemin~g Eqiuation R* f+- I 11&#xfd; *e+ Rw + (A,)J Assumptions C -fR* A.  (-&#xfd;T :) &#xfd;0'A 0 )K(*C *,)2( 'U 2 (i.e., the uncertainty in dimensions is negligible compared to the thermal resistance and convection coefficient uncertainties)
Analysis UR. _ UR*1 2 R U. 2  2U+ *) U ( R* 2(Uh* 2Y[R C UR 2 +2(h.R*) +R 2 + h 2Y OR k .Oof )R* AI *2) Rw 2* khe*lI R)+/- R*)UR, (Evaluated in Section 4)UR, = 0 (for extrapolation calculations only, i.e., no fouling calculation)
Proto-Power Calc: 97-199 

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J Rev: A Page 11 of 43 
: 6) Uncertainty in Calculation of Heat Transfer Rate at Extrapolation Conditions Goveming Equation q* = (I/R*) (A,) (LMTD*)Assumptions ULMTD ; 0.0 Analysis q" 2 Uq* 69q* 2_ 2 +LuN (q 2_____j( ) UR.') ++~ ~ ___ LNITDj q ) q>) 3~ q(LMTD) Yq)Uq _MT*2 (UR ' 2 (1V UA. 21]Y-=[(-R'-A LMTD' -L) + -LMTD -q q1.1 UR (Evaluated in Section 5)UAo (Evaluated in Section 1)Proto-Power Calc: 97-199 

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J Rev: A Page 12 of 43 
: 7) Uncertainty in Calculation of Extrapolated Heat Transfer for Entire Unit The uncertainties in extrapolated heat transfer, computed for each tube row, are combined in the following manner to yield an overall uncertainty value for the entire air cooler.q tot &#xfd; q, + q2 + q3 ...... +q, where, "n " is the number of tube rows in the unit.Uqt___ _ _ (qU qo Vo + (d q 0  2 + ( d q 2t 2 3Uq 3 +......... 
(! q t, 2 Vq 2 1/2 Uq to +q .( U 2 tot ~~) Uq qtot -,dqt I ) q tot! + , q 2J qtt , qqtotJ \ q ,qtot Assuming that the extrapolated heat transfer rates of the various rows do not depend on each other, the above expression becomes: 21 I L 2 L 2 q 2.11 L_ + L + _+ ...........
q t q C q tot (. q tot ( k q tot "/ (,q tot , q tot,/Proto-Power Calc: 97-199 

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J Rev: A Page 13 of 43 Definition of Analytical Uncertainty Analysis Terms Ao/Ai =di (in) =Ao (ft^2) =do (in) =Udo/do (%) =Udo =Nt=NI=Lambda (fins/in)L (Ft) =UL/L (%) =UL(ft) =tfin (in) =Utfin/tfin 
(%) =Utfin (in) =hfin (in) =Uhfin/hfin 
(%) =Uhfin (in) =Mdotc (Ibm/hr) =Q (Ft^3/hr) 
=DT (DegF) =rho (lbm/ftA3) 
=Urho/rho (%) =Urho =Cp (Btu/Ibm/DegF)
IUCp/Cp (%) =UCp =qtest (Btu/hr) =LMTD (DegF)=Uo =R = (I/Uo)=Rf [(hr-DegF-ft^2)fBtul 
=Etas =ho [Btu/(hr-DegF-ftA2)1 
=ho(eff) [Btu/(hr-DegF-ft^2)1 
=Uho/ho(%)=
Uho =hi [Btu/(hr-DegF-ftA2)1 
=Uhi/hi (%) =Uhi =Rw f(hr-DegF-ft^2)/Btuj 
=URw/Rw (%) =URw =Heat transfer area ratio Tube inside diameter Outside heat transfer area Tube outside diameter Uncertainty in tube outside diameter (as a percentage)
Uncertainty in tube outside diameter (absolute)
Number of tubes in given row Number of rows in heat exchanger Fin pitch Tube length Uncertainty in tube length (as a percentage)
Uncertainty in tube length (absolute)
Fin thickness Uncertainty in fin thickness (as a percentage)
Uncertainty in fin thickness (absolute)
Fin height Uncertainty in fin height (as a percentage)
Uncertainty in fin height (absolute)
Cooling water mass flow rate Cooling water volumetric flow rate Cooling water temperature difference (inlet to outlet)Cooling water density Uncertainty in cooling water density (as a percentage)
Uncertainty in cooling water density (absolute)
Cooling water specific heat Uncertainty in cooling water specific heat (as a percentage)
Uncertainty in cooling water specific heat (absolute)
Calculated test heat transfer for coil section Calculated log mean temperature difference Heat transfer coefficient Heat transfer resistance Fouling resistance Outside film coefficient Effective outside film coefficient Uncertainty in outside film coefficient (as a percentage)
Uncertainty in outside film coefficient (absolute)
Inside film coefficient Uncertainty in inside film coefficient (as a percentage)
Uncertainty in inside film coefficient (absolute)
Wall thermal resistance Uncertainty in wall resistance (as a percentage)
Unccrtainiy in wall resistance (absolute)
Proto-Power Calc: 97-199 

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J Rev: A Page 14 of 43 Page 1 VY03A-AU.XLS Analytical Uncertainty Analysis -- Uncertainty Inputs Parameter Udo/do ULc/Lc Utfin/tfin Uhfin/hfin Urho/rho UCp/Cp Uho/ho CUhi/hi URw/Rw Notes: (1)(2)(3)(4)(5)(6)(7)Definition Uncertainty in tube outside diameter Uncertainty in coil (tube) length Uncertainty in fin thickness Uncertainty in circular fin height Uncertainty in cooling water density Uncertainty in cooling water specific heat Uncertainty in outside film coefficient Uncertainty in inside film coefficient Uncertainty in wall resistance Value (%)8.00 0.23 4.17 1.38 2.00 2.00 15.00 15.00 2.00 (1)(2)(3)(4)(5)(5)(6)(7)(5)Measurement of 5/8" +/-/- 0.05" yields an uncertainty of 8.0%Measurement of 108" +/- 0.25" yields an uncertainty of 0.23%Specified as 0.012" with estimated tolerance of 0.0005" yields an uncertainty of 4.17%Measurement of 1.452" +/- 0.02" yields an uncertainty of 1.38%Uncertainty in property values is estimated as 2%Uncertainty in outside film coefficient is estimated as 15%Uncertainty in inside film coefficient is estimated as 15%Proto-Power Calc: 97-199 

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J Rev: A Page 15 of 43 VY03A-AU.XLS Page 2 PROTO-HX Report -Model Inputs 15:30:35 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -72.5 gpm Case Air Coil Heat Exchanger Input Parameters 07/06/98 Fluid Quantity.
Total Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Air-Side 31066 acfm 150 &deg;F 92 &deg;F 108.8 &deg;F 84 'F Tube-Side 180 gpm 105 &deg;F 117.7 &deg;F Fresh Water 0.002 0.002 1108000 14.315 1 0 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-=F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-"F) 108 10 128 0.012 0.012 1.452 2 10 24 24 0.527 0.625 1.4 1.41 1 225 Proto-Power Calc: 97-199 

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J Rev: A Page 16 of 43 Page 3 VY03A-AU.XLS PROTO-HX Report -- Fouling Calculation Output Fouling Calculation Summary There is no fouling calculation for the rating analysis case.Uncertainty in use of design fouling in rating analysis is zero.Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 17 of 43 VY03A-AU.XLS Page 4 PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Extrapolation Calculation Summary Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity *Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft hr)Density (Ibm/ft')Cp (BTU/Ibm&deg;F)
K (BTU/hr-ft-'F) 104644.6 148 106.8483 Tube-Side 89504.32 Tube-Side hi (BTU/hr.ft 2.&deg;F)100 j Factor 112 Air-Side ho (8TU/hr-ft1."F)
Tube Wall Resistance (hr'ft=&deg;F/BTU)
Overall Fouling (hr~ft'.&deg;F/BTU)
U Overall (BTU/hr-ft 2-OF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.000294 0.037342 10532.34 1077246 1077246 Extrapolation Calculation for Row 1(Dry)Air-Side Tube-Side Mass Flow (Ibm/hr) 104644.6 89504.32 Tube-Side hi (BTU/hr-ft1-.F)
Inlet Temperature 
(&deg;F) 148 109.709 j Factor Outlet Temperature (OF) 140.1758 112 Air-Side ho (BTU/hr.ft2-OF Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft=.&deg;F/BTU)
Outlet Specific Humidity 0.020268 Overall Fouling (hr ftt-=F/BTU)
Average Temp ("F) 144.0878 110.8551 Skin Temperature 
(*F) 120.3509 112.9962 U Overall (BTU/hr-ft 2.&deg;F)Velocity *** 4238.791 5.52875 Effective Area (ftW)Reynold's Number 946.3845 ** 36742.29 LMTD Prandtl Number 0.725478 4.006047 Total Heat Transferred (BTU/hr)Bulk Visc (Ibm/ft'hr) 0.048993 1.471354 Skin Visc (Ibm/ft'hr) 1.440431 Surface Effectiveness (Eta)Density (ibm/ft')
0.062393 61.84786 Sensible Heat Transferred (BTU/hr)Cp (BTU/Ibm-&deg;F) 0.240245 0.998826 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft-OF) 0.016224 0.366848 Heat to Condensate (BTU/hr)&#xfd;.. Reynolds Number Outside Range of Equation Applicability
)1612.69 0.007083 8.933621 0.000294 0.037342 5.880206 1053.234 33.07128 204818.2 0.921529 204818.2 Air-Side Mass Flow (Ibm/ht) 104644.6 Inlet Temperature 
(&deg;F) 140.1758 Outlet Temperature 
(&deg;F) 133.5736 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (&deg;F) 136.8747 Skin Temperature 
(&deg;F) 116.7764 Velocity *** 4238.791 Reynold's Number 955.0962 Prandtl Number 0.726116 Bulk Visc (Ibm/ft.hr) 0.048546 Skin Visc (Ibm/ft.hr)
Density (Ibmtft 3) 0.063087 Cp (BTU/Ibm'F) 0.240245 K (BTU/hr-ft-&deg;F) 0.016062** Reynolds Number Outside Range of Equation Applica Extrapolation Calculation for Row 2(Dry)Tube-Side 89504.32 Tube-Side hi (BTU/hr-ft'-OF) 107.7758 j Factor 109.709 Air-Side ho (BTU/hr-ft 2-OF)Tube Wall Resistance (hr-ft=.&deg;F/BTU)
Overall Fouling (hr-ft2.&deg;F/BTU) 108.7425 110.5706 U Overall (BTU/hr-ftl.&deg;F) 5.526084 Effective Area (ft2)35969.7 LMTD 4.100739 Total Heat Transferred (BTU/hr)1.502958 1.475547 Surface Effectiveness (Eta)61.8777 Sensible Heat Transferred (BTU/hr)0.998847 Latent Heat Transferred (BTU/hr)0.366082 Heat to Condensate (BTU/hr)1593;929 0.007061 8.900292 0,000294 0.037342 5.861286 1053.234 27.99597 172827.7 0.921793 172827.7 Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 18 of 43 Page 5 VY03A-AU.XLS PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Extrapolation Calculation for Row 3(Dry)Air-Side Tube-Side Mass Flow (Ibm/hr) 104644.6 89504.32 Tube-Side hi (BTU/hrlft.l'F)
Inlet Temperature 
('F) 133.5736 106.143 j Factor Outlet Temperature (0 F) 127.9973 107.7758 Air-Side ho (BTU/hr.ft 2.&deg;F Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr.ft 2'&deg;F/BTU Outlet Specific Humidity 0.020268 Overall Fouling (hr-ftl.*F/BTU)
Average Temp ('F) 130.7854 106.9595 Skin Temperature 
('F) 113.7605 108.519 U Overall (BTU/hr ftl.&deg;F)Velocity *** 4238.791 5.52388 Effective Area (f11)Reynold's Number 962.6409 ** 35322.05 LMTD Prandtl Number 0.726616 4.183518 Total Heat Transferred (BTU/hr)Bulk Visc (lbm/ft.hr) 0.048165 1.530515 Skin Visc (Ibm/ft-hr) 1.506367 Surface Effectiveness (Eta)Density (Ibm/ft3) 0.063686 61,90239 Sensible Heat Transferred (BTU/hr)Cp (BTU/lbm."F) 0.240245 0.99887 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft.&deg;F) 0.015925 0.365426 Heat to Condensate (BTU/hr)** Reynolds Number Outside Range of Equation Applicability F))1578.041 0.007042 8.872166 0.000294 0.037342 5.845234 1053.234 23.71117 145975.4 0.922016 145975.4 Extrapolation Calculation for Row 4(Dry)Tube-Side Air-Side Mass Flow (Ibm/hr) 104644.6 89504.32 Tube-Side hi (BTU/hr.ft2-=F)
Inlet Temperature 
(&deg;F) 127.9973 104.7628 j Factor Outlet Temperature 
(&deg;F) 123.2834 106.143 Air-Side ho (BTU/hr.ft2.&deg;F Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2 0.F/BTU)Outlet Specific Humidity 0.020268 Overall Fouling (hr.ft 2-&deg;F/BTU)Average Temp (&deg;F) 125.6403 105.453 Skin Temperature 
(&deg;F) 111.2133 106.7826 U Overall (BTU/hr-ft 2.&deg;F)Velocity *** 4238.791 5.522051 Effective Area (ftW)Reynold's Number 969.1571 ** 34778.02 LMTD Prandtl Number 0.72701 4.255589 Total Heat Transferred (BTU/hr)Bulk Visc (Ibmnft-hr) 0.047841 1.554457 Skin Visc (Ibm/ft-hr) 1.533295 Surface Effectiveness (Eta)Density (Ibm/ft 3) 0.064201 61.9229 Sensible Heat Transferred (BTU/hr)Cp (BTU/lbm.OF) 0.240245 0.998893 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft.*F) 0.015809 0.364865 Heat to Condensate (BTU/hr)** Reynolds Number Outside Range of Equation Applicability
;))1564.579 0.007025 8.84841 0.000294 0.037342 5.831615 1053.234 20.0905 123397 0.922204 123397 Extrapolation Calculation for Row 5(Dry)Air-Side Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp ("F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/ft')Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft-&deg;F) 104644.6 123.2834 119.2958 0.020268 0.020268 121.2894 109.0602 4238.791 974.7719 0.727321 0.047566 Tube-Side 89504.32 Tube-Side hi (BTU/hr.ftl'.F) 103.5953 j Factor 104.7628 Air-Side ho (BTU/hrft 2'&deg;F)1553.173 0.007011 8.828331 0.000294 0.037342 Tube Wall Resistance (hr-ft 2-OF/BTU)Overall Fouling (hr.ft 2-"F/BTU)104.1795 105.3123 U Overall (BTU/hr.ft 0.OF) 5.1 5.520528 Effective Area (ft 2) 10 34320.49 LMTD 17 4.318086 Total Heat Transferred (BTU/hr) 10 1.57518 1.556723 Surface Effectiveness (Eta) 0, 61.93997 Sensible Heat Transferred (BTU/hr) 10 0.998915 Latent Heat Transferred (BTU/hr)0.364387 Heat to Condensate (BTU/hr) Proto-Power Calc: 97-199 

==Attachment:==

j 820059 53.234.02872 4384.1 922363 4384.1 0.064643 0.240245 0.015712 Rev: A Page 19 of 43 Page 6 VY03A-AU.XLS PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 6(Dry)Air-Side Tube-Side Mass Flow (Ibm/hr) 104644.6 89504-32 Tube-Side hi (BTU/hr-fPt-F)
Inlet Temperature (OF) 119.2958 102.6071 j Factor Outlet Temperature 
(&deg;F) 115.9206 103.5953 Air-Side ho (BTU/hr-ftW.&deg;F Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2.&deg;F/BTU Outlet Specific Humidity 0.020268 Overall Fouling (hr.ft2-&deg;F/BTU)
Average Temp (OF) 117.6082 103.101 Skin Temperature (OF) 107.2384 104.066 U Overall (BTU/hr-ft2-&deg;F)
Velocity***
4238.791 5.519256 Effective Area (ft2)Reynold's Number 979.5995 "* 33934.63 LMTD Prandtl Number 0.727568 4.372184 Total Heat Transferred (BTUihr)Bulk Visc (Ibm/ft-hr) 0.047331 1.59309 Skin Visc (Ibm/ft-hr) 1.577049 Surface Effectiveness (Eta)Density (Ibm/fP) 0.065022 61.95425 Sensible Heat Transferred (BTU/hr)Cp (BTU/Ibm-&deg;F) 0.240245 0.998935 Latent Heat Transferred (BTU/hr)K (BTU/hr.ft-&deg;F) 0.015629 0.363978 Heat to Condensate (BTU/hr)** Reynolds Number Outside Range of Equation Applicability
;))1543.495 0.006999 8.811349 0.000294 0.037342 5.81025 1053.234 14.4379 88353.51 0.922498 88353.51 Air-Side Mass Flow (Ibm/hr) 104644.6 Inlet Temperature (OF) 115.9206 Outlet Temperature 
(&deg;F) 113.0624 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (&deg;F) 114.4917 Skin Temperature 
(&deg;F) 105.6963 Velocity *** 4238.791 Reynold's Number 983.7432 Prandtl Number 0.727765 Bulk Visc (Ibm/ft-hr) 0.047132 Skin Visc (Ibm/ft-hr)
Density (Ibmift3) 0.065347 Cp (BTU/Ibm.&deg;F) 0.240244 K (BTUfhr-ft.&deg;F) 0.0115559** Reynolds Number Outside Range of Equation Applica Extrapolation Calculation for Row 7(Dry)Tube-Side 89504.32 Tube-Side hi (BTU/hr-ft 2.&deg;F)101.7702 j Factor 102.6071 Air-Side ho (BTU/hr-ft2.&deg;F)
Tube Wall Resistance (hrft 2.F/BTU)Overall Fouling (hr-ft 2-&deg;F/BTU)102.1879 103.0096 U Overall (BTU/hr-ftz 2.F)5.518191 Effective Area (ft')33609.16 LMTD 4.418844 Total Heat Transferred (BTU/hr)1.608518 1.594624 Surface Effectiveness (Eta)61.96621 Sensible Heat Transferred (BTU/hr)0.998954 Latent Heat Transferred (BTU/hr)0.363629 Heat to Condensate (BTU/hr)1535.286 0.006989 8.796979 0.000294 0.037342 5.801925 1053.234 12.24441 74822.97 0.922612 74822.97 Extrapolation Calculation for Row 8(Dry)Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature 
(&deg;F)Velocity **Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ft.hr)
Density (Ibm/fl')104644.6 113.0624 110.6407 0.020268 0.020268 Tube-Side 89504.32 Tube-Side hi (BTU/hr.ft'.'F) 101.0612 j Factor 101.7702 Air-Side ho (BTU/hr-ft3.'F)
Tube Wall Resistance (hr-ft.&deg;FBTU)
Overall Fouling (hr-ft2.=F/BTU) 111.8516 101.4156 104.3909 102.1149 U Overall (BTU/hr-ftf.&deg;F) 4238.791 5.5173 Effective Area (ft')987.2948 ** 33334.75 LMTD 0.727923 4.458934 Total Heat Transferred (BTU/hr)0.046963 1.621759 1.609762 Surface Effectiveness (Eta)0.065624 61.97622 Sensible Heat Transferred (BTU/hr)1528.334 0.006981 8.784811 0.000294 0.037342 5.794861 1053.234 10.38637 63391.63 0.922708 63391.63 Proto-Power Calc: 97-199 VY03A-AU.XLS

==Attachment:==

J Rev: A Page 20 of 43Page 7 PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Cp (BTU/Ibm&deg;*F) 0.240244 0.99897 Latent Heat Transferred (BTU/hr)K (BTU/hrftt-F) 0.0 155 0.363332 Heat to Condensate (BTU/hr)Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 9(Dry)Air-Side Tube-Side Mass Flow (Ibm/hr) 104644.6 89504.32 Tube-Side hi (BTU/hr-ft'.&deg;F)
Inlet Temperature 
(&deg;F) 110.6407 100.4603 i Factor Outlet Temperature (OF) 108.5883 101.0612 Air-Side ho (BTU/hr-ft 2-&deg;F Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ftl.'F/BTU Outlet Specific Humidity 0.020268 Overall Fouling (hr-ftW-&deg;F/BTU)
Average Temp (&deg;F) 109.6146 100.7607 Skin Temperature 
(&deg;F) 103.2846 101.3556 U Overall (BTU/hr-ft 2-"F)Velocity *** 4238,791 5.51655 Effective Area (ft-)Reynold's Number 990.3344 ** 33102.65 LMTD Prandtl Number 0.72805 4.493396 Total Heat Transferred (BTU/hr)Bulk Visc (Ibm/ft-hr) 0.046818 1.63313 Skin Visc (Ibm/ft-hr) 1.622796 Surface Effectiveness (Eta)Density (Ibm/fl 3) 0.065861 61.98464 Sensible Heat Transferred (BTU/hr)Cp (BTU/Ibm'&deg;F) 0.240244 0.998985 Latent Heat Transferred (BTU/hr)K (BTU/hrft-&deg;F) 0.015449 0.36308 Heat to Condensate (BTU/hr)"* Reynolds Number Outside Range of Equation Applicability
=))1522.43 0.006973 8.774505 0.000294 0.037342 5.788863 1053.234 8.81192 53726.53 0.92279 53726.53 Extrapolation Calculation for Row 10(Dry)Tube-Side Air-Side Mass Flow (Ibm/hr) 104644.6 89504.32 Tube-Side hi (BTU/hr-ft 2.&deg;F)Inlet Temperature (OF) 108.5883 99.95088 j Factor Outlet Temperature 
(&deg;F) 106.8483 100.4603 Air-Side ho (BTU/hr.ft 2-&deg;F Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2-&deg;F/BTU)Outlet Specific Humidity 0.020268 Overall Fouling (hr-ft=-&deg;F/BTU)
Average Temp (&deg;F) 107.7184 100.2055 Skin Temperature 
(&deg;F) 102.3469 100.7115 U Overall (BTU/hr-ft2,&deg;F)
Velocity *** 4238.791 5.515919 Effective Area (ft 2)Reynold's Number 992.9331 ** 32906.36 LMTD Prandtl Number 0.728154 4.522943 Total Heat Transferred (BTU/hr)Bulk Visc (Ibm/ft hr) 0.046696 1.642872 Skin Visc (Ibm/ft-hr) 1.633988 Surface Effectiveness (Eta)Density (Ibm/ft 3) 0.066063 61.99173 Sensible Heat Transferred (BTU/hr)Cp (BTUIlbm.&deg;F) 0.240244 0.998992 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft-&deg;F) 0.015407 0.362865 Heat to Condensate (BTU/hr)"* Reynolds Number Outside Range of Equation Applicability
.-))1517.421 0.006967 8.765772 0.000294 0.037342 5.783772 1053.234 7.477258 45548.96 0.922859 45548.96 Air Mass Velocity (Lbm/hr-ft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Proto-Power Caic: 97-199 

==Attachment:==

J VY03A-AU.XLS Rev: A Page 21 of 43 Page8 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 1)t. PROTO-HX Output -Fouling Calculation di Cft) /Ad (ftA2) =Ao (ftA2) =AoIAI I do (ft)Udo/do (%) =Udo (ft)II. PROTO-HX Output -Extrapolation Calculation di (ft) = 0.043910667 Ai (ftA2) 29.80114791 Ao (ftA2) = 1053.234205 AoIAI 3534206831 do (ft) 0052083333 Udoldo (%)Udo (ft) o.o04lef, 7 Nt 24 Lambda (fins/ift)
L (ft) = 9 UL (0/0) 0.23 UL(fl) = 0.0207I Nt =NI =Lambda (fins/ft) 
=L (ft)ULL(%)tfln (ft)Utftinltfin 
(%) =hfln (ft)=Uhiln/hlin 
(%)=Mdotc (lbmlhr)Q (Ft^3/hr) 
=DT (DegF) =rho (lbmdft^3) 
=Urho/rho (%) =Cp (BtuflbmIDegF)
UCpICp (%)UL(ft)Utfin (ft) a I:hfi (fIt)Urho UCp =tMrs (ft) =Utfinlttin 
(%)Win (fl) =Ubfin/hrim 
%Mdotcl (1bm/hr)Q* (Ft'131hr)
D'T (De9F)rho flbmn/ftA3)
Urho~/rho* 
(%)Cp* (Btu/bIbnDeqFJ UCP*/Cp' (%) =q* (Btu/hr) =LMTD* ( DegF)Uo* =R* -(1/Ua)=Rf [(hr-0egF-ftt-2)/Btu]
Etas =ha* [BtuI(hr-DegF-ftA2)j ho*(eft) [Btu/(hr-DegF-ftA2)]
hi* [Btu/(hr-DegF-ft112)j UhtIfhi (%)=Rw' [(hr-OeqF-ftA2)IBtuj UR'wIRw M%)=0.001 2 481.174 Utfin(ft 33.07128037 010.1217 0.00134208 8.9043620386 2 2.232951074 Urho w, 1.234895163 ti3F 689988555 Uhr*33.012803 5.80D59 q (Stu/hr) =LMTD ( egF)Uo=R = (lIUo)Rf [(hr-DegF-ft^2)Btuj Etas ho [BtuI(hr-OegF-ftA2)]
ho(eff) [Btu/(hr-OogF-ftA 2)]Uho/ho (%) =hi [BtuIjhr-DegF-ftA'2)j Uhi/hi (%) =Rw [(hr-DegF~ftA 2)/Btuj URwIRw (%)Uho=Uhl=URw =Proto-Power Catc: 97-199 

==Attachment:==

J Rev: A Page 22 of 43 Page 9 ,0o3A .AUXLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 1)I Anah'tical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAolAo UAo 1053.23421 0.05208 0.00417 9.00000 0.02070 0.00100 0.00004 0.12100 0.00167 0.04277 45.04379 Derivatives: 
-7287.99 117.03 11223.78 19868.94 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty In Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R* ho* Uho* hi* Uhl* Rw* URw* Rf URf UR*IR* UR*0.17006 8.23259 1.23489 1612.68995 241.90349 0.00029 0.00001 0.03734 6.46O 0.10887 0.01851 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R' UR* Ao UAo LMTD* Uq*/q* Uq.204818.1740 0.17006 0.01851 1053.23421 45.04379 33.07128 0.11697 23957.07518 Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 23 of 43 VY03A-AU.XLS Page 10 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 2)I. PROTO-HX Output -Fouling.Calculation dl (Ift) =Ai (Mf^2) =Ao (ftA2)Ao/Ai do (ft)Udo/do (%)Udo (ft) =Nt=NI=Lambda (finslft) 
=L (ft) =UUL (%)06 WI. PROTO-HX Output -Extrapolation Calculation d! (ft) a 0.043916G67 Ai (ftA2)- 29.80114791 Ao (ft2l2) 1053.2.34205 Ao/AI = 35.34206831 do (ft) 0 00208333 Udoldo (%)Udo (ft) o004,r,667 Nt = I 241 NI = 2I Lambda (finslift)=
1 L (ft) =UUL (%) 0.23 UL(ft) =tfin (if) =Utfin/tfln M%) =hrf (1) =(Whflihtin 
(%)Mdotc (Ibm/hr) =0 (FtV31hr) 
=DT (DegF) =rho ([bmlftA3) 
=Urho/rho (%) =Utfin (ft)Uhnfin (It)Cp (Btu/ibmJDegF)
UCpICP %q (Btufhr)=LMTD (DegF)Uo=R = (lIUo)=Rf [(hr-OegF-ftA2)IBtuJ Etas =ho [BtuJ(hr.OegFftA 2)]ho(eft) [BtuI(hr-OegF~ftA 2)) =Uho/ho (%) =h! [BtuJ(hr-DegF-ftA2)]
MUMih (%) =Rw [(hr-DeqF-fttA2)IBtuJ IJRw/Rw (%) =Urho UCp ifiri (ft) =Utfin/tfin(%
hfin (it)I.liflij/hrin()
Mdotc, (lbm/hr)=Q* (Ft'3/hr)=
DTI (DegF)rho* (lbm/ftA3)
Urho/irho* 
(%)=Cp* (BtuIltbmiDegF)a UCp*/Cp* (%) =qI (Btu/hr) =LMTD* ( DegF)U = (U'Rf [(hr-DegF-ftA2)IBtuj Etas =ho* [BtuI(hr-DeqF-ftA2)1 ho*(etf) [Btu/(hr-DegF-ft'12)]
Uho/lho* (%) =hi* [BtuI(hr-OogF-ft&-2)j Uhithi* (%) -Rw' [(hr-DegF-ftA-2)/Btuj U Rw*/Rw' M) =Urhiln (ft)=0.812511 0.037408 8.933129233 Urho* 1.237653913 5.86[~9312851 l.is URw* E2~Uho =Uhi =URw Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 24 of 43 VYM.A-AU.ALS Page 11 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 2)I Analytical Uncertainty in Hleat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 1053.23421 0.05208 0.00417 9.00000 0.02070 0.00100 0.00004 0.12100 0.00167 0.04277 45.04379 Derivatives: 
-7287.99 117,03 11223.78 19868.94 2 Analytical Uncertainty In Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty In Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho" hi* Uhl* Rw' URw* Rf URf UR*IR&deg; UR*0.17061 8.20423 1.23063 1593.92875 239.08931 0.00029 0.00001 0.03734 0.00000 0.10892 0.01858 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R&deg; UR* Ao UAo LMTDO Uq/Iq&deg; Uq*172827.7249 0.17061 0.01858 1053.23421 45.04379 27.99597 0.11702 20223.83227 Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 25 of 43 Page 12 VY03A-AU.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 3)I. PROTO-HX Output -- Fouling Calculation di (ft) =Al (ft^2) =Ao (ftA2)Ao/A=do (ft)Udoldo (%)Udo (ft)Nt =NI =Lambda (fins/ift) 
=L (ft) =ULL (%) =II. PROTO-HX Output -- Extrapolation Calculation dl (ft) = I 0.043916667 Ai (ftA2) 2)80114791 Ao (ftA2) = 1053.234205 AoAi = 3534206831 do (if) 0.052083=Udo/do (%) 8 Udo (ift) = 0.0041667 Nt = Z" 124t Nl= 2 Lambda (fins/Ift)
L (ft) =UUL %23 UL(ft) z tfln (ft) =Utfln/tfin 
(%)Mhn fit) =Uhrla/hfln(%=
Mdotc (Ubmnhr) =Q (FtA3/hr)=
DT (DegF)=rho (Ibmn/ftA3) 
=Urho/rho (6) =Cp (Btu/Ibm/DegF)
UCpICp (%) =Utfin (ft)Uhfin (ft)Urho =UCp =ttin (if) =Utfinitfin N%Wiln 4ft) =Mdotc* (lbn&#xb6;/hr)Q* (Ft^3Jhr)DT* (OegF)=rho* (Ibm/ft A3)=Urho/irho*
M)Cp* (Btu/IbnVDeqF)
UCP/ICP* (%) M q* (Btu/hr) =LMTD* (DegF)=Uo* =fV= (1/Uci)Rf U(hr-DegF-ftA2)IBtu]
Etas =ho* [BtuI(hr-DegF-ftA2fl ho*(etff [Btu/(hr-DaqF-(tA12)j Uho/fho (%A)=hi* [Btu/(hr-OeqF-ft-2)]
Uhi-thi (%) =Rw* [(hr-DegF.ftt2)/BtuJ URw*/Rw* (%)=0.001 Utfln (ft) Lihff al 0.12 145.89451133 0.998869571
~~82 145975.4497j 23.71116759 5.42343 0.17079-q (Btu/hr) =LMTD ( DegF)Uo =R(=1/Uo)Rf [(hr-DegF-ft112)/Btu] 
=Etas=ho [Btu/(hr-DegF-ft'^2)j 
=ho~eff) [Btu/(hr-DegF-fthA2)]
Uholho (%)=hi [Btu/(hr-DegF-ftA2)j lihi/hi (%) =Rw [(hr-DegF-ftA2)/Btu]
URwIRw M%) =Uho =Uhi =URwc Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 26 of 43 Page 13 VY0:3A-ALI.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 3)I Analvtical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 1053.23421 0.05208 0.00417 9.00000 0.02070 0.00100 0.00004 0.12100 0.00167 0.04277 4504379 Derivatives: 
-7287.99 117.03 11223.78 19868.94 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho* hi* Uhi* Rw* URw* Rf URf UR*/R* UR*0.17108 8.18028 1.22704 1578.04098 236.70615 0.00029 0.00001 0.03734 0.00000 0.10897 0.01864 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R" UR* Ao UAo LMTDO Uq'iq* Uq*145975.4497 0.17108 0.01864 1053.23421 45.04379 23.71117 0.11706 17087.72434 Proto-POwer Calc: 97-199 

==Attachment:==

J Rev: A Page 27 of 43 Page 14 VY03A-AU.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 4)I PROTO4HX Output -Fouling Calcul di (if) =A! (ft^2) =Ao (ft12)AoWAi =do (ft) =Udoldo (%) =Udo ft)Nt =NI=Lambda (flnslfi) 
=L (ft)ULL (%) =It. PROTO-HX Output -Extrapolation Calculation di (ft) =0043916667 Al ((tA2) -2980114791 Ao (ftW2) = 1053234205 Ao/AI =35.34ZM3 do (ft) [ 0.0520,833331 Udotdo (%) =Udo (ft) 0.00416867 Nt -24J Nt = FIZZi NI =Lambda (ftnslft) 120 L (ft) =ULIL ()23 UL(ft) = o .2o7J UL(ff) =tfin (ft) =Utfinitfin 
(%) =hrw (ft)Uhlbn/hfin 
(%)=Mdotc (Ibmlhr) =Q (Fta3Jhr) 
=DT (DegF) =rho (tbrmiftA3)
Urho/rho (%) =Utfin (ft) =Ilhfin (11) =Urho =Cp fBtunlbmIDegF)
UCpICP(%q (Btu/hr)LMrD ( DegF)Uo-R =(IfUo) -Rf [(hr-OeqFiftA2)iBtu1 Etas =ho [Btu/(hr-DegF-ft112)j ho~eff) [BtuI(hr.DegF-fttA2)]
Uho/ho Nz hi [Btu/(hr.DegF~ftA2)]
MhIhN (%) =Rw j(hr4:OegF-ft12)JBtuj URwIRw M)=UCp tfin (ft) =Utfinrtfin 
(%) =hfln (f1) -IUhfln~bfln 
(%) -Mdotcl (Ibm/hr) =Q* (Ftt31hr)DTr (DegF)=rho' (IbmiffA3) a Urho*/rho* 
(%) =Cp* (BtuIlbm/DegF)
UCp*ICp" (%)q" (Btulhr) =LMTD* (DegF)Uo* =R* = (IlIUo] =Rf [(hr-OegF-ftA2)IBtuj 
=Etas =ho' [Btu/(hroDogF-ftA2)=
ho*(eff) [Btul(hr-DegF-ftA2)]
Uho'lho (%) =hil [Btu/(hr-DegF-ft^2)1 
-Uhi'/hl (%) =Rw* [(hr-DegF-ftA2)/Btu] 
=URw'IRw" (%) =0 .0o01 Utfin (ft) =E=.ai47 S 445.4156521 1.380210229 61.92289654
~1~2 Urho* 1.238457931 0.9892815 Ucp* 0 0=9L77856 123396-9987 20.09060152 5.831615259 0.171479077

==0.0 37342065==
0.922203852 8.848410099
-8.160037881 I.5 Uho' = 1-224005682 1!A4.57931 1 Uhi* = 24.086 URw* = , 8252E-406 Uho =Uhi =URw=Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 28 of 43 VY')3A-AL..LS)P 1 Page I5 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 4)I Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAoiAo UAo 1053.23421 0.05208 0.00417 9.00000 0.02070 0.00100 0.00004 0.12100 000167 0.04277 45.04379 Derivatives: 
-7287.99 117.03 11223.78 19868.94 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R" ho* Uho* hi* Uhi* Rw* URw Rf URf UR*R* UR*0.17148 8.16004 1.22401 1564.57931 234.68690 0.00029 0.00001 0.03734 0.00000 0.10900 0.01869 6 AnalytIcal Uncertainty in Extrapolated Heat Transfer q. R' UR* Ao UAo LMTDO Uq*/q&deg; Uq&deg;123396.9987 0.17148 0.01869 1053.23421 45.04379 20.09050 0.11709 14449.01463 Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 29 of 43 VY03A-AU.XLS Page 16 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 5)I. PROTO-HX Output -- Fouling Ca(culz di (It) =Al (ftA2) -Ao (ftA2)AoIAI do (ft) =Udoldo (%)Udo (ft)Nt NI=Lambda (fins/ft)L (fl) =ULIL (%) =fl. PROTO-HX Output -- Extrapolation Calculation di (ft) = 0.043916M7 Al (ftA2) 20.80114791 Ao (ft^2) 1053.234205 Ao/AI 35.34206831 do (ft) 0.052083333 UclO/dO (%)=Udo (ft) = 0.0041867 Nt =24 NI= 2 Lambda (fins/if) 12 L (ift)UL(ft)J 0.0207[UL(ft) =tmn (ft) =Utfin/tfln 
(%) =hfin (ft) =['hfln/h fin (%) =Mdotc (Ibm/hr) =Q (Ft3/Ihr)DT (DegF) 2 rho (IbmIftA3) 
=Urho/rho (%)Cp (BtullbmrDegF) 
=UCp/Cp (%) =Utfin (ft) =Ubfhn (Rt)Urho=UCp =Min (ft) =Utfln/tfin(%
WIGtnh~ (11 %)Mdotc* (ibmlhr)=Q* (FtA3/hr)=
DT* (DegF)=rho* (tlhrr.ftA 3)=Utho*lrho* 
(%)Cp* (Btuflbm/OeDgF)=
UCp*/Cp* (%) =q* (Btulhr) =LMTD* (DegF)Uo*R*= (iI1.o')Rf [(hr-DegF-ft112)IBtuj Etas =ho* [StuJ(hr-OegF-ftA2fl ho*(eff) [Btu/(hr4OagF-ftA2)J Uho/lho' M =hi* (BtuI(hr-DegF-ftA2fl U h NI Mi( =Rw' j(hr-DegF-ftA2)IBtu]
URw*/Rw* (%) =1-~388~~1445072 61.9399430 17.02871803 5.820059059 0.171819562

==0.0 37342068==
0.922362959 8.82833058 8.142925i16 Uho* = 1.221438767 0.00294 126~l2 LIRW = 5.85E0 q (B~tuhr)=LMTD ( DegF)2 U0 =R =(1ION)=Rf [lhr-OegF-ftA2)JBtuj Etas =ho [BtuI(hr..DegF4fA 2)]ho(eff) [Btu/(hr~OogF-ft42)j U ho/ho (%') =hi [BtuI(hr-DegF-ftA2))
UhI/hi (%) =Rw j(hr-DeqF-ft112)IBtuj U RwIRw (%) =Uho =Uhi =URw =Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 30 of 43 VYO.IA..AU XLS Pa'Je 17 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 5)I Analytical Uncertainly in [feat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAoIAo UAo 1053.23421 0.05208 0.00417 9.00000 0.02070 0.00100 0.00004 0.12100 0.00167 0.04277 45.04379 Derivatives: 
-7287.99 117.03 11223.78 19868.94 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty In Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty In Observed Rf 5 Analytical Uncertainty In Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho" hi* Uhl* Rw* URw* Rf URf UR*IR* UR*0.17182 8.14293 1.22144 1553.17314 232.97597 0.00029 0.00001 0.03734 0.00000 0.10904 0.01873 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R" UR* Ao UAo LMTD* UqIq&deg; Uq*104384.0880 0.17182 0.01873 1053.23421 45.04379 17.02872 0.11712 12225.77360 Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 31 of 43 Page 18 VY03A-AU.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 6)I. PROTO.HX Output -- Fouling Calculation di (ft) =Ai (ft-2) =Ao (ft^2) =Ao/A=do (ft) -Udoldo (%) =Udo (ft)=Nt=NI=Lambda (finslft) 
=L (ft) =ULIL(%) =II. PROTO-HX Output -- Extrapolation Calculation di (ft) = 0.U43516667 A! (ftA2) =  Ao (IV"2) ilo3 234205 AolAj =35 34206831 do (ft) = 0.052083333 Udoldo (%)Udo (ift) = 0.00415667 Nt =Lambda (fins/ft) 
[120 L (ft) =UL (/) =0.23 UL(ft) _ 0.0207_UL(ft) =tfln (Ift) =Utfinltfin 
(%) =Wll (ft) -Uhrin/hfin 
(%)=Mdotc (Ibmlhr) =Q (Ft^31hr) 
=OT (DegF)rho (Ibm/ftA3)
Urho/rho (%) =Cp (BtuAbm/DegF)
UCp/cp (%) =Utfln (ft)Uhflh (ft)=Urho UCp trin (ft) =Utfin/tfin(%
Uhflnhn (%))Mdotcl (Ibmihir)Q* (Ft^31hr)DT* (DegF)rho* (ibml/ftA3)
Urho*/rho' 
(%)Cp (Btu/tlbsnDegF)
UCpl'Cp, M%)q* (Btuihr) =LMTD1 (DeqF)=Ue=R' =(1/Uo*)Rf j~hr4DegF-ftA2)iatuj Etas =he [BtuIjhr-OogF-ftA2fl ho'(eff) [Btu/(hr.OegF~ftA 2)]Uho~lho' M) =hi' [ltu/(hr-DegF-ftA2fl UhIlhi* (%) =Rw' [(hr-OegF-ftA12)/Btu]=
URWIRW (%) =0.001 I.1T 144.6437882 0.1872183431 00.73425241 FU0999935192176 U j~~s57 88353106 14.43789828a~
5.810~325044 q (Stu/hr) =LMTD ( DeqF)U0 R =(lIUo)=Rf !(hr-OegF-ftA2)IBtuj Etas=ho [Btu1(hr-OegF-ftA2)j=
ho(eff) j~tu1(hr-DegF-ftA2)]
Uholho (%) =hi !Btu/(hr-DegF-ftA 211 WhINi (%) =Rw [(hr-OegF-ftA2)1Btu]
URwIRw (%) =Uho =Uhi =URw=Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 32 of 43 VYf):iA AU X! .$Page 1A Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 6)I Analytical Uncertainty in Heat Transfer Surface Area An Do Ud L UL tfin Utfin hfin Uhfin UAoIAo UAo 1053.23421 0.05208 0.00417 9.00000 0.02070 000100 0.00004 0.12100 0.00167 0.04277 45.04379 Derivatives: 
-7287.99 117.03 11223.78 19868.94 2 Analytical Uncertainty in Test Hteat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho' hi* Uhl* Rw* URw* Rf URf UR*R* UR&deg;0.17211 8.12845 1.21927 1543.49457 231.52419 0.00029 0.00001 0.03734 0.00000 0.10906 0.01877 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R" UR* Ao UAo LMTD" Uq-lq- Uq.88353.5056 0.17211 0.01877 1053.23421 45.04379 14.43790 0.11715 10350.39262 Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 33 of 43 VY03A-AU XLS Page 20 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 7)1. PROTO-HX Output -- Fouling Calculation di (ft) =At (ftA2)Ao (ftA2)Ao/Ai =do (ft)Udo/do (%) =Udo (ft)Nt=NI=Lambda (finsift) 
=L (It) =UJL(%)=II. PROTO-HX Output -- Extrapolation Calculation di (ft) = 0.0439161367 Al (ftW2) 29.80114791 Ao (ftA^2) 1053 2.34o0 AoAi = 35.3420631 do (ft) 0 0.052083333 Udo/do (%) = a Udo (ft) = 0.00410667 Nt= 24 NI=C Lambda (finsill)=
120 L (ft) =ULL (%)0.23 UL(ft) =tfin (ft) =Utfirdtfin 
(%) =hfia (ft) =UbfinJhfia 
(%) =Mdotc (Ibmihr) =a (Ft^3/hr)DT (DegF) =rho (Ibmift^3)
Urholrho (%) =Cp (Btu/lbmtnegF)
UCpICp (%) =Uffin (ft) a U h fn (ft) =Urho =UCP ifin (ft) =Utfjinitfin 4%)=hfIn (ft)-lilifinilhfin(%
Mdotc* (bmlhr)Q' (Ft^31hr)=
DT* (DeqF)rho* (WgMJftA 3)Urho/lrho* 
(%)Cp* (BtuAbm/DgqF)
UCp,/Cp, 4%)q* (Btulhr) =LMTO* ( DegF)Uo* =R*= (I/Uoj =Rf I(hr43egF-ftA2)/Btuj]
Etas =ho* [Btu/(hr.OegF-ft"2)]
ho*(eff) [BtuI(hr-DegF-ftA2)]
Uho*Iho' (%) =hi' [Btuil hr-DegF4tA 2)]Uh'IhiP (%) =Rw* [(hr-DegF-ftA12)16tuI URwI/Rw'(%)=
0.001 4.17b Utfin if).= 0.00004171 Win. (ft) =E ooea8 0121 hf. (ot)- 1 16 0.836912872I 61 .96620637J Urho* 1.239324127 0.998953792 UCp* 0019979076 74822.96581 12.24440881 5.801925428 0.172356576 0-037342068 0.922611524 8.796979195
-8.116194385 Uho= 1.217429158
' 1526 o -00094 =z6 URw* =E?5.SB25 2 EA62 q (Btu/hr)=LMTD ( DegF)=Uo=R= (lIUo)=91 j~hr-DeqF-ft112)/Btuj Etas =ho (Btu/W-rDegFiftA2)]=
ho(eff) [Btu/(hr-DegF-ft'I2)]
Uholho (%) =hi [Btul(hr-LDegF-ftA2)1 Uhi~hl 4%) =Rw [(hr-OegF-ftA2)I~tuj URw/Rw (%) =Uho =Uhi=URw =Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 34 of 43 VY03A-Aki Xi S Page 21 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 7)I Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 1053.23421 0.05208 0.00417 9.00000 0.02070 0.00100 0.00004 0.12100 0.00167 0.04277 45.04379 Derivatives: 
-7287.99 117.03 11223.78 19868.94 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty In Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho" hi* Uhi* Rw* URw* Rf URf UR*R&deg; UR*0.17236 8.11619 1.21743 1535.28639 230.29296 0.00029 0.00001 0.03734 0.00000 0.10908 0.01880 6 Analytical Uncertainty in Extrapolated Heat Transfer q" R" UR* Ao UAo LMTD" Uq*/q* Uq*74822.9658 0.17236 0.01880 1053.23421 45.04379 12.24441 0.11717 8766.86859 Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 35 of 43 VY03A-AU.XLS Page 22 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 8)I. PROTO-HX Output -- Fouling Calcul dl (ft) =Ai (ftA2)Ao (ft^2)=Ao/AI do (ft)Udo/do (%) =Udo (ft)Nt =NI =Lambda (fins/ift) 
=L (ft) =UUL (%) =II. PROTO-HX Output -Extrapolation Calculation di (ft) 0 0U43916667 Al (ftA2) = 29.0114791 Ao (ftA2) = 1053.234205 Ao/AI =3534208831 do (ft) =0.052o3333 Udoldo (%) =Udo (ft) 004168687 Nt 24 NI= 2 Lambda (fins/fl) 
=12 L (ft) =UL/L (%) =.23 UL(tl) = 0.0207 UL4ft) =tfln (ft)a Utfln/tfln(%=
hrin (ft)Tlihfin/brin 3/4Mdatc (Ibm/tir)0 (FtA3Ihr)DT (DegF)=rho (Ibm/ft A3)Urho/rho (%) =Cp (BtuilbmIDegF)
UCp/Cp (%) =Utfin (ft) =Uhfln (Vt) -Urho =UCp.tfln (ft) =Utfin/Itln 
(%)bfin (fl)L.1hills/hrio(%
Mdotc* (Ibrn/hr)0 (Ft,431hr)
DT*(DegF)rho* (bm/ftA3)Urhoilrho* 
(%)=Cp* (StuIlbrMe~gIF) a q* (Btuihr) -LMTD* (DegF)Uo, =Vt (1/Uo*)Rf [(hr.DegF-ft'12)jBtuj 
=Eta3 =ha* [Btu/(hr.OegF ftA 2)1 ho*(eff) [Btu/(hr-DegF-ftAI2)J Utio/ho' N% =hi* (BtuI(hr-DegF~ttA 211 Uhi/h[I (%)=Rw* I(hr-DegF-ftA 2)/Btul URw*/Rw* (%) =Utfin(ft)=Lj~
0.1L~219 89504.3W 6331.762193 0.725869742 UC* 0.092270041 51984811M63
=8.10581SB54.
Uhl* =0.0002941261 URw* = 5 8852E-&#xfd;6 q (Btufth) =LMTD ( DegF) =Uo =R = (1/Uo) =Rf [(hr-DegFftA2)JBtu) 
: Etas =ho [Btu/(hr-DegP-ftA2)j 
-ho(eff) 1BtuI(hr-DegF-ft^2)) 
=Uholho (%) =hi [Btu/(hf-DegF-ftI2)I 
=Uhi/hi (%) =Rw [(hr-DegF-ftA2)/Btuj 
=URwIRw (%) =Uho I Uhl =URw =Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 36 of 43 VYO3A-AI i XLS Page 23 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 8)I Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 1053.23421 0.05208 0.00417 9.00000 0.02070 0.00100 0.00004 0.12100 000167 0.04277 45.04379 Derivatives: 
-7287.99 117.03 11223,78 19868.94 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho* hi* Uhl* Rw. URw* Rf URf UR/IR* UR&deg;0.17257 8.10582 1.21587 1528.33364 229.25005 0.00029 0.00001 0.03734 0.00000 0.10910 0.01883 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R' UR&deg; Ao UAo LMTD* Uq'lq' Uq*63391.6280 0.17257 0.01883 1053.23421 45.04379 10.38637 0.11719 7428.58409 Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 37 of 43 VY03A-AU.XLS Page 24 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 9)I. PROTO-HX Output -- Fouling Calcu di (ft) =At (ftA2)Ao (ifA2)AoIAI =do (ft)Udoldo (%) =Udo (ft)Nt=NI=Lambda (fins/f) =L (if)ULJL(%) =It. PROTO-HX Output -Extrapolation Calculation di (ft) = 0.04391Gjj7 Ai (ftA2) 29.80114791 Ao (tft 2) 1053.234205 Ao/Ai 35.34-06831 do (ft) 0.052083 Udo/do (%)Udo (ft) =  Nt a24 Ni =Lambda (fins/if) 
=120i L (ft) 9 UUL (%)0=027 UJL(ft) = 002071 UL(ft) =tfin (if) =Utfin/tfln 
(%) =hIfin (it) =UlIfm/hinu 
(%)=Mdotc (Ibm/h)=Q (FtA3/hr) 
=DT (DegF) =rho (IbmfftA3) 
=Urho/rho (%) =Cp (Bftblbm/DegF)
UCp/Cp (%) =Utfin (ft) =tjhrIn (ft)Urho UCp =ifin (ft) =Utfin/tfin(%=
Wiin (ft) =LUhrofiJfn M'I)Mdotc* (lbm/hr)Q1 (Ft"31hr)DT' (Deg F)rho* (lbmfdft63)
Urho*/rho* 
(%)Cp (BtU/IbanIDegF)=
UCp!/Cp (%)=q* (Btuihr)=LMTD ( DegF)Uo*R* -(1/Uo*)Rt [(hr-DegF-ftA12)/Btuj Etas=ho' [Btu/(hr.OegF-ftA2)I ho'(eff) (Btu1(hr-OogF-ft42)J Uhoilho* (%) =hr [BtuI(hr-(DegF-ftA2)1 Uhi'/h1- (%) =Rw* i(hr-OeqF-ftA2)/Btuj URwI/Rw' (%)=Utfin (ft) = [ 0i j (ihfn (ft) jj j 8 895"4.32386 1443.975836 0.600857156I 61.96404105I
~2 Urho* 1 239M28211 S5324 UCp, 53726,53071 8.811920175 5.788863224 0.172745488

==0.0 37342068==
0A922789817 8.774504759

==8.0 97023643==
15 Uho* -1.214553546 15 2.4302781 Uh* L= 28364 6418 URw* =L E ]q (Btu/hr)LMTD ( DagF)Uo =R = (IUo)=Rf [(hr.OegF-ftA12)/Btu1 Etas =he IBtul(hr-DegF -ftA2)1 ho(eff) [Btu/(hr-DegF-ftA2)]
Uho/ho (%) =hi iBtu/(hr-DegF~ftA 2))UhINh 1%)=Rw [(hr.DegF-ftA2)/Btu]
URw/Rw (%) =Uho =Uhl =URw=Proto-Power Calc: 97-199 

==Attachment:==

j Rev: A Page 38 of 43 VYn3A-AU XLS Page 25 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 9)I Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAoIAo UAo 1053.23421 0.05208 0.00417 9.00000 0.02070 0.00100 0.00004 0.12100 0.00167 0.04277 45.04379 Derivatives: 
-7287.99 117.03 11223.78 19868.94 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty In Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R* ho* Uho* hi* Uhi* Rw* URw Rf URf UR*IR/ UR*0.17275 8.09702 1.21455 1522.43028 228.36454 0.00029 0.00001 0.03734 0.00000 0.10912 0.01885 6 Analytical Uncertainty in Extrapolated Heat Transfer q* R' UR&deg; Ao UAo LMTD* Uq.lq* Uq&deg;53726.5307 0.17275 0.01885 1053.23421 45.04379 8.81192 0.11720 6296.76278 Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 39 of 43 VY03A-AU.XLS Page 26 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 10)I. PROTO-HX Output -Fouling Calculation di (Ift) =Ai (ft^2) =Ao (ftA2)Ao/Ai =do (ft) =Udo/do (%) =Udo (ft)Nt NI=Lambda (fins/ift) 
=L (ft) =UUL M%) =II. PROTO-HX Output -Extrapolation Calculation di (ft) = 0).0439113667 Al (ftA2) 29.8011479t Ao (fth2) 1053.234205 Ao/Ai =35 34206831 do (ft) = 05208333 Udoldo (%) =Udo (fit) = 0.0o4166667 Nt = I 7 If NI = 2zI~Lambda (finslft) 
=1 L (ft) =UL/L (%)=0.23 UL(ft) =.0207 UL(fM) a tfin (ft) =Utfinitfln 4%)=hfiuu (ft)I'hilnhfibln 
/Mdotc (lbm/hr)Q (FtA3Ihr)DT4(DegF)rho (lbm/ftA3l Urholrho (%)Cp (Btuflbm/DegF)
UCpJCp (*A) =Utfin (ft)IbtMa (ft)Urho=UCp tfim (ft) =Utfin/tfin 
(%)hfin (rt) -Ujhfln/hfln(%
Mdotc, (ibm/hr)=Q*(FtA3/hr)
DrT4DegF)rho* 4lbmtftA3) 
=Urho*irho*
M% =Cp* (lBtufibmIDegF)
UCP*ICp* %)q* (Btulhr) =LMTD* ( DegF)=Uo* =R*= 4lUoj=Rf [(hr.OogF-ftA2)!Btul Etas =ho* jBtuI(hr-DegF-ftA2))
ho'(eff) [Btu/(hr-DegF~ftA2)]
Uho*/ho* (%)=hi* [8tu[(hr-OeqF-ftA2)]
Uhi'thil (%)=Rw* f(hr-DegF-ftt'2)/Btuj URW*/Rwl (%)=1 41371 Lhfln(I().)
0.7121 0.509422401 01.917289712 0ro .2398348208 0.9969591801
= ~ 558.095718M 0925123 URw* = L~2~q (Btuflir)=-
LUMT ( DegF)=U=R = (1/Lie)RI j(hr-OegF-ftA2)IBtuj=
Etas=ha [Btuji(hr.0egF-ft-2)j ho~eff) [Btu/(hr-DegF-ftA"2)J Uha/ho (%) =hi [Btuijhr-OegF-ItA2)]
Uhi/hi (%) =RW [(hr-OagF-ftt2)/Btuj URwIRw (%) =Uho Uhl =URw =Proto-Power Calc: 97-199 

==Attachment:==

I Rev: A Page 40 of 43 VY0.3A AU XLS Page .7 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 10)I Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAoIAo UAo 1053.23421 0.05208 0-00417 9.00000 0.02070 0.00100 0.00004 0.12100 0.00167 0.04277 45.04379 Derivatives: 
-7287.99 117.03 11223.78 19868.94 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty In Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty In Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R" ho* Umo* hi* Uhi* Rw* URw Rf URf UR*IR* UR*0.17290 8.08957 1.21344 1517.42121 227.61318 0.00029 0.00001 0.03734 0.00000 0.10913 0.01887 6 Analytical Uncertainty in Extrapolated Heat Transfer q* R* UR&deg; Ao UAo LMTD* Uq'Iq* Uq.45548.9581 0.17290 0.01887 1053.23421 45.04379 7.47726 0.11721 5338.91366 Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 41 of 43 VY03A-AU.XLS Page 28 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate Extrapolated Heat Transfer (Btulhr)Calculated Uncertainty (Btu/hr)(Uq/q)^2 Row1. 204818.1740 23957.0752 0.000495 Row2 172827.7249 20223.8323 0.000352 Row3 145975.4497 17087.7243 0.000252 Row4 123396.9987 14449.0146 0.000180 Row5 104384.0880 12225.7736 0.000129 Row6 88353.5056 10350.3926 0.000092 Row7 74822.9658 8766.8686 0.000066 Row8 63391.6280 7428.5841 0.000048 Row9 53726.5307 6296.7628 0.000034 Rowl0 45548.9581 5338.9137 0.000025 1077246.0236 44051.11569 SRSS 0.040892 SRSS qtot Uqtot/qtot 
=4.09%(180 gpm Case)Proto-Power Calc: 97-199 

==Attachment:==

J Rev: A Page 42 of 43 VY03A-AU.XLS Page 29 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate Extrapolated Heat Transfer (Btu/hr)Calculated Uncertainty (Btu/hr)(Uq/q)A2 Row1 123421.7443 14238.0167 0.000230 Row2 115581.9845 13337.4092 0.000202 Row3 108279.4713 12498.2201 0.000177 Row4 101473.2524 11715.7928 0.000156 Row5 95125.8622 10985.8637 0.000137 Row6 89203.2338 10304.5540 0.000121 Row7 83673.9831 9668.2876 0.000106 Row8 78509.4314 9073.7955 0.000094 Row9 73683.3994 8518.0925 0.000082 Row10 69171.4500 7998.3902 0.000073 938123.8123 34832.2787 SRSS 0.037130 SRSS qtot Uqtot/qtot 
=3.71%(72.5 gpm Case)Proto-Power Calc: 97-199 Attachment; J Rev: A Page 43 of 43 Page 1 VY03A-AU XLS Attachment K to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

K Rev: A Page 1 of 4 COMPARING SPIRAL AND CIRCULAR FINS Area Calculation A view of the spiral fin layout as compared to the circular fin layout is provided below.Let angle ct represent the angle between the plane of the circular fin and the plane of the spiral fin.* F~.Is.~nI C.~,i Ffl (tJL~d8~A differential area in the circular fin is given as: dA = rdrdO The expression for circular fin surface area (times 2 for both sides and disregarding the edge area) taken over a complete traverse of the tube is given as: ACf = 2 rdrd0 = 2)r(r.2 -r i)Where: r. = the fin outside radius which is one half the fin height ri = the inside fin radius which is the tube outside radius Proto-Power Calc: 97-199 

==Attachment:==

K Rev: A Page 2 of 4 The spiral fin surface area (times 2 for both sides and disregarding the edge area) can be approximated by the expression:
A~r (-- --1 2ff(ro2- rif)The ratio of the two areas becomes: Act Ac = cosa Angle cc is approximated by the expression:
1-(fin separation) 1 tan a 4 r. 4r./, a = tan-'(1 where: X =fin pitch Substituting fin height into the expression yields the following:
a = tan-' 2 tan-' 1 As the angle a goes to zero, the spiral fin area approaches that of the circular fin. It can be seen that for very small fin separations (i.e., high fin pitch) the smaller the resulting angle a.For the case of the VY cooler fin geometry: a = tan- .48-)(1 = tan-' (0.033625) 
= 1.93o= = tn-' 21.48-7)(10))
Proto-Power Calc: 97-199 

==Attachment:==

K Rev: A Page 3 of 4 The resulting area ratio is then: Af cos(1.93 1.00057 This difference' is negligible and is bounded by the uncertainty in the analysis presented in Attachment J.Heat Transfer Coefficient The fin geometry affects the calculation of the outside heat transfer film coefficient (ho)for condensing modes of operation.
Vertical (circular) fins provide for better condensation heat transfer since the condensate falls away from the fins at a faster rate than if the fin were inclined (i.e., spiral geometry).
As shown in the area discussion above, the angular difference between the circular fin geometry and the spriral fin geometry for the VY coils with a fin pitch of 10 fins per inch is very small (i.e., <20).The angle of incline, therefore, is deemed to be sufficiently small as to make the difference between circular and spiral fin geometries negligible even for condensing modes of operation.
In other words, as far as condensation removal from the fin surfaces is concerned, the 10 fin per inch fin pitch of the VY coils results in a fin orientation that is sufficiently close to vertical as to make differences in condensation heat transfer predictions negligible.
Proto-Power Calc: 97-199 

==Attachment:==

K Rev: A Page 4 of 4 Attachment L to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

L Rev: A Page 1 of 5 COMED NUCLEAR DESIGN INFORMATION TRANSMITTAL
[ SAFETY-RELATED Originating Organization NOIT No.: LS-0847 fl NON-SAFETY-RELATED Section: SE Upgrade: 0 fl REGULATORY RELATED Company: CornEd Page 1 of 2 Station: LaSalle County Units: 1,2 Design Change Aulhority No NIA 

==Subject:==
Dimensional Verification for Tubing and Fins for Coolers 1(2)VY03A and 1(2)VYO4A.
To: P hilpot, Lloyd. Proto-Power A .,~'Miller, William J. System Engineer 7/6trS Prep~w.r po:&#xfd;ionr 1O -0 &#xfd;k01 Friedrich.
Rich Engineer-716/198 Rev .er Po =-iin a hall. Rich DE- Mech. Supv. 7/6/98 AOD, .ef Posit n 0olu 0.te Status of Information: 
[ Approved for Use [ Unverified Verefic-tion Method N/A D Engineering judgement Schedulo: Purpose of Issuance Transmittal of Dimensions to Proto-Power for Heat Exchanger analysis.Source of Information Walkdown performed on Ine 2vYO3A and 2VYO4A coolers performed byW. Miller (System Engineering) and R. Friedrick (Design Engineering) on 7/3/98.Description of Information The following measurements were obtained for the 2VY03A and 2VYO4A room coolers at the request of Proto Power Corporation.
These conditions were obtained at ambient conditions with the systems shutdown.
Attached is a copy of a sketch for each cooler that provides dimensions obtained in the field.The following information was obtained for the 2VY03A cooler Tube outside diameter 0.672 inches Fin Height: 1 452 inches Transvemse Tube Pitch, 1.410 Inches Effective Finned Tube Length: 108 inches (dimension is based on 111 inches from the inside of the furthest separated tube support"end" plates, which includeg three -1 inch tube suppon plates between the end plates)The following information was obtained for the 2VY04A cooler Distribution:
SEAG Szurnski.
Daniel R. -CornEd, SES-BOP Wilhclnmsen, Ckor~c R. -Con'Fd, SES-BOP JUL 06 '98 14:12 2502 PAGE. 03 Proto-Power Calc: 97-199 

==Attachment:==

L Rev: A Page 2 of 5 C I.,, A,. Uc I -.s &#xfd;c.L r ,. V .-''t .), , -, V ~ 0 <> &#xfd;-; 4 r. I A -.. R ,A A- I 5IL,4,J ,D% LAJji,.-7.3L.X l ; A- %-PJA'L'-. 
& AL. rL. I Q7J IT A& A A t,%...,SAFET'Y-REL.ATEE)
Originating Organization NDrT No.: LS-0847[]NON-SAFETY-RELATED Seto: S;E U Dgr-ade: 0[ REGULATORY RELATED Company: ComrEd Page 2 of 2 Tube diameter.
0.675 inres Fin Heght: 1.347 inces Transverse Tube Pitch: 1.370 inc:esi Ef1dlrve Finned Tube Length: ACS inches (dimenqion is b.ased on 108 irnches from the inside o! the lu.rlhett separated tube support.end' plates. which include three -1 inch tube suoport plates between the end plates).The first three measurement for each cooler were taken with a calibrated set of calipers (MMD Id No 7140. calibration due 2J99). The Effectve Finned Tube Length was taken with a metal tape measure. The uncertainites for these measurements are based on enginrerenn best estimates for the measurement techiniques used and are as stated in NOIT LS-,,35 dated 6/19/98. Each cooler appeared to have staggered rows of tubes. The transverse tube pitch was variable for the various individual Nris and the above dimension is typiol, ArtacnMent I contains two sheets wich sketches of the identical dimensions provide( above.NDIT LS-0647. Page 2 of 2 end. Attached -2 pages of sketch.I CornEd -Nuclear Operations Disivion I Proto-Power Calc: 97-199 

==Attachment:==

L Rev: A Page 3 of 5 
-- .- 1 -10 Va&#xfd;e &#xfd;oEV2..I SI I / I jF)-lq&#xfd;51,-~ -1, 67-6)o. 472" I , ~A~0 Proto-Power Calc: 97-199 

==Attachment:==

L Rev: A Page 4 of 5 1 1"" h M e CJ"A T~e_2 o -V2 VVY u t 1 K-/) I S9 ~ 'I Fla.3-0--, 4 .,-"-05" HII- 111414 I 111H Proto-Power Calc: 97-199 

==Attachment:==

L Rev: A Page 5 of 5 Attachment M to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 1 of 17 Sheet art4 Thermal Margin as a function of Tube-Side Fouling[1(2)VY03A at 72.5 gpm]50.00%40.00%-I-., 30.00%20.00%SI.....................................I.........................I..., 10.00%0 Ov 0 0 C0 0.00%g t'."-4 0.0000 0.0005 0.0010 0.0015 0.0020 0.0025 0.0030 0.0035 0.0040 Tube-Side Fouling Factor 4 Page 1 16:11:38 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f = 0.0000 07/06/98 Air Coil Heat Exchanger Input Parameters Flifii-Q-an ntity, Total Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperat Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side..... ..3-I ,0 0&-fii 150.00 OF 92.00 OF ure 108.80 OF 84.00 OF Tube-Side.180-. gpm 105.00 OF 117.70 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr ft.&deg;F)Fresh Water 0.002000 1,108,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 3 of 17 16:11:38 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f = 0.0000 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfin)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfm) 28,185.00 Tube Inlet Temp (IF) 100.00 Air Inlet Temp (IF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (IF) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 4 of 17 16:11:38 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000)
ComEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f =- 0.0000 07/06/98 K __ _Extrapolation Calculation Summary 11 11 Air-Side Mass Flow (Ibm/hr) 104,153.08 Inlet Temperature (OF) 148.00 Outlet Temperature (IF) 109.52 Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft'hr)
Skin Vise (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft-&deg;F)
Tube-Side 36,050.35 100.00 127.84 Tube-Side hi (BTU/hr'f 2 I'F)j Factor Air-Side ho (BTU/hr'ft 2.'F)Tube Wall Resistance (hr" ft 2_-F/BTU Overall Fouling (hr-ft 2-F/BTU)U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 0200000==
10,532.34 1,002,563 1,002,563 Extrapolation Calculation for Row 1(Dry)11 I.Air-Side Mass Flow (Ibm/hr) 104,153.08 Inlet Temperature (OF) 148.00 Outlet Temperature (OF) 142.64 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 145.32 Skin Temperature (OF) 129.02 Velocity *** 4,218.88 Reynold's Number 940**Prandtl Number 0.7254 Bulk Visc (Ibm/f-ihr) 0.0491 Skin Visc (lbm/ft-hr)
Density (lbm/fl 3) 0.0621 Cp (BTU/Ibm'&deg;F) 0.2402 K (BTU/hr'ft-&deg;F) 0.0163 Tube-Side 36,050.35 123.96 127.84 125.90 128.72 2.24 17,080 3.4236 1.2749 1.2430 61.6179 0.9989 0.3720 Tube-Side hi (BTU/hr-ft 2-&deg;F) 841.25 j Factor 0.0071 Air-Side ho (BTU/hr.ft 2"&deg;F) 8.91 Tube Wall Resistance (hr-ft2-&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr ft 2-&deg;F/BTU) 0.00200000 U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.89 1,053.23 19.24 139,692 0.9217 139,692** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 5 of 17*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 16:15:17 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f= 0.0010 07/06/98 Air Coil Heat Exchanger Input Parameters Fl--iid-Q-i-afi~
i-i,,fTt 6T ---Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Tempera Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Air-Side 3 16.0- acTm 150.00 OF 92.00 OF ture 108.80 OF 84.00 OF Tube-Side.. f80.00 gpm 105.00 OF 117.70 OF Fresh Water 0.001000 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hrfl.'F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F) 108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 6 of 17 16:15:17 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f= 0.0010 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acflm)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
(&deg;F)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfm) 28,125.00 Tube Inlet Temp ('F) 100.00 Air Inlet Temp ('F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ('F) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 7 of 17 16:15:17 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f= 0.0010 07/06/98 0 .-. .UI Extrapolation Caiculation summary II 11 Mass Flow (lbm/lhr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Vise (lbmr/fthr)
Density (lbm/ft 3)Cp (BTU/ibm-'F)
K (BTU/hr-ft--F)
Air-Side 103,931.36 148.00 110.72 Tube-Side 36,050.35 100.00 126.91 Tube-Side hi (BTU/hr-ft 2-&deg;F)j Factor Air-Side ho (BTU/hr'ft 2.'F)Tube Wall Resistance (hr-ft 2-&deg;F/BTU Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr ft2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 1967103==
10,532.34 969,164 969,164 Extrapolation Calculation for Row l(Dry)II I.Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/flhir)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr'ft 0-F)Air-Side 103,931.36 148.00 142.97 0.0203 0.0203 145.48 130.23 4,209.90 938*1 0.7253 0.0491 0.0621 0.2402 0.0163 Tube-Side 36,050.35 123.27 126.91 125.09 127.73 2.23 16,954 3.4514 1.2844 1.2540 61.6311 0.9989 0.3717 Tube-Side hi (BTU/hr-ftl-&deg;F) 837.78 j Factor 0.0071 Air-Side ho (BTU/hr-ft2-&deg;F) 8.90 Tube Wall Resistance (hr-ft 2 l-F/BTU 0.00029413 Overall Fouling (hr-.ft 2.oF/BTU) 0.01967103 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.14 1,053.23 20.24 130,852 0.9218 130,852** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 8 of 17*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 16:17:19 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f = 0.0020 07/06/98 Air Coil Heat Exchanger Input Parameters FletidrQyButbiy T,-emT-pF Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side-310-667.0 acfm 150.00 OF 92.00 OF 108.80 OF 84.00 OF Tube-Side....--. 1000-gpm 105.00 OF 117.70 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Fresh Water 0.002000 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-.F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F) 108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 9 of 17 16:17:19 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000) 7/6/98 CornEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f = 0.0020 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In ()F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out (*F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfim) 28,070.00 Tube Inlet Temp (&deg;F) 100.00 Air Inlet Temp ('F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ('F) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 10 of 17 16:17:19 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f = 0.0020 07/06/98 Extrapolation Calculation Summary 11 1.Air-Side Mass Flow (lbmnhr) 103,728.12 Inlet Temperature (IF) 148.00 Outlet Temperature 
(&deg;F) 111.85 Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr'ft'&deg;F)
Tube-Side 36,050.35 100.00 126.02 Tube-Side hi (BTU/hr'ft 2"&deg;F)j Factor Air-Side ho (BTU/hr ft 2_-F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 3734207==
10,532.34 938,124 938,124 w Extrapolation Calculation for Row l(Dry)II I. II Air-Side Mass Flow (lbm/hr) 103,728.12 Inlet Temperature 
(&deg;F) 148.00 Outlet Temperature (OF) 143.24 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 145.62 Skin Temperature (IF) 131.24 Velocity *** 4,201.67 Reynold's Number 936**Prandtl Number 0.7253 Bulk Visc (Ibm/ft-hr) 0.0491 Skin Visc (lbm/fl-hr)
Density (lbrn/fl3) 0.0621 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr.ft-&deg;F) 0.0163 Tube-Side 36,050.35 122.59 126.02 124.30 126.80 2.23 16,832 3.4788 1.2936 1.2646 61.6438 0.9988 0.3714 Tube-Side hi (BTU/hr.ft 2.&deg;F) 834.45 j Factor 0.0071 Air-Side ho (BTU/hr ft 2.&deg;F) 8.89 Tube Wall Resistance (hr-fV2.&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr-ft 2-&deg;F/BTU) 0.03734207 U Overall (BTU/hr ft2- F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTUihr)Heat to Condensate (BTU/hr)5.S3 1,053.23 21.19 123,422 0.9219 123,422** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 11 of 17*** Air Mass Velocity (Lbml/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 16:19:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f = 0.0030 07/06/98 Air Coil Heat Exchanger Input Parameters Flidiil--Qu-antity, TOTal Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Air-Side 3 1,0-6-6O0-&ffi1 150.00 OF 92.00 OF 108.80 OF 84.00 OF Tube-Side.-8-Y.0- gpm 105.00 OF 117.70 OF Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Fresh Water 0.003000 0.002000 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-.F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.IF) 108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 12 of 17 16:19:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f-- 0.0030 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfirn)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfin) 28,015.00 Tube Inlet Temp (IF) 100.00 Air Inlet Temp (IF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (IF) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 13 of 17 16:19:46 PROTO-IIX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f= 0.0030 07/06/98 R .Extrapolation Calculation Summary 11 11 Air-Side Mass Flow (lbm/hr) 103,524.88 Inlet Temperature (0 F) 148.00 Outlet Temperature (0 F) 112.97 Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft.hr)
Density (Ibm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr'fti'F)
Tube-Side 36,050.35 100.00 125.22 Tube-Side hi (BTU/hr'ft 2'0 F)j Factor Air-Side ho (BTU/hr'ft 2.'F)Tube Wall Resistance (hr- ft 2-&deg;F/BTU Overall Fouling (hr- ft 2.&deg;F/BTU)U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 5501310==
10,532.34 907,127 907,127 Extrapolation Calculation for Row 1 (Dry)II I.Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbml/fthr)
Density (Ibm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr'ft 0'F)Air-Side 103,524.88 148.00 143.49 0.0203 0.0203 145.75 132.13 4,193.44 934**0.7253 0.0491 0.0620 0.2402 0.0163 Tube-Side 36,050.35 121.98 125.22 123.60 125.97 2.23 16,723 3.5035 1.3021 1.2741 61.6551 0.9988 0.3712 Tube-Side hi (BTU/hl'ft 2 .F) 831.46 j Factor 0.0071 Air-Side ho (BTU/hrt'ft 2.'F) 8.88 Tube Wall Resistance (hr-ft2. F/BTU 0.00029413 Overall Fouling (hr-ft 2.F/BTU) 0.05501310 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.03 1,053.23 22.04 116,793 0.9220 116,793** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 14 of 17*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 16:23:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f = 0.0040 07/06/98 Air Coil Heat Exchanger Input Parameters Air-Side F l-i] 
-I3], 0U6Y&0-(fiii-Inlet Dry Bulb Temp 150.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature 108.80 OF Outlet Wet Bulb Temp 84.00 OF Outlet Relative Humidity %Tube-Side 1-80_00 gpmi 105.00 OF 117.70 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Fresh Water 0.004000 0.002000 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTUihr-ftl-F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-&deg;F) 108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 15 of 17 16:23:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/6/98 CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f= 0.0040 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfmn)Air Dry Bulb Temp In (OF)Air Dry Bulb Temp Out (OF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (OF)Wet Bulb Temp Out (OF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfm) 27,967.00 Tube Inlet Temp (OF) 100.00 Air Inlet Temp (&deg;F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (OF) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 16 of 17 16:23:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity:
Tube f= 0.0040 07/06/98 0 Extrapolation Calculation Summary II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (ibm/ft-hr)
Skin Vise (lbm/fi-hr)
Density (Ibm/fl 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hrft-0 F)Air-Side 103,347.50 148.00 113.96 Tube-Side 36,050.35 100.00 124.42 Tube-Side hi (BTU/hr ft 2 i'F)j Factor Air-Side ho (BTU/hr'ft2-&deg;F)
Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2 -F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTUihr)0.00029413

==0.0 7268414==
10,532.34 879,956 879,956 Extrapolation Calculation for Row l(Dry)II*1 Mass Flow (lbm/hr)Inlet Teqperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature 
('F)Velocity ***Reynold's Number Prandtl Number Bulk Vise (ibm/ft hr)Skin Vise (lbm/ft-hr)
Density (Ibm/fl 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 103,347.50 148.00 143.70 0.0203 0.0203 145.85 132.88 4,186.25 933**0.7253 0.0491 0.0620 0.2402 0.0163 Tube-Side 36,050.35 121.33 124.42 122.88 125.14 2.23 16,612 3.5291 1.3108 1.2838 61.6665 0.9988 0.3710 Tube-Side hi (BTU/hr-ft 2.&deg;F) 828.42 j Factor 0.0071 Air-Side ho (BTU/hr ft 2.-F) 8.87 Tube Wall Resistance (hr-ft 2_-F/BTU 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.07268414 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.62 1,053.23 22.87 111,227 0.9220 111,227** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-199 

==Attachment:==

M Rev: A Page 17 of 17*** Air Mass Velocity (Lbmi/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Attachment N to Proto-Power Calculation 97-199 Revision A Proto-Power Calc: 97-199 

==Attachment:==

N Rev: A Page 1 of 2 Proto-HX Model Database.40 Saved on attached disk as: Name: vy-03a.phx Size: 1,277,952 bytes Date: 7/6/98 Time: 6:21:52 pm Proto-Power Caic: 97-199 

==Attachment:==

N Rev: A Page 2 of 2 Commonwealth Edison Company NEP-12-02LA Nuclear Operations Division Revision 4 LASALLE CALCULATION SITE APPENDIX -LASALLE SITE EXHIBIT A (Page 4 of 4)CALCATION NO. q GE N REVISION NO.I I page 7 Commonwealth Edison Company NEP-12-02LA Nuclear Operations Division Revision 4 LASALLE CALCULATION SITE APPENDIX -LASALLE SITE CALCULATION NO. 97-199 ERev. B Project NO: 7 PAGE NO. f-1 ATTACHMENT P 1.0 PURPOSEIOBJECTIVE
.I The purpose of this revision is to pertbrm sensitivity computer calculations for the subject air cooler using reduced air inlet flow rates. This information may be used in the future for assessments of system performance in cases where air flow through this cooler may be slightly below the intended design values. Cases involving a 5% reduction and 10% reduction in inlet air volumetric flow will be calculated so that effect on heat transfer rate (Btulhr) can be assessed.
The existing computer model for the air cooling coil I (2)VY03A generated in Revision A of this calculation will be used for this revision.2.0 METHODOLOGY AND ACCEPTANCE CRITERIA 2.1 The methodology for this calculation involves the following activities:
* Utilize approved Proto-F1x software.
I (2)VY03A cooling coil model (generated in Revision A of this calculation), to calculate the heat exchanger performance with reductions in inlet air volumetric flow of 5% and 10% (two cases).2.2 The acceptance criteria for this calculation is the following:
* There is no specific acceptance criteria as the purpose of this calculation is merely to predict additional data points for heat rejection capability based on reduced air inlet flow values.3.0 ASSUMPTIONS 3.1 There are no assumptions within this calculation.
Commonwealth Edison Company Nuclear Operations Division NEP-12-02LA Revision 4 LASALLE CALCULATION SITE APPENDIX-LASALLE SITE r CALCULATION NO. 97-199 I Rev. B I Project No: I PAGE NO.ATTACHM ENT P 4.0 DESIGN INPUT The design inputs to this calculation are the tblloing: 4.1 Proto-Mx.
Thermal Performance model for the LaSalle 1(2)VY03A cooling coil model, an approved calculational computer model generated in Revision A of this calculation.
4.2 Verification of PC Installation of Proto-l x Version 3.00 an approved Computer Program (Reference 5.2).

==5.0 REFERENCES==

5.1 Proto-Hx.
Version 3.00 and User Documentation 
-1996 5.2 Calculation L-002210.
Rev. 0. dated 11-18-98.
Verification of PC Installation of Proto-4x Version 3.00. (CoinEd PC #507943)
Commonwealth Edison Company NEP-12-02LA Nuclear Operations Division Revision 4 LASALLE CALCULATION SITE APPENDIX -LASALLE SITE CALCULATION NO. 97-199 Rev. B 7 Project NO: =PAGE NO./ATTACHMENT P 6.0 CALCULATIONS The existing Proto-Hx Model for this cooling coil. has adjusted design fouling factors of. Air Side=O.002 and Tube Side=O.002.
this is acceptable and conservative for use in this sensitivity study.since the design values for these parameters are Air Side-=0 and Tube Side=0.00l15 (per Table 2 of this calculation).
The cooling water flow rate used is 72.5 gpm, which is a limiting value, per Section 7.3 of this calculation.
Additional computer runs were made to evaluate cases of reduced air flow entering the cooler as follows: a) Benchmark case (Run No. 1) using the above indicated fouling factors and the tube side flow rate=72.5 gpm. Air flow into the cooler is 28,070 aclin (identical to fouling sensitivity case in Attachment M). The other input extrapolation data, e.g. tube inlet temperature, air inlet temperature, relative humidity, and atmospheric pressure are not altered. This computer run yielded identical results to the referenced Attachment M case indicating the model is working acceptably.
Since the VY fan is on the discharge side of the cooling coil, it is desirable to calculate the volumetric air flow on the discharge side of the coil. This is done by taking the exiting air-side mass flow given by Proto-Hx (from Row 10 of the coil), using the outlet density given by Proto-Fix convert to a volumetric flow (acfm).103.728 (ibm/hr) / 0.0655 (lbm/ft')
x 60 (min./hr) 
= 26.394 acfm. say 26.400 acfm b) 5% reduction in inlet air flow (Run No. 2): Inlet air flow = 28.070 acfrn -5% = 26.666 acfm.This is the only input value changed for this case. The coil outlet flow is calculated as follows: 98,540 (lbm/hr) / 0.0656 (lbm/ft3) x 60 (min./hr) 
= 25,036 acfm. say 25.000 acfm c) 10% reduction in inlet air flow (Run No. 3): Inlet air flow = 28,070 acfm -10% = 25.263 acfm. This is the only input value changed for this case.93.355 (lbm/hr) / 0.0657 (Ibm/ftl) x 60 (min./hr) 
= 23.682 acfm. say 23,700 acfm Commonwealth Edison Company Nuclear Operations Division NEP-12-02LA Revision 4 LASALLE CALCULATION SITE APPENDIX -LASALLE SITE CALCULATION NO. 97-199 I Rev. B I Project No: I PAGE NO.'4l ATTACHMENT P 7.0 

==SUMMARY==
AND CONCLUSIONS Following is a summary of the results based on the input inlet air flow values showing the predicted heat rejection:
Air Flow Reduction Inlet Air Flow base 28.070 acfm 5% 26.666 acfm 10% 25.263 acfm Outlet Air Flow 26,400 acfm 25,000 acfm 23.700 acfm Total [feat rransferred 938.124 Btuihr 909.799 Btu/hr 878.267 Btu/hr Based on Table I of this calculation, the required heat transfer rate for this cooler is 722.217 Btu/hr.As expected, the reduction in air inlet flow reduces the amount of heat transfer, however the calculated values are still well above the required heat transfer rate noted.
17:35:40 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Benchmark Case w/Service f-0.002 Ai-rCoi /it -/Air Coil Heat Exchanger Input Parameters 02/18/99 11 11 Fi-dnQetDffryt-l, Temtpl--Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Air-Side 3- 0660-a0_ciii_-
150.00 OF 92.00 OF 108.80 OF 84.00 OF.%....- --Tube-Side........1807.00 ii 105.00 OF 117.70 OF Fresh Water 0.002000 0.002000 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hrIft.&deg;F)
Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Calc #97-199, Rev. B Attachment P PageP5 17:35:40 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371) 02/18/1999 CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils FA Benchmark Case w/Service f=0.002 S&A/ A, q.Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfm) 28,070.00 Tube Inlet Temp ('F) 100.00 Air Inlet Temp ('F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ('F) 0.00 Atmospheric Pressure 14.315 Calc #97-199, Rev. B Attachment P PageP6 17:35:40 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Benchmark Case w/Service f=0.002 Extrapolation Calculation Summary 02/18/99 0 Air-Side Mass Flow (lbm/hr) 103,728.12 Inlet Temperature 
(*F) 148.00 Outlet Temperature 
(&deg;F) 111.85 Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (7F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fti-hr)
Skin Visc (Ibm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr'ft-&deg;F)
Tube-Side 36,050.35 100.00 126.02 Tube-Side hi (BTU/hr-ft 2-'F)j Factor Air-Side ho (BTU/hrft 2 0.&deg;F)Tube Wall Resistance (hr-ftl. F/BTU 0.00029413 Overall Fouling (hr-ftP.&deg;F/BTU) 

==0.0 3734207==
U Overall (BTU/hr-ft2-'F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)10,532.34 938,124 938,124 44~Extrapolation Calculation for Row l(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ftrhr)
Air-Side 103,728.12 148.00 143.24 0.0203 0.0203 145.62 131.24 4,201.67 936**0.7253 0.0491 Tube-Side 36,050.35 122.59 126.02 124.30 126.80 2.23 16,832 3.4788 1.2936 1.2646 Tube-Side hi (BTU/hr-ft2-&deg;F) 834.45 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2'.F) 8.89 Tube Wall Resistance (hr-ft 2 l-F/BTU 0.00029413 Overall Fouling (hr- ft2. F/BTU) 0.03734207 U Overall (BTU/hr-ft 2.'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.53 1,053.23 21.19 123,422 0.9219 123,422 Density (Ibm/ft) 0.0621 61.6438 Cp (BTU/Ibm-&deg;F) 0.2402 0.9988 K (BTU/hr-ft-&deg;F) 0.0163 0.3714** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP7*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:35:40 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Benchmark Case w/Service f=-0.002 k , .02/18/99 Extrapolation Calculation for Row 2(Dry)II Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 103,728.12 143.24 138.79 0.0203 0.0203 141.02 127.51 4,201.67 942**0.7258 0.0488 0.0625 0.2402 0.0162 Tube-Side 36,050.35 119.38 122.59 120.98 123.36 2.23 16,322 3.5979 1.3341 1.3049 61.6964 0.9988 0.3704 Tube-Side hi (BTU/hr.ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft2.&deg;F)
Tube Wall Resistance (hr-ft 2-&deg;F/BTU Overall Fouling (hr ft 2-&deg;F/BTU)U Overall (BTU/hr-ft 2.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)820.85 0.0071 8.87 0.00029413

==0.0 3734207==
5.51 1,053.23 19.91 115,582 0.9220 115,582** Reynolds Number Outside Range of Equation Applicability k.&#xfd;W, II Extrapolation Calculation for Row 3(Dry)*II Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftlhr)
Skin Visc (lbm/ft-hr)
Density (ibm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 103,728.12 138.79 134.62 0.0203 0.0203 136.70 124.03 4,201.67 947**0.7261 0.0485 0.0630 0.2402 0.0161 Tube-Side 36,050.35 116.37 119.38 117.87 120.14 2.23 15,849 3.7157 1.3739 1.3447 61.7443 0.9988 0.3693 Tube-Side hi (BTU/hr-ftl 2.F) 808.06 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2.F) 8.85 Tube Wall Resistance (hr-ft 2-F/BTU 0.00029413 Overall Fouling (hr-ftr 2.F/BTU) 0.03734207 U Overall (BTW/hr-ft 2.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.49 1,053.23 18.72 108,279 0.9222 108,279** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:35:40 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Benchmark Case w/Service f=0.002 /it 02/18/99 ii.Extrapolation Calculation for Row 4(Dry)II Mass Flow (Ibm/br)Inlet Temperature 
(&deg;F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft')Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 103,728.12 134.62 130.71 0.0203 0.0203 132.66 120.76 4,201.67 952**0.7265 0.0483 0.0634 0.2402 0.0160 Tube-Side 36,050.35 113.55 116.37 114.96 117.11 2.23 15,410 3.8319 1.4130 1.3839 61.7881 0.9988 0.3683 Tube-Side hi (BTU/hr-ft1 2.F) 796.02 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.83 Tube Wall Resistance (hr-ft 2 0-F/BTU 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.03734207 U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.48 1,053.23 17.59 101,473 0.9224 101,473** Reynolds Number Outside Range of Equation Applicability II Extrapolation Calculation for Row 5(Dry)iI Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ftihr)
Density (Ibm/fl 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft--F)
Air-Side 103,728.12 130.71 127.04 0.0203 0.0203 128.87 117.70 4,201.67 957**0.7268 0.0480 0.0638 0.2402 0.0159 Tube-Side 36,050.35 110.91 113.55 112.23 114.28 2.23 15,003 3.9463 1.4514 1.4224 61.8281 0.9988 0.3673 Tube-Side hi (BTU/hr'ft 2-&deg;F) 784.69 j Factor 0.0071 Air-Side ho (BTU/hr ft 2.F) 8.81 Tube Wall Resistance (hr-ft 2-F/BTU 0.00029413 Overall Fouling (hr-ft 2-F/BTU) 0.03734207 U Overall (BTU/hr-ft 2.IF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.46 1,053.23 16.54 95,126 0.9225 95,126** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP9*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:35:40 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Benchmark Case w/Service f=0.002 02/18/99 Extrapolation Calculation for Row 6(Dry)II I.Air-Side Tube-Side Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ftrhr)
Density (Ibm/ft 3)Cp (BTU/Ibm-OF)
K (BTU/hr-ft.'F) 103,728.12 127.04 123.60 0.0203 0.0203 125.32 114.82 4,201.67 961" 0.7270 0.0478 0.0642 0.2402 0.0158 36,050.35 108.43 110.91 109.67 111.62 2.23 14,624 4.0586 1.4889 1.4602 61.8646 0.9988 0.3664 n Applicability Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft 2.F)Tube Wall Resistance (hr-ft 2-F/BTU Overall Fouling (hr-ft 2 l-F/BTU)U Overall (BTU/hr-ft 2 7-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)774.02 0.0070 8.80 0.00029413

==0.0 3734207==
5.44 1,053.23 15.56 89,203 0.9226 89,203** Reynolds Number Outside Range of Equatio-I1I Extrapolation Calculation for Row 7(Dry)II Air-Side Mass Flow (Ibm/hr) 103,728.12 Inlet Temperature (OF) 123.60 Outlet Temperature (OF) 120.38 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 121.99 Skin Temperature (OF) 112.13 Velocity *** 4,201.67 Reynold's Number 965*" Prandtl Number 0.7273 Bulk Visc (lbm/ft-hr) 0.0476 Skin Visc (lbm/ft-hr)
Density (lbm/ft 3) 0.0645 Cp (BTU/Ibm-&deg;F) 0.2402 K (BTU/hr-fti.F) 0.0157 Tube-Side 36,050.35 106.11 108.43 107.27 109.12 2.23 14,272 4.1689 1.5256 1.4972 61.8981 0.9989 0.3655 Tube-Side hi (BTU/hr-ft 2-F) 763.98 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.78 Tube Wall Resistance (hr-ft2-&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr-ft 2.&deg;F/BTU) 0.03734207 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.43 1,053.23 14.63 83,674 0.9227 83,674** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PagePl 10 Air Mass Velocity (Lbm/hr-ft 2). Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:35:40 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Benchmark Case w/Service f=0.002 A / I 02/18/99 Extrapolation Calculation for Row 8(Dry)II I.Mass Flow (ibm/br)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (lbm/ft-hr)
Density (lbM/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 103,728.12 120.38 117.35 0.0203 0.0203 118.86 109.60 4,201.67 969**0.7275 0.0474 0.0649 0.2402 0.0157 Tube-Side 36,050.35 103.93 106.11 105.02 106.78 2.22 13,945 4.2767 1.5615 1.5334 61.9287 0.9989 0.3647 Tube-Side hi (BTU/hr-fV.&deg;F) 754.53 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2.0 F) 8.77 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr.ft 2.&deg;F/BTU) 0.03734207 U Overall (BTU/hr-ft 2 l-F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.42 1,053.23 13.77 78,509 0.9229 78,509** Reynolds Number Outside Range of Equation Applicability IWW,_1I Extrapolation Calculation for Row 9(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm.0 F)K (BTU/hr-ft.
0 F)Air-Side 103,728.12 117.35 114.51 0.0203 0.0203 115.93 107.22 4,201.67 973**0.7277 0.0472 0.0652 0.2402 0.0156 Tube-Side 36,050.35 101.88 103.93 102.91 104.57 2.22 13,640 4.3821 1.5964 1.5687 61.9568 0.9990 0.3639 Tube-Side hi (BTU/hr-ft 2-F)j Factor Air-Side ho (BTU/hr-ft 2-F)Tube Wall Resistance (hr-ft 2.F/BTU Overall Fouling (hr-ft 2.F/BTU)U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)745.64 0.0070 8.75 0.00029413

==0.0 3734207==
5.40 1,053.23 12.95 73,683 0.9230 73,683** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PagePl 1*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:35:40 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils Benchmark Case w/Service f--0.002 Extrapolation Calculation for Row 10(Dry)02/18/99 I I.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp ("F)Skin Temperature 
("F)Velocity ***Air-Side 114.51 111.85 0.0203 0.0203 113.18 104.99 4,201.67 Tube-Side 36,050.35 99.96 101.88 100.92 102.51 2.22 Tube-Side hi (BTU/hr ft 2.&deg;F) 737.27 j Factor 0.0070 Air-Side ho (BTU/hr-ft 2".F) 8.74 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hrvfi 2-&deg;F/BTU) 0.03734207 Reynold's Number 977** 13,356 Prandtl Number 0.7278 4.4848 Bulk Visc (lbm/ftihr) 0.0470 1.6303 Skin Visc (lbm/ftbhr) 1.6031 Density (Ibm/ft 3) -0.06555 61.9826 Cp (BTU/Ibm.&deg;F) 
: 0. 402 0.9990 K (BTU/hr'ft'&deg;F) 0.0155 0.3631** Reynolds Number Outside Range of Equation Applicability U Overall (BTU/hr-ft 2-IF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.39 1,053.23 12.19 69,171 0.9231 69,171 Calc #97-199, Rev. B Attachment P PagePl 2*** Air Mass Velocity (Lbm/hr-ft2), Tube Fluid Velocity (ftlsec);
Air Density at Inlet T, Other Properties at Average T 17:12:06 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Data Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils 5% Reduction in Air Inlet Vol. Flow 02/18/99 Air Coil Heat Exchanger Input Parameters FTurf-Qu tnt, t aF T --aF Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Air-Side 3F, OO. fi.150.00 OF 92.00 OF 108.80 OF 84.00 OF Tube-Side...... .. -gpm 105.00 OF 117.70 OF Fresh Water 0.002000 0.002000 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft 0.F)Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.
0 F)108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Calc #97-199, Rev. B Attachment P PageP 13 17:12:06 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371) 02/18/1999 CornEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils 5% Reduction in Air Inlet Vol. Flow Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (OF)Air Dry Bulb Temp Out (OF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (OF)Wet Bulb Temp Out (&deg;F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfm) 26,666.00 Tube Inlet Temp (OF) 100.00 Air Inlet Temp (&deg;F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (&deg;F) 0.00 Atmospheric Pressure 14.315 Calc #97-199, Rev. B Attachment P PageP 14 17:12:06 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1 (2)VY03A -CSCS Equipment Area Cooling Coils 5% Reduction in Air Inlet Vol. Flow 02/18/99 Extrapolation Calculation Summary II Air-Side Mass Flow (Ibm/hr) 98,539.87 Inlet Temperature (OF) 148.00 Outlet Temperature 
(&deg;F) 111.09 Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (lbm/ftihr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr-ft-&deg;F)
Tube-Side 36,050.35 100.00 125.22 Tube-Side hi (BTU/hr-ft2.
F)j Factor Air-Side ho (BTU/hr-ft2.&deg;F)
Tube Wall Resistance (hr-ft 2.F/BTU 0.00029413 Overall Fouling (hr-ft 2.F/BTU) 0.03734207 U Overall (BTU/hr-ft 2.F)Effective Area (f1 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)10,532.34 909,799 -909,799 Extrapolation Calculation for Row l(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft--F)
Air-Side 98,539.87 148.00 142.95 0.0203 0.0203 145.47 130.50 3,991.51 890**0.7253 0.0491 0.0621 0.2402 0.0163 Tube-Side 36,050.35 121.76 125.22 123.49 126.02 2.23 16,706 3.5073 1.3034 1.2735 61.6568 0.9988 0.3712 Tube-Side hi (BTU/hr-ft 2.F) 831.19 j Factor 0.0072 Air-Side ho (BTU/hr-ft 2 l-F) 8.59 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-F/BTU) 0.03734207 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.41 1,053.23 21.85 124,529 0.9242 124,529** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PagePl5*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:12:06 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1 (2)VY03A -CSCS Equipment Area Cooling Coils 5% Reduction in Air Inlet Vol. Flow A,1li.-02/18/99 Extrapolation Calculation for Row 2(Dry)II I, .Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (ibm/fl 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-PF)
Air-Side 98,539.87 142.95 138.27 0.0203 0.0203 140.61 126.69 3,991.51 895**0.7258 0.0488 0.0626 0.2402 0.0161 Tube-Side 36,050.35 118.55 121.76 120.16 122.54 2.23 16,196 3.6286 1.3445 1.3148 61.7092 0.9988 0.3701 Tube-Side hi (BTU/hr-ft 2.&deg;F) 817.50 j Factor 0.0072 Air-Side ho (BTU/hr ft 2"&deg;F) 8.57 Tube Wall Resistance (hr-ft 2-F/BTU 0.00029413 Overall Fouling (hrft2. 'F/BTU) 0.03734207 U Overall (BTU/hr-ft2.
F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTUihr)5.39 1,053.23 20.32 115,433 0.9244 115,433** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)Ai Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 98,539.87 138.27 133.92 0.0203 0.0203 136.09 123.16 3,991.51 900*4 0.7262 0.0485 0.0631 0.2402 0.0160 Tube-Side 36,050.35 115.58 118.55 117.07 119.31 2.23 15,727 3.7473 1.3845 1.3552 61.7566 0.9988 0.3690 Tube-Side hi (BTU/hr-ft 2.0 F) 804.75 j Factor 0.0072 Air-Side ho (BTU/hr-ft 2"&deg;F) 8.55 Tube Wall Resistance (hr-ft 2.&deg;F[BTU 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.03734207 U Overall (BTU/hr.ft 2.&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.37 1,053.23 18.91 107,047 0.9246 107,047** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PagePl 6*** Air Mass Velocity (Lbm/hr-f 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:12:06 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils 5% Reduction in Air Inlet Vol. Flow 02/18/99 Extrapolation Calculation for Row 4(Dry)HI Air-Side Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr-ft--F) 98,539.87 133.92 129.89 0.0203 0.0203 131.91 119.89 3,991.51 905**0.7265 0.0482 Tube-Side 36,050.35 112.82 115.58 Tube-Side hi (BTU/hr'ft 2-F) 792.86 j Factor 0.0072 Air-Side ho (BTU/hr.ft 2-&deg;F) 8.53 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-F/BTU) 0.03734207 114.20 116.32 2.23 15,297 3.8631 1.4235 1.3946 61.7993 0.9988 0.3680 U Overall (BTU/hr.ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.36 1,053.23 17.60 99,311 0.9247 99,311 0.0635 0.2402 0.0160** Reynolds Number Outside Range of Equation Applicability V.Extrapolation Calculation for Row 5(Dry)II Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (lbm/ft-hr)
Density (ibm/fl 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 98,539.87 129.89 126.15 0.0203 0.0203 128.02 116.85 3,991.51 910**0.7268 0.0480 0.0639 0.2402 0.0159 Tube-Side 36,050.35 110.26 112.82 111.54 113.53 2.23 14,901 3.9760 1.4613 1.4328 61.8380 0.9988 0.3671 Tube-Side hi (BTU/hr-ft 2.&deg;F) 781.79 j Factor 0.0072 Air-Side ho (BTU/hr-ft 2.IF) 8.52 Tube Wall Resistance (hr-ft 2-F/BTU 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.03734207 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.34 1,053.23 16.38 92,171 0.9248 92,171** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP 17*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T I17:12:06 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1 (2)VY03A -CSCS Equipment Area Cooling Coils 5% Reduction in Air Inlet Vol. Flow 41' /4.02/18/99 Extrapolation Calculation for Row 6(Dry)II Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbmr/fthr)
Skin Visc (Ibrn/fthr)
Density (lbm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 98,539.87 126.15 122.68 0.0203 0.0203 124.42 114.02 3,991.51 914**0.7271 0.0478 0.0643 0.2402 0.0158 Tube-Side 36,050.35 107.89 110.26 109.07 110.95 2.23 14,537 4.0856 1.4979 1.4700 61.8730 0.9988 0.3662 Tube-Side hi (BTU/hr-ft 2.&deg;F) 771.48 j Factor 0.0072 Air-Side ho (BTU/hr-ft2.&deg;F) 8.50 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.03734207 U Overall (f3TU/hr-ft 2-IF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.33 1,053.23 15.25 85,575 0.9250 85,575** Reynolds Number Outside Range of Equation Applicability
...... ...._1L_Extrapolation Calculation for Row 7(Dry)II 11 II Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft.hr)
Skin Visc (lbm/ftrhr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 98,539.87 122.68 119.46 0.0203 0.0203 121.07 111.40 3,991.51 918**0.7273 0.0476 0.0646 0.2402 0.0157 Tube-Side 36,050.35 105.68 107.89 Tube-Side hi (BTU/hr-ft2.&deg;F) 761.86 j Factor 0.0072 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.49 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2.&deg; F/BTU) 0.03734207 106.78 108.54 2.22 14,201 4.1919 1.5333 1.5060 61.9048 0.9989 0.3654 U Overall (BTU/hr-ft2.
0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.31 1,053.23 14.20 79,478 0.9251 79,478** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP 18*** Air Mass Velocity (Lbm/hr-fi 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 1 7:12:06 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1 (2)VY03A -CSCS Equipment Area Cooling Coils 5% Reduction in Air Inlet Vol. Flow f-(~. IL '02/18/99 a Extrapolation Calculation for Row 8(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ftrhr)
Skin Visc (ibm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 98,539.87 119.46 116.46 0.0203 0.0203 117.96 108.96 3,991.51 922**0.7275 0.0474 0.0650 0.2402 0.0156 Tube-Side 36,050.35 103.63 105.68 104.65 106.31 2.22 13,892 4.2946 1.5674 1.5408 61.9336 0.9989 0.3646 Tube-Side hi (BTU/hr-ft 2.'F) 752.91 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2 l-F) 8.47 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.03734207 U Overall (BTU/hr.ft2.IF)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.30 1,053.23 13.23 73,840 0.9252 73,840** Reynolds Number Outside Range of Equation Applicability Iz"1l Extrapolation Calculation for Row 9(Dry)II I. *1 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 98,539.87 116.46 113.68 0.0203 0.0203 115.07 106.70 3,991.51 926**0.7277 0.0472 0.0653 0.2402 0.0156 Tube-Side 36,050.35 101.72 103.63 102.68 104.23 2.22 13,607 4.3938 1.6002 1.5743 61.9598 0.9990 0.3638 Tube-Side hi (BTU/hr-ft 2 -F) 744.56 j Factor 0.0071 Air-Side ho (BTU/hr.ft 2 -F) 8.46 Tube Wall Resistance (hr-ft2-&deg;F/BTU 

==0.0 0029413==
Overall Fouling (hr-ftl 2.F/BTU) 0.03734207 U Overall (BTU/hr-ft 2-IF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.29 1,053.23 12.32 68,623 0.9253 68,623** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP19*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (W/sec); Air Density at Inlet T, Other Properties at Average T I 7:12:06 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils 5% Reduction in Air Inlet Vol. Flow Extrapolation Calculation for Row 10(Dry)02/18/99.1 d II 1.Air-Side Tube-Side Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Visc (lbmr/fthr)
Density (Ibm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
(9&539.87,)
113.68 111.09 0.0203 0.0203 112.39 104.59 3,991.51 929**0.7279 0.0470 0.2402 0.0155 36,050.35 99.95 101.72 100.84 102.30 2.22 13,344 4.4893 1.6318 1.6066 61.9837 0.9990 0.3631 Tube-Side hi (BTU/hrft 2.'F) 736.78 j Factor 0.0071 Air-Side ho (BTU/hr-ft 2-'F) 8.45 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.03734207 U Overall (BTU/hr-ft2.'F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.28 1,053.23 11.48 63,792 0.9254 63,792** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP20*** Air Mass Velocity (Lbm/hr-f 2). Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:13:08 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Data Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils 10% Reduction in Air Inlet Vol. Flow 02/18/99'al/44. g Air Coil Heat Exchanger Input Parameters Air-Side FluH-d-QuatiW,YotFa 31,066Y00-a-ffin-Inlet Dry Bulb Temp 150.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature 108.80 OF Outlet Wet Bulb Temp 84.00 OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Tube-Side 1-8O70.gpm 105.00 OF 117.70 OF Fresh Water 0.002000 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 1,108,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY03A j = EXP[-2.5939 
+ -0.3438
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F) 108.000 10.000 128.000 0.0120 0.0120 1.452 2 10 24.00 24.00 0.5270 0.6250 1.400 1.410 1.000 225.00 Calc #97-199, Rev. B Attachment P PageP21 17:13:08 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371) 02/18/1999 ComEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils 10% Reduction in Air Inlet Vol. Flow Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (OF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm) 72.50 Air Flow (acfm) 25,263.00 Tube Inlet Temp (IF) 100.00 Air Inlet Temp (IF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (&deg;F) 0.00 Atmospheric Pressure 14.315 Calc #97-199, Rev. B Attachment P PageP22 17:'13:08 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: l(2)VY03A 
-CSCS Equipment Area Cooling Coils 10% Reduction in Air Inlet Vol. Flow 02/18/99 rwr~Extrapolation Calculation Summary I!Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp ('F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ftvhr)
Density (lbm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr4ft-&deg;F)
Air-Side 93,355.31 148.00 110.39 Tube-Side 36,050.35 100.00 124.42 Tube-Side hi (BTU/hr-ft2-&deg;F) j Factor Air-Side ho (BTU/hr ft 2.'F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr-ft 2-&deg;F/BTU)U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00029413

==0.0 3734207==
10,532.34 878,267<-878,267 Extrapolation Calculation for Row l(Dry)II Mass Flow (lbm/hr)Inlet Temperature (7F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-0 F)K (BTU/hr-ft.&deg;F)
Air-Side 93,355.31 148.00 142.64 0.0203 0.0203 145.32 129.74 3,781.50 843**0.7254 0.0491 0.0621 0.2402 0.0163 Tube-Side 36,050.35 120.94 124.42 122.68 125.24 2.23 16,582 3.5361 1.3131 1.2826 61.6696 0.9988 0.3709 Tube-Side hi (BTU/hr-ft 2-'F)j Factor Air-Side ho (BTU/hr-ft 2.'F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr-ft2.&deg;F/BTU)
U Overall (BTU/hr-ft 2-'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)827.94 0.0074 8.29 0.00029413

==0.0 3734207==
5.29 1,053.23 22.49 125,278 0.9266 125,278** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP23 Air Mass Velocity (Lbm/hrft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:13:08 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1 (2)VY03A -CSCS Equipment Area Cooling Coils 10% Reduction in Air Inlet Vol. Flow~I41j//02/18/99 0 -Extrapolation Calculation for Row 2(Dry)II Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 93,355.31 142.64 137.72 0.0203 0.0203 140.18 125.86 3,781.50 848**0.7258 0.0488 0.0626 0.2402 0.0161 Tube-Side 36,050.35 117.75 120.94 119.35 121.73 2.23 16,073 3.6591 1.3548 1.3248 61.7218 0.9988 0.3698 Tube-Side hi (BTU/hr-ft 2.'F)j Factor Air-Side ho (BTU/hr'ft 2-0 F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr-ft 2'-F/BTU)U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)814.20 0.0074 8.27 0.00029413

==0.0 3734207==
5.27 1,053.23 20.70 114,868 0.9268 114,868** Reynolds Number Outside Range of Equation Applicability II Extrapolation Calculation for Row 3(Dry)II *Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft.hr)
Skin Visc (Ibm/ft-hr)
Density (lbm/fl 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 93,355.31 137.72 133.20 0.0203 0.0203 135.46 122.30 3,781.50 854**0.7262 0.0485 0.0631 0.2402 0.0160 Tube-Side 36,050.35 114.83 117.75 116.29 118.51 2.23 15,610 3.7782 1.3949 1.3656 61.7683 0.9988 0.3688 Tube-Side hi (BTU/hr'ft 2"&deg;F)j Factor Air-Side ho (BTU/hr-ftl 2.F)Tube Wall Resistance (hr-ftl 2-F/BTU Overall Fouling (hr-ftZ .F/BTU)U Overall (BTU/hr-ft 2.OF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)801.53 0.0073 8.25 0.00029413

==0.0 3734207==
5.25 1,053.23 19.05 105,379 0.9270 105,379** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP24*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:13:08 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils 10% Reduction in Air Inlet Vol. Flow I4a, tA.10 02/18/99-~ -.. ~. ... --' II Extrapolation Calculation tor How 4(DJry)II I, Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbml/fthr)
Skin Visc (lbm/ft-hr)
Density (ibm/ft 3)Cp (BTU/Ibm 0'F)K (BTU/hr-ft-'F)
Air-Side 93,355.31 133.20 129.06 0.0203 0.0203 131.13 119.03 3,781.50 858" 0.7266 0.0482 0.0636 0.2402 0.0159 Tube-Side 36,050.35 112.14 114.83 113.48 115.55 2.23 15,189 3.8931 1.4336 1.4049 61.8099 0.9988 0.3678 Tube-Side hi (BTU/hr'ft 2 0-F) 789.86 j Factor 0.0073 Air-Side ho (BTU/hr-ft2 -F) 8.23 Tube Wall Resistance (hr-ft 2 0-F/BTU 0.00029413 Overall Fouling (hr-ft 2.F/BTU) 0.03734207 U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.24 1,053.23 17.54 96,720 0.9271 96,720** Reynolds Number Outside Range of Equation Applicability
~rir --II Extrapolation Calculation for Row 5(Dry)II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft'&deg;F)
Air-Side 93,355.31 129.06 125.26 0.0203 0.0203 127.16 116.02 3,781.50 863*4 0.7269 0.0479 0.0640 0.2402 0.0158 Tube-Side 36,050.35 109.67 112.14 110.91 112.83 2.23 14,807 4.0038 1.4706 1.4428 61.8471 0.9988 0.3669 Tube-Side hi (BTU/hr-ft 2 0-F) 779.10 j Factor 0.0073 Air-Side ho (BTU/hr'ft 2-&deg;F) 8.22 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00029413 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.03734207 U Overall (BTU/hr'ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.22 1,053.23 16.15 88,814 0.9272 88,814** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP25*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 17:13:08 PROTO-HX 3.00 by Proto-Power Corporation (SN4663-7371)
CornEd -- LaSalle Calculation Report for: 1 (2)VY03A -CSCS Equipment Area Cooling Coils 10% Reduction in Air Inlet Vol. Flow 02/18/99 Extrapolation Calculation for Row 6(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ftihr)
Density (Ibm/fi 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 93,355.31 125.26 121.77 0.0203 0.0203 123.51 113.26 3,781.50 867**0.7272 0.0477 0.0644 0.2402 0.0158 Tube-Side 36,050.35 107.41 109.67 108.54 110.33 2.23 14,458 4.1100 1.5060 1.4791 61.8805 0.9989 0.3660 Tube-Side hi (BTU/hr-ft 2'-F)j Factor Air-Side ho (BTU/hr-ft 2"&deg;F)Tube Wall Resistance (hr-ft2-&deg;F/BTU Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)769.18 0.0073 8.20 0.00029413

==0.0 3734207==
5.21 1,053.23 14.88 81,588 0.9274 81,588** Reynolds Number Outside Range of Equation Applicability-II Extrapolation Calculation for Row 7(Dry)--II Mass Flow (lbmlhr)Inlet Temperature (1F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Air-Side 93,355.31 121.77 118.56 0.0203 0.0203 120.16 110.73 3,781.50 871*0.7274 0.0475 Tube-Side 36,050.35 105.33 107.41 106.37 108.03 2.22 14,140 4.2117 1.5399 1.5139 Tube-Side hi (BTU/hr-ft 2.F)j Factor Air-Side ho (BTU/hr-ft 2.0 F)Tube Wall Resistance (hr-ft 2-'F/BTU Overall Fouling (hr-ft2.&deg;F/BTU)
U Overall (BTU/hr-ft2.
F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)760.03 0.0073 8.19 0.00029413

==0.0 3734207==
5.19 1,053.23 13.71 74,979 0.9275 74,979 Density (Ibm/ft 3) 0.0647 61.9105 Cp (BTU/lbm-&deg;F) 0.2402 0.9989 K (BTU/hr-fti.F) 0.0157 0.3652** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP26*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:13:08 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: I(2)VY03A 
-CSCS Equipment Area Cooling Coils 10% Reduction in Air Inlet Vol. Flow d 02/18/99 Extrapolation Calculation for Row 8(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbmr/f-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-'F)
K (BTU/hr-fr'&deg;F)
Air-Side 93,355.31 118.56 115.60 0.0203 0.0203 117.08 108.39 3,781.50 875**0.7276 0.0473 0.0651 0.2402 0.0156 Tube-Side 36,050.35 103.41 105.33 104.37 105.92 2.22 13,851 4.3088 1.5721 1.5470 61.9375 0.9989 0.3645 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr-ft 2-&deg;F/BTU)U Overall (BTU/hr-ft 2'-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)751.60 0.0073 8.17 0.00029413

==0.0 3734207==
5.18 1,053.23 12.63 68,931 0.9276 68,931** Reynolds Number Outside Range of Equation Applicability II Extrapolation Calculation for Row 9(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (lbm/ft-hr)
Air-Side 93,355.31 115.60 112.89 0.0203 0.0203 114.25 106.25 3,781.50 878**0.7278 0.0471 Tube-Side 36,050.35 101.65 103.41 102.53 103.97 2.22 13,586 4.4012 1.6027 1.5786 61.9617 0.9990 0.3638 n Applicability Tube-Side hi (BTU/hr-ft 2.&deg;F) 743.83 j Factor 0.0073 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.16 Tube Wall Resistance (hr-ft2. F/BTU 0.00029413 Overall Fouling (hr-ft2. F/BTU) 0.03734207 U Overall (BTU/hr-ft 2.IF)Effective Area (ftf)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.17 1,053.23 11.65 63,393 0.9277 63,393 Density (Ibm/ft 3) 0.0654 Cp (BTU/Ibm-&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0156** Reynolds Number Outside Range of Equatioi Calc #97-199, Rev. B Attachment P PageP27*** Air Mass Velocity (Lbm/hr-t 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 17:13:08 PROTO-HX 3.00 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY03A 
-CSCS Equipment Area Cooling Coils 02/18/99 10% Reduction in Air Inlet Vol. Flow 1 4wM. S14.TI Extrapolation Calculation for Row 10(Dry)11 I.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ltfhr)
Skin Visc (lbm/.fhr)
Density (Ibm/ft 3)Cp (BTU/Ibm-0 F)K (BTU/hr'ft-&deg;F)
Air-Side (793,355.31) 110.39 0.0203 0.0203 111.64 104.27 3,781.50 881*4 0.7279 0.0469 0.2402 0.0155 Tube-Side 36,050.35 100.03 101.65 100.84 102.18 2.22 13,344 4.4892 1.6317 1.6087 61.9836 0.9990 0.3631 Tube-Side hi (BTU/hr-ft 2-&deg;F) 736.66 j Factor 0.0073 Air-Side ho (BTU/hr-ft 2.&deg;F) 8.15 Tube Wall Resistance (hr-ft 2 -F/BTU 0.00029413 Overall Fouling (hr-ft 2-F/BTU) 0.03734207 U Overall (BTU/hr-ft 2-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.16 1,053.23 10.73 58,318 0.9278 58,318** Reynolds Number Outside Range of Equation Applicability Calc #97-199, Rev. B Attachment P PageP28/FINAL
*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T CC-AA-309-1001 Revision 6 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page 1 Design Analysis (Minor Revision)
Last Page No. 6 Attachment A, A13 Analysis No.:' 97-198 Revision:
I A03 Title: 3 VY Cooler Thermal Performance Model -1(2)VY04A EC/ECR No.: 4 388666 Revision:
000 Station(s):'
LaSalle Unit No.: 8 01 & 02 Safety/QA Class: 9  SR System Code(s): ,o VY Is this Design Analysis Safeguards Information?" Yes El No 0 If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?
12 Yes E] No 0 If yes, ATI/AR#: N/A This Design Analysis SUPERCEDES: 
'3 N/A in its entirety.Description of Changes (list affected pages):1 This revision evaluates a maximum cooling water inlet temperature of 107 OF. The previous temperature that was evaluated was 104 OF. Affected pages are Pages 1 & 2 and Attachment A, Pages Al-Al 3.Disposition of Changes: 15 See attached pages. Changes are acceptable.
Preparer:
18 PL-( X ____ ____ ____ _i__ ____Print Name Sign Name D ae Method of Review: 7 Detailed Review Alternate Calculations E] Testing El Reviewer: " Lie C- f Q... h0 --_ Q/, Print Name Sign Name Date Review Independent review I Peer review El Notes: 9 (For Extemal Anayses Only)External Approver:
20 A1/_Print Name Sign Name Date Exelon Reviewer 2 ,/, Print Rame Siqn Name Date Exelon Approver:
2 A'ci'i , :rr3i 5r ,_2--Print Name SiNg Date 97-198 Rev. A03 Page 2 of 2 Purpose: The purpose of this revision is to verify that the 1(2)VY04A coolers can remove the design heat load of 633,288 BTU/hr with a revised maximum cooling water temperature of 107 OF.Assumptions:
There are no assumptions for this revision.Inputs:* Cooling water temperature 
= 107 OF (Reference 2)* Air temperature 
= 148 OF (Reference 1)* Water flow rate = 66.5 gpm (39.2 gpm front, 27.3 gpm back) (Reference 1)* Air Flow rate = 27,075 cfm (Reference 1)* Fouling factor = 0.02228812 hr-ft 2.F/BTU (design fouling factor) (Reference 1)* 1 tube plugged (5% tube plugging) (Reference 1)

==References:==
: 1. Design analysis 97-198, Rev. A, up to and including Revs AO0 through A02 2. EC 388666, Rev. 000 Identification of Computer Programs: The computer program used in this analysis is Proto HX version 4.01. This program has been validated per DTSQA tracking number EX0000103.
Method of Analysis / Numeric Analysis: The existing heat exchanger model will be revised by changing the input of the 'Tube Inlet Temp" from 104 OF to 107 OF. Because the 1(2)VY04A model consists of two separate models of the front and back portions of the cooler, the temperature, and relative humidity of the air exiting the front cooler are the inputs for the back cooler.The air flow rate is adjusted to match the mass flow rates between the two models. Because the fan for the coolers is at the exit of the cooler, the inlet air flow for the front cooler is iterated until the flow rate at the exit of the last row of the back cooler is approximately 27,075 cfm. The iteration process is detailed in section 6.7 of revision AOO. The calculated input flows for the two coolers are shown on the last page of Attachment A.Results I

== Conclusions:==

The 1(2)VY04A coolers can remove the design heat load of 633,288 BTU/hr with the following conditions:
* 107 OF cooling water temperature
* 148 &deg;F air temperature
* design fouling factor of 0.02228812 hr-ft 2-&deg;F/BTU* 1 tube plugged* air flow rate of 27,075 cfm 0 water flow rate of 66.5 gpm (39.2 gpm front, 27.3 gpm back)The total heat removed at these conditions is 697,494 BTU/hr, which provides 10.13% thermal margin over the design heat load. This thermal margin is enough to account for the 9.5% model uncertainty shown in Attachment J and is acceptable.
Note that a maximum fouling factor was not calculated as was done in previous revisions because it is not practical to set up test conditions that would allow accurate measurement of the fouling factor for these heat exchangers.
The bounding fouling factor is the design fouling factor of 0.02228812 hr-ft 2.&deg;F/BTU.This case is shown in Attachment A.Attachments:
A. Data Report for 1(2)VY04A Front and Back (13 pgs) 04-26-2012 07:02:14 PROTO-HX 4.01 by Proto-Power Corporation (SN#P-LX-1002)
CornEd -- LaSalle Data Report for 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 -148 'F air side, 27,075 cfm, 107 TF water side, 66.5 gpm, Design FF, 1 tube plugged I[ Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Flow 33,546.00 acfm 118.00 gpm Mass Flow 0.00 lbm/hr 0.00 lbm/hr Dry Bulb (Inlet Temperature) 150.00 OF 105.00 OF Inlet Wet Bulb Temperature 92.00 OF Inlet Relative Humidity 0.00 %Dry Bulb (Outlet Temperature) 0.00 OF 0.00 OF Outlet Wet Bulb Temperature 0.00 OF Outlet Relative Humidity 0.00 %Tube Fluid Name Tube-Side Fouling Air-Side Fouling Design Q (BTU/hr)Atmospheric Pressure (psia)Design Sensible Heat Ratio Performance Factor (% Reduction)
Coil Flow Direction Fin Type Configuration (for Air-Side h)Coil Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hrftV-&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Conductivity (BTU/hr4ft.&deg;F)
Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-I.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 19.00 0.5270 0.6250 2.000 1.370 97-198 2.000 Rev. A03 225.00 Attachment A Page Al of A13 04-26-2012 07:02:14 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
CornEd -- LaSalle Calculation Report for 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 -148 'F air side, 27,075 cfm. 107 'F water side, 66.5 gpm, Design FF, I tube plugged Page 1 V Calculation Specifications II i-Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfln)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure (psia)Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm)Air Flow (acfin)Tube Inlet Temp (&deg;F)Air Inlet Temp (&deg;F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp ('F)Atmospheric Pressure (psia)39.20 28,317.00 107.00 148.00 12.76 0.00 14.315 97-198 Rev. A03 Attachment A Page A2 of A13* Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 07:02:14 PROTO--LX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 2 CornEd -- LaSalle Calculation Report for 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 -148 'F air side, 27,075 cfm, 107 'F water side, 66.5 gpm, Design FF, 1 tube plugged..Extrapolation Calculation Summary II Air-Side Mass Flow (Ibm/hr) 104,640.87 Inlet Temperature (IF) 148.00 Outlet Temperature (IF) 131.79 Inlet Specific Humidity Outlet Specific Humidity Tube-Side 19,464.32 107.00 128.77 Tube-Side hi (BTU/hr-ft 2 -F) 0.00 j Factor 0.0000 Air-Side ho (BTU/hr-ft 2.F) 0.00 Tube Wall Resistance (hr ft 2-&deg;F/BTU) 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)2,726.55 0.00 424,209 0.0000 424,209 11 Extrapolation Calculation for Row l(Dry) 1 Air-Side Mass Flow (Ibm/br) 104,640.87 Inlet Temperature (IF) 148.00 Outlet Temperature (IF) 143.95 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 145.97 Skin Temperature (IF) 136.04 Velocity *** 5,736.24 Reynold's Number 2,084 Prandtl Number 0.7253 Bulk Visc (lbm/ft.hr) 0.0491 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0620 Cp (BTU/lbm.&deg;F) 0.2402 K (BTU/hr-ft-&deg;F) 0.0163 Relative Humidity In (%) 12.76 Relative Humidity Out (%) 14.12 Tube-Side 19,464.32 119.19 130.10 124.6468 132.4445 0.7619 5,758 3.4667 1.2896 1.2027 61.6382 0.9990 0.3716 Tube-Side hi (BTU/hr. ft 2-&deg;F) 304.04 j Factor 0.0106 Air-Side ho (BTU/hr-ft 2.OF) 18.03 Tube Wall Resistance (hr ft 2-.F/BTU) 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.48 681.64 20.80 106,080 0.8907 106,080 p97-198 Rev. A03 Attachment A Page A3 of A13*** Air Mass Velocity (Lbm/hr-ft'), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T. Other Properties at Average T 04-26-2012 07:02:14 PROTO-HIX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 3 ComEd -- LaSalle Calculation Report for 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 -148 'F air side, 27,075 cfm, 107 'F water side, 66.5 gpm, Design FF, 1 tube plugged Extrapolation Calculation for Row 2(Dry)II Air-Side Mass Flow (lbm/hr) 104,640.87 Inlet Temperature (IF) 143.95 Outlet Temperature (IF) 140.25 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 142.10 Skin Temperature (IF) 133.01 Velocity *** 5,736.24 Reynold's Number 2,094 Prandtl Number 0.7257 Bulk Visc (lbm/ft-hr) 0.0489 Skin Visc (Ibm/if hr) 0.0000 Density (lbm/ft 3) 0.0624 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-ft-&deg;F) 0.0162 Relative Humidity In (%) 14.12 Relative Humidity Out (%) 15.52 Tube-Side 19,464.32 117.48 127.45 122.4658 129.7309 0.7615 5,643 3.5438 1.3158 1.2318 61.6730 0.9988 0.3708 Tube-Side hi (BTU/hr-ft 2.&deg;F) 297.87 j Factor 0.0105 Air-Side ho (BTU/hr-ft 2.&deg;F) 18.00 Tube Wall Resistance (hr-ft 2-&deg;F/BTU) 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.42 681.64 19.16 96,874 0.8909 96,874]1 Extrapolation Calculation for Row 3(Dry)Air-Side Mass Flow (lbm/hr) 104,640.87 Inlet Temperature 
(&deg;F) 140.25 Outlet Temperature 
(&deg;F) 135.70 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 137.98 Skin Temperature 
(&deg;F) 126.82 Velocity *** 5,736.24 Reynold's Number 2,105 Prandtl Number 0.7260 Bulk Visc (lbm/ft-hr) 0.0486 Skin Visc (Ibm/ft hr) 0.0000 Density (lbm/ft 3) 0.0629 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr.ft.&deg;F) 0.0161 Relative Humidity In (%) 15.52 Relative Humidity Out (%) 17.46 Tube-Side 19,464.32 106.96 119.19 113.0737 122.7968 0.7598 5,159 3.9104 1.4393 1.3117 61.8159 0.9988 0.3676 Tube-Side hi (BTU/hr-ft 2 2-&deg;F) 272.81 j Factor 0.0105 Air-Side ho (BTU/hr-ft 2-&deg;F) 17.96 Tube Wall Resistance (hr.ft 2-&deg;F/BTU) 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.17 681.64 24.34 118,921 0.8911 118,921 97-198 Rev. A03 Attachment A Page A4 of A13* Air Mass Velocity (Lbrn/hrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 07:02:14 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 4 ComEd -- LaSalle Calculation Report for l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 -148 'F air side, 27,075 cfm, 107 'F water side, 66.5 gpm, Design FF, I tube plugged..Extrapolation Calculation for Row 4(Dry)II I.I Air-Side Mass Flow (Ibm/hr) 104,640.87 Inlet Temperature 
(&deg;F) 135.70 Outlet Temperature 
(&deg;F) 131.79 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (&deg;F) 133.75 Skin Temperature 
(&deg;F) 124.13 Velocity *** 5,736.24 Reynold's Number 2,117 Prandtl Number 0.7264 Bulk Visc (ibm/ft-hr) 0.0484 Skin Visc (lbni/ft-hr) 0.0000 Density (lbm/ft 3) 0.0633 Cp (BTU/1bm-&deg;F) 0.2402 K (BTU/hr.ff.&deg;F) 0.0160 Relative Humidity In (%) 17.46 Relative Humidity Out (%) 19.35 Tube-Side 19,464.32 106.96 117.48 112.2195 120.6718 0.7596 5,115 3.9468 1.4515 1.3380 61.8283 0.9988 0.3673 Tube-Side hi (BTU/hr-ft 2.&deg;F) 269.98 j Factor 0.0105 Air-Side ho (BTU/hr-ft 2.&deg;F) 17.92 Tube Wall Resistance (hr-ft 2-&deg;F/BTU) 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.13 681.64 21.05 102,335 0.8913 102,335 97-198 Rev. A03 Attachment A Page A5 of A13* Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 07:05:11 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
ComEd -- LaSalle Data Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 -148 'F air side, 27,075 cfm, 107 TF water side, 66.5 gpm, Design FF, 1 tube plugged Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Flow 32,483.00 acfmn 82.00 gpm Mass Flow 0.00 lbm/hr 0.00 lbm/hr Dry Bulb (Inlet Temperature) 0.00 OF 105.00 OF Inlet Wet Bulb Temperature 0.00 OF Inlet Relative Humidity 0.00 %Dry Bulb (Outlet Temperature) 0.00 OF 0.00 OF Outlet Wet Bulb Temperature 0.00 OF Outlet Relative Humidity 0.00 %Tube Fluid Name Tube-Side Fouling Air-Side Fouling Design Q (BTU/hr)Atmospheric Pressure (psia)Design Sensible Heat Ratio Performance Factor (% Reduction)
Coil Flow Direction Fin Type Configuration (for Air-Side h)Coil Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hrlft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Conductivity (BTU/hr-ft-&deg;F)
Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-I.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 19.00 0.5270 0.6250 1.500 1.370 97-198 2.000 Rev. A03 225.00 Attachment A Page A6 of A13 04-26-2012 07:05:11 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
CornEd -- LaSalle Calculation Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 -148 'F air side, 27,075 cfmn, 107 'F water side, 66.5 gpm, Design FF, I tube plugged Page 1 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfmn)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (&deg;F)Wet Bulb Temp Out (&deg;F)Atmospheric Pressure (psia)Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm)Air Flow (acfm)Tube Inlet Temp ('F)Air Inlet Temp ('F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp ('F)Atmospheric Pressure (psia)27.30 27,561.00 107.00 131.79 19.35 0.00 14.315 97-198 Rev. A03 Attachment A Page A7 of A13 Air Mass Velocity (Lbm/hr-ff), Tube Fluid Velocity (ftlsec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 07:05:11 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 2 ComEd -- LaSalle Calculation Report for I(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 -148 'F air side, 27,075 cfm, 107 TF water side, 66.5 gpm, Design FF, I tube plugged Extrapolation Calculation Summary II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Air-Side 104,640.61 131.79 121.35 Tube-Side 13,555.51 107.00 127.22 Tube-Side hi (BTU/hr.ftR 2.F) 0.00 j Factor 0.0000 Air-Side ho (BTU/hr-ft 2.&deg;F) 0.00 Tube Wall Resistance (hr-ft 2-&deg;F/BTU) 0.00024732 Overall Fouling (hr-ft 2-F/BTU) 0.02228812 U Overall (BTU/hrft 2'-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5,453.10 0.00 273,285 0.0000 273,285 11 Extrapolation Calculation for Row l(Dry) I Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (Ibm/ft-hr)
Density (lbm/Ift 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft-&deg;F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 104,640.61 131.79 130.96 0.020255 0.02Q255 131.37 129.48 5,736.23 1,592 0.7266 0.0482 0.0000 0.0634 0.2402 0.0159 19.35 19.78 Tube-Side 13,555.51 124.51 127.72 126.1164 128.7309 0.5308 4,064 3.4163 1.2724 1.2428 61.6145 0.9989 0.3720 Tube-Side hi (BTU/hr-ft2.&deg;F) 187.93 j Factor 0.0116 Air-Side ho (BTU/hr-ft 2-&deg;F) 19.76 Tube Wall Resistance (hr-ft 2-OF/BTU) 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft2-IF)
Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.29 681.64 5.08 21,784 0.8818 21,784 97-198 Rev. A03 Attachment A Page A8 of A13*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 07:05:11 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 3 ComEd -- LaSalle Calculation Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 -148 IF air side, 27,075 cfmn, 107 IF water side, 66.5 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 2(Dry)II 1. I Air-Side Mass Flow (lbm/hr) 104,640.61 Inlet Temperature (IF) 130.96 Outlet Temperature (OF) 130.09 Inlet Specific Humidity 0.020255 Outlet Specific Humidity 0.020255 Average Temp (IF) 130.53 Skin Temperature (IF) 128.56 Velocity *** 5,736.23 Reynold's Number 1,594 Prandtl Number 0.7266 Bulk Visc (lbm/if hr) 0.0481 Skin Visc (Ibm/ifthr) 0.0000 Density (lbm/ft 3) 0.0635 Cp (BTU/Ibm-'F) 0.2402 K (BTU/hr'if 0-F) 0.0159 Relative Humidity In (%) 19.78 Relative Humidity Out (%) 20.24 Tube-Side 13,555.51 123.37 126.71 125.0365 127.7817 0.5307 4,024 3.4533 1.2850 1.2534 61.6320 0.9989 0.3717 Tube-Side hi (BTU/hr'ft2.
F) 185.77 j Factor 0.0116 Air-Side ho (BTU/hr'ft 2-&deg;F) 19.75 Tube Wall Resistance (hr-ft 2.&deg;F/BTU) 0.00024732 Overall Fouling (hr-ft 2.'F/BTU) 0.02228812 U Overall (BTU/hr'ft 2"&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.25 681.64 5.31 22,618 0.8819 22,618 Extrapolation Calculation for Row 3(Dry) 7 I Air-Side Mass Flow (Ibm/hr) 104,640.61 Inlet Temperature (IF) 130.09 Outlet Temperature (IF) 128.98 Inlet Specific Humidity 0.020255 Outlet Specific Humidity 0.020255 Average Temp (IF) 129.54 Skin Temperature (IF) 126.99 Velocity *** 5,736.23 Reynold's Number 1,596 Prandtl Number 0.7267 Bulk Visc (lbm/Ifthr) 0.0481 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ift 3) 0.0636 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-ft-VF) 0.0159 Relative Humidity In (%) 20.24 Relative Humidity Out (%) 20.85 Tube-Side 13,555.51 120.19 124.51 122.3516 125.9955 0.5303 3,926 3.5479 1.3171 1.2738 61.6749 0.9989 0.3708 Tube-Side hi (BTU/hr-ft 2.0 F) 180.50 j Factor 0.0116 Air-Side ho (BTU/hr-ft 2.&deg;F) 19.74 Tube Wall Resistance (hr-ft 2.&deg;F/BTU) 0.00024732 Overall Fouling (hr-ft 2-0 F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.16 681.64 6.95 29,200 0.8819 29,200 97-198 Rev. A03 Attachment A Page A9 of A13* Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 07:05:11 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 4 ComEd -- LaSalle Calculation Report for l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 -148 'F air side, 27,075 cfmn, 107 'F water side, 66.5 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 4(Dry)II I.Air-Side Mass Flow (Ibm/hr) 104,640.61 Inlet Temperature 
(&deg;F) 128.98 Outlet Temperature (OF) 127.87 Inlet Specific Humidity 0.020255 Outlet Specific Humidity 0.020255 Average Temp (OF) 128.42 Skin Temperature (OF) 125.89 Velocity *** 5,736.23 Reynold's Number 1,599 Prandtl Number 0.7268 Bulk Visc (lbm/ft-hr) 0.0480 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft3) 0.0637 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr.ft-&deg;F) 0.0159 Relative Humidity In (%) 20.85 Relative Humidity Out (%) 21.48 Tube-Side 13,555.51 119.07 123.37 121.2174 124.8943 0.5302 3,885 3.5892 1.3311 1.2866 61.6927 0.9988 0.3704 Tube-Side hi (BTU/hr ft2-&deg;F) 178.19 j Factor 0.0116 Air-Side ho (BTU/hr-ft2-&deg;F) 19.73 Tube Wall Resistance (hr-ft 2.F/BTU) 0.00024732 Overall Fouling (hr-ft 2-.F/BTU) 0.02228812 U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.12 681.64 6.98 29,100 0.8820 29,100 11 Extrapolation Calculation for Row 5(Dry) [Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/Ift 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 104,640.61 127.87 126.39 0.020255 0.020255 127.13 123.76 5,736.23 1,601 0.7269 0.0479 0.0000 0.0639 0.2402 0.0158 21.48 22.36 Tube-Side 13,555.51 114.48 120.19 117.3359 122.4389 0.5297 3,745 3.7367 1.3810 1.3161 61.7525 0.9988 0.3691 Tube-Side hi (BTU/hr.ft 2-&deg;F) 170.55 j Factor 0.0116 Air-Side ho (BTU/hr.ft2.&deg;F) 19.72 Tube Wall Resistance (hr-ft 2-&deg;F/BTU) 0.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr'ft2-OF)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.98 681.64 9.49 38,704 0.8820 38,704 97-198 Rev. A03 Attachment A Page Al0 of A13* Air Mass Velocity (Lbm/hr-ft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 07:05:11 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 5 ComEd -- LaSalle Calculation Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 -148 *F air side, 27,075 cfrn, 107 'F water side, 66.5 gpm, Design FF, 1 tube plugged~., Extrapolation Calculation for Row 6(Dry)II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Vise (lbm/ftfhr)
Density (Ibm/ft 3)Cp (BTU/lbm.0 F)K (BTU/hr-ft.&deg;F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 104,640.61 126.39 124.99 0.020255 0.020255 125.69 122.50 5,736.23 1,604 0.7270 0.0478 0.0000 0.0640 0.2402 0.0158 22.36 23.23 Tube-Side 13,555.51 113.66 119.07 116.3626 121.2497 0.5295 3,710 3.7752 1.3939 1.3307 61.7672 0.9988 0.3688 Tube-Side hi (BTU/hr-ft 2-0 F) 168.50 j Factor 0.0116 Air-Side ho (BTU/hr ft 2-&deg;F) 19.70 Tube Wall Resistance (hr-ft 2.&deg;F/BTU) 0.00024732 Overall Fouling (hr'ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.94 681.64 9.04 36,639 0.8821 36,639[1 Extrapolation Calculation for Row 7(Dry) 71 Air-Side Mass Flow (lbm/hr) 104,640.61 Inlet Temperature (IF) 124.99 Outlet Temperature (IF) 123.06 Inlet Specific Humidity 0.020255 Outlet Specific Humidity 0.020255 Average Temp (IF) 124.03 Skin Temperature (IF) 119.65 Velocity *** 5,736.23 Reynold's Number 1,608 Prandtl Number 0.7271 Bulk Vise (Ibm/ft-hr) 0.0477 Skin Vise (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0642 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0158 Relative Humidity In (%) 23.23 Relative Humidity Out (%) 24.48 Tube-Side 13,555.51 107.04 114.48 110.7576 117.9344 0.5288 3,511 4.0103 1.4728 1.3731 61.8492 0.9988 0.3668 Tube-Side hi (BTU/hr.ft 2.&deg;F) 157.40 j Factor 0.0115 Air-Side ho (BTU/hr-ft 2-&deg;F) 19.68 Tube Wall Resistance (hr-ft 2.&deg;F/BTU) 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr.ft 2.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.73 681.64 12.89 50,363 0.8822 50,363 97-198 Rev. A03 Attachment A Page Al1 of A13* Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (fI/sec);
Air Density at Inlet T, Other Properties at Average T 04-26-2012 07:05:11 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)
Page 6 ComEd -- LaSalle Calculation Report for l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 -148 'F air side, 27.,075 cfm, 107 'F water side, 66.5 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 8(Dry)II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft-&deg;F)
Relative Humidity In (%)Air-Side 104,640.61 123.06 121.35 0.020255 0.020255 122.21 118.30 5,736.23 1,612 0.7273 0.0476 0.0000 0.0644 0.2402 0.0157 24.48 Tube-Side 13,555.51 107.03 113.66 110.3426 116.7770 0.5288 3,497 4.0287 1.4789 1.3884 61.8552 0.9988 0.3667 Tube-Side hi (BTU/hr.ft2.&deg;F) 156.39 j Factor 0.0115 Air-Side ho (BTU/hr.ft 2-&deg;F) 19.67 Tube Wall Resistance (hr ft 2 -&deg;F/BTU) 0.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.71 681.64 11.53 44,875 0.8823 44,875 Relative Humidity Out (%)25.67 97-198 Rev. A03 Attachment A Page A12 of A13* Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Back I I I I Formulas from Section 6.8 for iteration process to determine inlet airflow for extrapolation conditions Total P: P = 14.3151psia I Dry Bulb T OUT: T1 = 121.35 F Specific Hum.: W = 0.02026 VH20 Vap. P: Pv = (W*Rv*P)/(Ra+(W*Rv)) 
= 0.45158 psia 4Rv = 85.778 (ft-lbf)/(Ibm-R)
_Ra = 53.352 (ft-lbf)/(Ibm-R)
Dry Air P: Pa = P -Pv = j 13.86342 psia Dry Air rho OUT: rho.out = (144/Ra)*(Pa/(459.67+T1)) 
= 0.064401 Ibm/ftA3 Dry Air rho IN: rho.in = (144tRa)*(Pa/(459.67+T2)) 
= 0.063264 Ibm/ftA^3 Dry Bulb T IN: T2 = 4 131.79 F Outlet Air Flow: V = 27075 cfm cfm.in cfm.in = V,(rho.outlrho.in) 
= 27561.49 acfm Front _Formulas from Section 6.8 for iteration process to determine inlet airflow for extrapolation conditions Total P: P = 14.315[psia Dry Bulb T OUT: T1 = 131.79 F Specific Hum.: W = 0.02026 H20 Vap. P: Pv = (W*Rv*P)/(Ra+(W*Rv)) 
= 0.45158 psia t Rv = 85.778 (ft-lbf)/(Ibm-R)
Ra 53.352 (ft-lbf)/(Ibm-R)
Dry Air P: Pa = P -Pv = 13.86342 psia Dry Air rho OUT: rho.out = (144/Ra)*(Pa/(459.67+T1)) 
=1 0.063264 Ibm/ftA^3 Dry Air rho IN: rho.in = (144/Ra)*(Pa/(459.67+T2)) 
= 0.061576 Ibm/ftA3 Dry Bulb T IN: T2 = 148 F Outlet Air Flow: V = 27561 cfm[cf m, in cfm.in = V*(rho.out/rho.in) 
= 28316.87 acfm 97-198 Rev. A03 Attachment A Page A13 of A13 CC-AA-309-1001 Revision 1 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page 1 of/'I >lr /u! dg#oS eif. Last Page No.Analysis No. 97-198 , Revision A02 ECIECR No. 356225 Ac d Revision 0 Title: VY Cooler Thermal Performance Model -1(2)VY04A Station(s)
LaSalle Is this Design Analysis Safeguards?
Yes F] No Z Unit No.: 01/02 Does this Design Analysis Contain Unverified Assumptions?
Yes E] No 0 Safety Class SR System Code VY ATI/AR#Description of Change This minor revision reduces the amount of air flow required into the 1(2)VY04A coolers by 5%, and determines a new maximum fouling factor at this reduced air flow.Disposition of Changes (include additional pages as required)See attached sheets. The change is acceptable.
Preparer Reviewer Terry Martin Print Name DLAA/ I-U Sign Name 7/6/05 Date" Date/Print Name[EDetailed Review ame Method of Review Review Notes: Approver Date Print Name (For External Analyses Only)Exelon Reviewer Print Name Sign Name Approver Date Date Print Name Sign Name Print Name Sian Name Purpose: The purpose of this minor revision is to revise the thermal model of the 1(2)VY04A coolers for a 5% reduction in airflow. This assessment will evaluate the adequacy of these heat exchangers with a maximum allowable inlet service water temperature of 104'F, using the design fouling factor of 0.02228812, and 5% tube plugging.
Another case will be run to find the maximum fouling factor with the 5% reduction in air flow and 5% of the tubes plugged.Inputs: The design inputs consist of Reference 1 listed below.Assumptions:
The assumptions indicated in section 5.0 of Reference I are still valid.

==References:==
: 1. Calculation No. 97-198, Rev. A, "Thermal Model of COMED / LaSalle Station Unit I and 2 LPCS Pump Room Coolers." Identification of Computer Programs: Proto Hx version 4.01 is used for this minor revision.
The same software was used for the other revisions in this calculation.
Method of Analysis and Acceptance Criteria: The existing heat exchanger model will be revised by changing the input of the air inlet flow rate, but the air flow rate is measured on the discharge of the cooler. Therefore, the 5% reduction is calculated on the exit of the cooler by manipulation of the inlet air flow rate. This reduction in flow along with the 5% plugged tubes, design fouling factor, and 104'F incoming cooling water was used to determine the thermal margin of the coolers and the maximum fouling factor. The acceptance criteria will be for the calculated heat transfer to exceed the LaSalle design heat load of 633,288 BTU/hr for 1(2)VY04A coolers (See Reference 1, Table 1). The original benchmark model developed for these heat exchangers demonstrated a correlation to vendor performance specification within an assumed 5% margin.Analysis: All input parameters except for air flow rate have remained the same and will not change for this model. Proto HX requires the inlet air flow rate, but our flow device is located on the exit of the heat exchanger.
Each of the coolers actually has two coolers in one (a front and back cooler). Therefore this revision will drop the front cooler air flow by 5%and the back cooler will take the exit flow rate of the front decreased from cooling of the air as its inlet flow. This translates to more than a 5% reduction in overall exit flow and therefore is conservative.
The current analyzed exit flow rate is taken from the 4 th row of the front cooler (see Reference I Rev AOO Attachment B, page B6), which is 108,332.51 Ibm/hr. Dividing this mass flow rate by the density (which is also on that same page) and converting to minutes gives an exit flow rate of 28,479 CFM. Reducing this number by x, 5% results in an exit flow rate of 27,058 CFM. Manipulation of the inlet flow rate was used until the exit flow rate is 27,058 CFM. Using this value for the inlet to the back cooler results in an exit flow rate of 26,520 CFM. Therefore the total reduction in air is 6.9%, which is more than 5%.When the Service Water inlet temperature is 1047F for the limiting flow rate of 39.20 gpm, a design fouling factor of 0.02228812 hr*fi 2*&deg;F/BTU, and a 5% tube plugging allowance, the new total heat transfer is 450,396 BTU/hr for the front cooler and 290,765 BTU/hr for the back cooler for a total of 741,161 BTU/hr. The thermal margin is calculated as Qcalculated 
-Qrequired, which is 741,161 -633,288 BTU/hr = 107,873 or 17.0 % gross Thermal Margin. Allowing for 5% model uncertainty, the net margin is 741,161(0.95) 
-633,288 = 70,815 or 11.2% Thermal Margin.The maximum fouling factor with the same assumptions as above and a 5% model uncertainty is 0.07479374 hr*ft 2 l*F/BTU.Results /

== Conclusion:==

The l(2)VY04A coolers were found to have adequate thermal margin for a maximum lake temperature of 104'F when operated at design fouling conditions (0.02228812 hr*ft 2*OF/BTU), a 5% tube plugging allowance, and a 5% reduction in air flow rate. The maximum fouling factor is 0.07479374 hr*ft 2*&deg;F/BTU. A reduced airflow rate of 27,075 ACFM (95% of 28,500) may therefore be used as acceptance criteria for airside flow rate testing (e.g. LTS-200-19).
Attachments:
Attachment "A" -Proto-Hx Calc. Report for 1(2)VY04A (CSCS=104&deg;F 
@ design fouling, 5% tube plugged, 5% reduction in flow)Attachment "B" -Proto-Hx Calc. Report for 1(2)VY04A (CSCS=104'F Max FF, 5% tube plugged, 5% reduction in flow)3_3A 07-05-2005 08:51:34 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Data Report for 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Flow Mass Flow Dry Bulb (Inlet Temperature)
Inlet Wet Bulb Temperature Inlet Relative Humidity Dry Bulb (Outlet Temperature)
Outlet Wet Bulb Temperature Outlet Relative Humidity Tube Fluid Name Tube-Side Fouling Air-Side Fouling Design Q (BTU/hr)Atmospheric Pressure (psia)Design Sensible Heat Ratio Performance Factor (% Reduction)-
Coil Flow Direction Fin Type Configuration (for Air-Side h)Coil Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Conductivity (BTU/hr-fl-&deg;F) 33,546.00 0.00 150.00 92.00 0.00 0.00 0.00 0.00 acfm Ibm/hr OF OF OF OF 118.00 0.00 105.00 gpm lbm/hr OF 0.00 0 F Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 19.00 0.5270 0.6250 2.000 1.370 2.000 225.00-4 qg4, c4 /n (A4-14 07-05-2005 08:51:34 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 Page 1.1 Calculation Specifications 11 Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure (psia)Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm)Air Flow (acfm)Tube Inlet Temp ('F)Air Inlet Temp (&deg;F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp ('F)Atmospheric Pressure (psia)39.20 27,854.00 104.00 148.00 12.76 0.00 14.315 ATOT**Air Mass Velocity (Lbmihr-ft 2). Tube Fluid Velocity (fi/sec);
Air Density at Inlet T, Other Properties at Average T 07-05-2005 08:51:34 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 2 ComEd -- LaSalle Calculation Report for l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 II Extrapolation Calculation Summary 11 Air-Side Mass Flow (lbm/hr) 102,929.93 Inlet Temperature (0 F) 148.00 Outlet Temperature (0 F) 130.51 Inlet Specific Humidity Outlet Specific Humidity Tube-Side 19,477.06 104.00 127.16 Tube-Side hi (BTU/hr ft2.'F) 0.00 j Factor 0.0000 Air-Side ho (BTU/hr-ft 2"&deg;F) 0.00 Tube Wall Resistance (hr-ft 2.&deg;F/BTU' 0.00024732 Overall Fouling (hr-fi 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)2,726.55 0.00 450,396 0.0000 450,396[ Extrapolation Calculation for Row 1(Dry) I Air-Side Mass Flow (lbmihr) 102,929.93 Inlet Temperature (0 F) 148.00 Outlet Temperature (0 F) 143.59 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (0 F) 145.80 Skin Temperature 
('F) 135.06 Velocity *** 5.642.45 Reynold's Number 2.050 Prandtl Number 0.7253 Bulk Visc (lbm/ft-hr) 0.0491 Skin Visc (lbm/fi-hr) 0.0000 Density (Ibm/fl 3) 0.0620 Cp (BTU/Ibm'&deg;F) 0.2402 K (BTU/hr-ft-&deg;F) 0.0163 Relative Humidity In (%) 12.76 Relative Humidity Out (%) 14.25 Tube-Side 19,477.06 116.91 128.58 122.7422 131.2162 0.7621 5,661 3.5339 1.3124 1.2157 61.6687 0.9989 0.3709 Tube-Side hi (BTU/hr-ft 2.&deg;F) 299.33 j Factor 0.0106 Air-Side ho (BTU/hrft 2 0.&deg;F) 17.84 Tube Wall Resistance (hrft 2.&deg;lF/BTU'j 

==0.0 0024732==
Overall Fouling (hr- ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.41 681.64 22.49 113,542 0.8917 113,542+ +'~A~+ /*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 07-05-2005 08:51:34 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 3 CornEd -- LaSalle Calculation Report for 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 Extrapolation Calculation for Row 2(Dry)Air-Side Tube-Side Mass Flow (lbm/hr) 102,929.93 19,477.06 Tube-Side hi (BTU/hr-ft 2.&deg;F) 292.77 Inlet Temperature (OF) 143.59 115.13 j Factor 0.0106 Outlet Temperature (OF) 139.58 125.75 Air-Side ho (BTU/hr ft 2.&deg;F) 17.80 Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2 0-F/BTU' 0.00024732 Outlet Specific Humidity 0.020268 Overall Fouling (hr-ft 2-.F/BTU) 0.02228812 Average Temp (OF) 141.59 120.4390 Skin Temperature (OF) 131.81 128.3139 U Overall (BTU/hr ft 2.&deg;F) 7.34 Velocity *** 5.642.45 0.7616 Effective Area (ftf) 681.64 Reynold's Number 2.061 5,541 LMTD 20.64 Prandtl Number 0.7257 3.6180 Total Heat Transferred (BTU/hr) 103,257 Bulk Visc (lbm/ft-hr) 0.0488 1.3409 Skin Visc (lbm/ftehr) 0.0000 1.2474 Surface Effectiveness (Eta) 0.8919 Density (lbm/ft3) 0.0625 61.7048 Sensible Heat Transferred (BTU/hr) 103,257 Cp (BTU/Ibm-'F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft'&deg;F) 0.0162 0.3702 Heat to Condensate (BTU/hr)Relative Humidity In (%) 14.25 Relative Humidity Out (%) 15.79 IF Extrapolation Calculation for Row 3(Dry)Air-Side Mass Flow (Ibm/hr) 102,929.93 Inlet Temperature (OF) 139.58 Outlet Temperature (OF) 134.70 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (OF) 137.14 Skin Temperature (OF) 125.23 Velocity *** 5.642.45 Reynold's Number 2.073 Prandtl Number 0.7261 Bulk Visc (lbm/ft-hr) 0.0486 Skin Visc (lbm/ft-hr) 0.0000 Density (Ibm/ft 3) 0.0630 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-fti.F) 0.0161 Relative Humidity In (%) 15.79 Relative Humidity Out (%) 17.93 Tube-Side 19,477.06 103.98 116.91 110.4436 120.9806 0.7598 5,029 4.0242 1.4774 1.3341 61.8537 0.9988 0.3667 Tube-Side hi (BTU/hr-ft 2-OF) 265.99 j Factor 0.0106 Air-Side ho (BTU/hr-ft 2.&deg;F) 17.76 Tube Wall Resistance (hr-ft 2" 0 F/BTU' 0.00024732 Overall Fouling (hr-ft2.&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.07 681.64 26.10 125,736 0.8921 125,736 Lq-?klC8 Act-A++4c4A'q i- 4--par' A 4*** Air Mass Velocity (Lbm/hr.ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 07-05-2005 08:51!:34 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 4 CornEd -- LaSalle Calculation Report for l(2)VYO4A-Front 
-CSCS Equipment Area Cooling Coils VYO4, 5% Plug. Design FF. 5% reduction in air flow 6/29/05 Extrapolation Calculation for Row 4(Dry)Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/frhr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr-ft.&deg;F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 102,929.93 134.70 130.51 0.020268 0.020268 132.60 122.37 5.642.45 2.085 0.7265 0.0483 0.0000 0.0634 0.2402 0.0160 17.93 20.03 Tube-Side 19,477.06 104.04 115.13 109.5872 118.7232 0.7596 4,986 4.0624 1.4902 1.3628 61.8658 0.9988 0.3664 Tube-Side hi (BTU/hr-ft2.&deg;F) 263.11 j Factor 0.0106 Air-Side ho (BTU/hr ft2. F) 17.72 Tube Wall Resistance (hr-ft2. F/BTU' 0.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr.ft 2.-F)Effective Area (ft)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.03 681.64 22.51 107,861 0.8923 107,861 A S_*** Air Mass Velocity (Lbm/hr-ft 2). Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 10:30:31 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Data Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Flow Mass Flow Dry Bulb (Inlet Temperature)
Inlet Wet Bulb Temperature Inlet Relative Humidity Dry Bulb (Outlet Temperature)
Outlet Wet Bulb Temperature Outlet Relative Humidity 32,483.0 0.0 0.0 0.0(0.0(0.0 0.0 0.0(0 acfm 82.00 gpm 0 Ibm/hr 0.00 lbm/hr 0 OF 105.00 OF 0 OF 0%0 OF 0.00 OF 0 OF 0%Tube Fluid Name Tube-Side Fouling Air-Side Fouling Design Q (BTU/hr)Atmospheric Pressure (psia)Design Sensible Heat Ratio Performance Factor (% Reduction)
Coil Flow Direction Fin Type Configuration (for Air-Side h)Coil Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft 0.F)Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Conductivity (BTU/hr-fti.F)
Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 19.00 0.5270 0.6250 1.500 1.370 v*- lo P'ev 4o 2.000 225.00 06-29-2005 10:30:31 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 Page 1.1 I" Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used 11 Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure (psia)Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm)Air Flow (acfm)Tube Inlet Temp (IF)Air Inlet Temp (IF)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (IF)Atmospheric Pressure (psia)27.30 27,058.00 104.00 130.51 20.03 0.00 14.315 Ar s o A 7**Air Mass Velocity (Lbmn/hr-ftt), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 10:30:31 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 2 ComEd -- LaSalle Calculation Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 I. ,1 Extrapolation Calculation Summary II Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Air-Side 102,952.03 130.51 119.22 Tube-Side 13,564.38 104.00 125.43 Tube-Side hi (BTU/hrt. .F) 0.00 j Factor 0.0000 Air-Side ho (BTU/hr'ft2.
0 F) 0.00 Tube Wall Resistance (hr-ft 2-&deg;F/BTU' 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr'ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5,453.10 0.00 290,765 0.0000 290,765 11 Extrapolation Calculation for Row l(Dry)Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (lbm/fI-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft-.F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 102,952.03 130.51 129.59 0.020265 0.020265 130.05 127.96 5.643.66 1.569 0.7267 0.0481 0.0000 0.0635 0.2402 0.0159 20.03 20.53 Tube-Side 13,564.38 122.48 125.99 124.2348 127.1431 0.5309 3,997 3.4811 1.2944 1.2606 61.6449 0.9989 0.3714 Tube-Side hi (BTU/hrft2.&deg;IF) 184.35 j Factor 0.0116 Air-Side ho (BTU/hr-ft2-&deg;F) 19.54 Tube Wall Resistance (hr-ft 2-&deg;F/BTU' 0.00024732 Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-fl2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.21 681.64 5.62 23,790 0.8830 23,790 q-7-/96 4u4o4 46AC~ 4-t41*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (fl/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 10:30:31 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 3 ComEd -- LaSalle Calculation Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 IL .!Extrapolation Calculation for Row 2(Dry)i1 Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (ibm/if hr)Skin Visc (Ibm/ifthr)
Density (lbm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ff-&deg;F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 102,952.03 129.59 128.63 0.020265 0.020265 129.11 126.95 5.643.66 1.571 0.7267 0.0481 0.0000 0.0636 0.2402 0.0159 20.53 21.06 Tube-Side 13,564.38 121.25 124.88 123.0662 126.1082 0.5308 3,955 3.5223 1.3085 1.2725 61.6635 0.9988 0.3710 Tube-Side hi (BTU/hr-ft 2-&deg;F) 182.00 j Factor 0.0116 Air-Side ho (BTU/hrift 2.&deg;F) 19.53 Tube Wall Resistance (hr-ft 2-0 F/BTU, 0.00024732 Overall Fouling (hr.ft2.&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr ft2.&deg;F)Effective Area (Wt 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.17 681.64 5.85 24,578 0.8830 24,578 Extrapolation Calculation for Row 3(Dry) 7I Air-Side Mass Flow (lbm/hr) 102,952.03 Inlet Temperature (IF) 128.63 Outlet Temperature (IF) 127.41 Inlet Specific Humidity 0.020265 Outlet Specific Humidity 0.020265 Average Temp (&deg;F) 128.02 Skin Temperature (IF) 125.25 Velocity *** 5.643.66 Reynold's Number 1.574 Prandtl Number 0.7268 Bulk Visc (lbm/ftrhr) 0.0480 Skin Visc (lbm/ft-hr) 0.0000 Density (Ibm/ff 3) 0.0637 Cp (BTU/lbm.&deg;F) 0.2402 K (BTU/hr-if-&deg;F) 0.0159 Relative Humidity In (%) 21.06 Relative Humidity Out (%) 21.76 Tube-Side 13,564.38 117.83 122.48 120.1542 124.1762 0.5304 3,849 3.6287 1.3445 1.2951 61.7093 0.9988 0.3701 Tube-Side hi (BTU/hr'ft 2.&deg;F) 176.27 j Factor 0.0116 Air-Side ho (BTU/hrift2-F) 19.52 Tube Wall Resistance (hr'ft 2-&deg;F/BTU, 0.00024732 Overall Fouling (hr.ft 2.0 F/BTU) 0.02228812 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.07 681.64 7.62 31,504 0.8831 31,504 p-q7g( AvcL4&1 4*** Air Mass Velocity (Lbrn/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 10:30:31 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 Page 4 Extrapolation Calculation for Row 4(Dry)II I. *1 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ftfhr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-&deg;F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 102,952.03 127.41 126.20 0.020265 0.020265 126.80 124.06 5.643.66 1.576 0.7269 0.0479 0.0000 0.0639 0.2402 0.0158 21.76 22.49 Tube-Side 13,564.38 116.64 121.25 118.9467 122.9902 0.5302 3,805 3.6743 1.3599 1.3094 61.7279 0.9988 0.3697 Tube-Side hi (BTU/hr.ft 2.&deg;F) 173.80 j Factor 0.0116 Air-Side ho (BTU/hr.ft 2.&deg;F) 19.50 Tube Wall Resistance (hr-ft 2"&deg;F/BTU, 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.02 681.64 7.61 31,242 0.8831 31,242[ Extrapolation Calculation for Row 5(Dry)Air-Side Mass Flow (lbm/hr) 102,952.03 Inlet Temperature 
(&deg;F) 126.20 Outlet Temperature (IF) 124.60 Inlet Specific Humidity 0.020265 Outlet Specific Humidity 0.020265 Average Temp (&deg;F) 125.40 Skin Temperature (OF) 121.78 Velocity *** 5.643.66 Reynold's Number 1.579 Prandtl Number 0.7270 Bulk Visc (lbm/ft-hr) 0.0478 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0641 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr-ft-&deg;F) 0.0158 Relative Humidity In (%) 22.49 Relative Humidity Out (%) 23.49 Tube-Side 13,564.38 111.75 117.83 114.7885 120.3756 0.5297 3,656 3.8389 1.4154 1.3417 61.7907 0.9988 0.3682 Tube-Side hi (BTU/hr-ft 2.&deg;F) 165.58 j Factor 0.0116 Air-Side ho (BTU/hr-ftV-&deg;F) 19.49 Tube Wall Resistance (hr-ft2-&deg;F/BTU' 

==0.0 0024732==
Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.87 681.64 10.29 41,187 0.8832 41,187 A-H-1q 4, 4 o*** Air Mass Velocity (Lbrn/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 10:30:31 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 5 ComEd -- LaSalle Calculation Report for I(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 Extrapolation Calculation for Row 6(Dry)II Air-Side Mass Flow (lbm/hr) 102,952.03 Inlet Temperature (0 F) 124.60 Outlet Temperature (0 F) 123.09 Inlet Specific Humidity 0.020265 Outlet Specific Humidity 0.020265 Average Temp (0 F) 123.84 Skin Temperature (0 F) 120.43 Velocity *** 5.643.66 Reynold's Number 1.582 Prandtl Number 0.7271 Bulk Visc (lbm/ft-hr) 0.0477 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0642 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr-ft 0.F) 0.0158 Relative Humidity In (%) 23.49 Relative Humidity Out (%) 24.48 Tube-Side 13,564.38 110.91 116.64 113.7752 119.1091 0.5296 3,620 3.8809 1.4294 1.3578 61.8056 0.9988 0.3679 Tube-Side hi (BTU/hr't2-&deg;F) 163.43 j Factor 0.0116 Air-Side ho (BTU/hr-ft 2.&deg;F) 19.47 Tube Wall Resistance (hr-ft2-&deg;F/BTU' 

==0.0 0024732==
Overall Fouling (hr-ft 2"&deg;F/BTU) 0.02228812 U Overall (BTU/hr.ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.83 681.64 9.77 38,830 0.8833 38,830 Extrapolation Calculation for Row 7(Dry)Air-Side Mass Flow (lbm/hr) 102,952.03 Inlet Temperature 
(&deg;F) 123.09 Outlet Temperature 
(&deg;F) 121.04 Inlet Specific Humidity 0.020265 Outlet Specific Humidity 0.020265 Average Temp (&deg;F) 122.06 Skin Temperature 
('F) 117.44 Velocity *** 5.643.66 Reynold's Number 1.586 Prandtl Number 0.7273 Bulk Visc (lbm/ft-hr) 0.0476 Skin Visc (Ibm/ft-hr) 0.0000 Density (lbm/ft3) 0.0644 Cp (BTU/Ibm-&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0157 Relative Humidity In (%) 24.48 Relative Humidity Out (%) 25.90 Tube-Side 13,564.38 103.96 111.75 107.8562 115.6463 0.5288 3,412 4.1416 1.5166 1.4036 61.8900 0.9988 0.3658 Tube-Side hi (BTU/hrft 2 0-&deg;F) 151.65 j Factor 0.0116 Air-Side ho (BTU/hr.ft 2.0 F) 19.46 Tube Wall Resistance (hr-ft2.&deg;F/BTU' 

==0.0 0024732==
Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr.ftl.
0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.60 681.64 13.83 52,737 0.8834 52,737 q7,4-4s 8r kv 46*** Air Mass Velocity (Lbm/hr1ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 10:30:31 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 6 ComEd -- LaSalle Calculation Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04, 5% Plug, Design FF, 5% reduction in air flow 6/29/05 Extrapolation Calculation for Row 8(Dry)Air-Side Mass Flow (lbm/hr) 102,952.03 Inlet Temperature (OF) 121.04 Outlet Temperature (OF) 119.22 Inlet Specific Humidity 0.020265 Outlet Specific Humidity 0.020265 Average Temp (OF) 120.13 Skin Temperature (OF) 116.01 Velocity *** 5.643.66 Reynold's Number 1.590 Prandtl Number 0.7274 Bulk Visc (ibm/ft hr) 0.0475 Skin Visc (Ibm/ft hr) 0.0000 Density (Ibm/ft 3) 0.0647 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-ft.PF) 0.0157 Relative Humidity In (%) 25.90 Relative Humidity Out (%) 27.24 Tube-Side 13,564.38 103.99 110.91 107.4483 114.4205 0.5288 3,398 4.1606 1.5229 1.4205 61.8957 0.9989 0.3656 Tube-Side hi (BTU/hr-ft 2.&deg;F) 150.63 j Factor 0.0116 Air-Side ho (BTU/hr.ft 2.F) 19.44 Tube Wall Resistance (hr-ft 2-&deg;F/BTU' 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr.ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.57 681.64 12.34 46,896 0.8835 46,896 6{7-(q~ 4L,4O~4/~~1~2 ~*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 11:14:56 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF4 ,36/o q//" 0[-Air Coil Heat Exchanger Input Parameters Flow Mass Flow Dry Bulb (Inlet Temperature)
Inlet Wet Bulb Temperature Inlet Relative Humidity Dry Bulb (Outlet Temperature)
Outlet Wet Bulb Temperature Outlet Relative Humidity Tube Fluid Name Tube-Side Fouling Air-Side Fouling Design Q (BTU/hr)Atmospheric Pressure (psia)Design Sensible Heat Ratio Performance Factor (% Reduction)
Coil Flow Direction Fin Type Configuration (for Air-Side h)Coil Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-fl.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Conductivity (BTU/hr-ft.&deg;F)
Air-Side 33,546.00 acfm 0.00 Ibm/hr 150.00 OF 92.00 OF 0.00 %0.00 OF 0.00 OF 0.00 %Tube-Side 118.00 0.00 105.00 gpm Ibm/hr OF 0.00 OF Fresh Water 0.005000 0.000500 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 19.00 0.5270 0.6250 2.000 1.370 2.000 6T-1 225.00 06-29-2005 11:14:56 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF71  -q /O'- " Page 1 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfmn)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (&deg;F)Atmospheric Pressure (psia)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm)Air Flow (acfm)Tube Inlet Temp (IF)Air Inlet Temp (IF)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (IF)Atmospheric Pressure (psia)39.20 27,854.00 104.00 148.00 12.76 0.00 14.315 q7~J4~B 4d4c~~4~kVtA*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 11:14:56 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 2 ComEd -- LaSalle Calculation Report for l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF-3 S/t* .4 /F/ "-I. .1 Extrapolation Calculation Summary II 11 Mass Flow (ibm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Air-Side 102,929.93 148.00 133.38 Tube-Side 19,477.06 104.00 123.34 Tube-Side hi (BTU/hr ft 2.&deg;F) 0.00 j Factor 0.0000 Air-Side ho (BTU/hr-ft 2.&deg;F) 0.00 Tube Wall Resistance (hrft-2.F/BTU' 0.00024732 Overall Fouling (hr-ft 2.F/BTU) 0.07479374 U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)2,726.55 0.00 376,502 0.0000 376,502 11 Extrapolation Calculation for Row l(Dry)Air-Side Mass Flow (lbm/hr) 102,929.93 Inlet Temperature (7F) 148.00 Outlet Temperature (0 F) 144.31 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (&deg;F) 146.15 Skin Temperature 
(&deg;F) 137.27 Velocity *** 5.642.45 Reynold's Number 2.049 Prandtl Number 0.7253 Bulk Visc (lbm/ftihr) 0.0491 Skin Visc (Ibm/ftrhr) 0.0000 Density (lbm/ft 3) 0.0620 Cp (BTU/Ibm-&deg;F) 0.2402 K (BTU/hr-ft-&deg;F) 0.0163 Relative Humidity In (%) 12.76 Relative Humidity Out (%) 14.00 Tube-Side 19,477.06 114.54 124.32 119.4304 126.6741 0.7614 5,489 3.6559 1.3537 1.2660 61.7205 0.9989 0.3698 Tube-Side hi (BTU/hr-ft2.'F) 289.76 j Factor 0.0106 Air-Side ho (BTU/hr-ftl 2.F) 17.84 Tube Wall Resistance (hr- ft 2.&deg;F/BTU' 0.00024732 Overall Fouling (hr-ft 2 l-F/BTU) 0.07479374 U Overall (BTU/hr-ft 2 .F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.29 681.64 26.39 95,075 0.8917 95,075 eq S A, C,4 .v*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 11:14:56 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 3 ComEd -- LaSalle Calculation Report for 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF,25 6[I Extrapolation Calculation for Row 2(Dry)Air-Side Tube-Side Mass Flow (lbm/hr) 102,929.93 19,477.06 Tube-Side hi (BTU/hrl'ft2-&deg;F) 285.26 Inlet Temperature 
(&deg;F) 144.31 113.36 j Factor 0.0106 Outlet Temperature (IF) 140.90 122.36 Air-Side ho (BTU/hr'ft2.&deg;F) 17.81 Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2.F/BTU' 0.00024732 Outlet Specific Humidity 0.020268 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.07479374 Average Temp (&deg;F) 142.61 117.8608 Skin Temperature (IF) 134.41 124.6414 U Overall (BTU/hr ft 2-&deg;F) 5.26 Velocity *** 5.642.45 0.7611 Effective Area (ft2) 681.64 Reynold's Number 2.059 5,407 LMTD 24.44 Prandtl Number 0.7256 3.7162 Total Heat Transferred (BTU/hr) 87,625 Bulk Visc (lbm/ftihr) 0.0489 1.3740 Skin Visc (Ibm/ft-hr) 0.0000 1.2896 Surface Effectiveness (Eta) 0.8919 Density (Ibm/fl 3) 0.0623 61.7445 Sensible Heat Transferred (BTU/hr) 87,625 Cp (BTU/lbm-&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft-.F) 0.0162 0.3693 Heat to Condensate (BTU/hr)Relative Humidity In (%) 14.00 Relative Humidity Out (%) 15.26 I Extrapolation Calculation.
for Row 3(Dry)Air-Side Mass Flow (lbm/hr) 102,929.93 Inlet Temperature 
(&deg;F) 140.90 Outlet Temperature (IF) 136.92 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (&deg;F) 138.91 Skin Temperature (OF) 129.32 Velocity *** 5.642.45 Reynold's Number 2.068 Prandtl Number 0.7259 Bulk Visc (lbm/ft'hr) 0.0487 Skin Visc (Ibm/ft-hr) 0.0000 Density (Ibm/fl 3) 0.0627 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0161 Relative Humidity In (%) 15.26 Relative Humidity Out (%) 16.91 Tube-Side 19,477.06 104.01 114.54 109.2760 117.9023 0.7596 4,970 4.0765 1.4949 1.3735 61.8702 0.9988 0.3663 Tube-Side hi (BTU/hr ft 2.&deg;F) 262.06 j Factor 0.0106 Air-Side ho (BTU/hr.ft 2-&deg;F) 17.77 Tube Wall Resistance (hrff 2.&deg; F/BTU' 0.00024732 Overall Fouling (hr- ft 2.&deg;F/BTU) 0.07479374 U Overall (BTU/hr.ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.13 681.64 29.29 102,471 0.8920 102,471 Ao~.t%-c. L~*** Air Mass Velocity (Lbm/hrR 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 11:14:56 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 4 ComEd -- LaSalle Calculation Report for 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF-29S f 6/9-r/0 Extrapolation Calculation for Row 4(Dry) I Air-Side Mass Flow (lbm/hr) 102,929.93 Inlet Temperature (0 F) 136.92 Outlet Temperature (0 F) 133.38 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (0 F) 135.15 Skin Temperature 
(&deg;F) 126.58 Velocity *** 5.642.45 Reynold's Number 2.078 Prandtl Number 0.7263 Bulk Visc (lbrn/fi-hr) 0.0484 Skin Visc (lbm/ft-hr) 0.0000 Density (Ibm/fl 3) 0.0631 Cp (BTU/lbm-'F) 0.2402 K (BTU/hr-ft'&deg;F) 0.0160 Relative Humidity In (%) 16.91 Relative Humidity Out (%) 18.56 Tube-Side 19,477.06 103.97 113.36 108.6620 116.4098 0.7595 4,940 4.1044 1.5042 1.3933 61.8788 0.9988 0.3661 Tube-Side hi (BTU/hr-ft 2.&deg;F) 260.04 j Factor 0.0106 Air-Side ho (BTU/hr-ft 2.&deg;F) 17.74 Tube Wall Resistance (hr-ft2-&deg;F/BTU' 

==0.0 0024732==
Overall Fouling (hr-ft 2.F/BTU) 0.07479374 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.12 681.64 26.18 91,330 0.8922 91,330 q7 -A A f_ 5*** Air Mass Velocity (Lbm/hr-fiP), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 11:13:08 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF 6/29/05 Air Coil Heat Exchanger Input Parameters Air-Side Flow Mass Flow Dry Bulb (Inlet Temperature)
Inlet Wet Bulb Temperature Inlet Relative Humidity Dry Bulb (Outlet Temperature)
Outlet Wet Bulb Temperature Outlet Relative Humidity Tube Fluid Name Tube-Side Fouling Air-Side Fouling Design Q (BTU/hr)Atmospheric Pressure (psia)Design Sensible Heat Ratio Performance Factor (% Reduction)
Coil Flow Direction Fin Type Configuration (for Air-Side h)Coil Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Conductivity (BTU/hr-ft-.F) 32,483.00 acfm 0.00 lbm/hr 0.00 OF 0.00 OF 0.00 %0.00 OF 0.00 OF 0.00 %Tube-Side 82.00 gpm 0.00 lbm/hr 105.00 OF 0.00 OF Fresh Water 0.005000 0.000500 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-I.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 19.00 0.5270 0.6250 1.500 1.370&#xfd; 7 -/? 8 AV 14ro 2.000 225.00 06-29-2005 11:13:08 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF 6/29/05 Page I Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfmi)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out (*F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure (psia)Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm)Air Flow (acfmn)Tube Inlet Temp ('F)Air Inlet Temp (&deg;F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp ('F)Atmospheric Pressure (psia)27.30 27,187.00 104.00 133.38 18.56 0.00 14.315 tq 7 f8lwA 4*** Air Mass Velocity (Lbm/hrtVfl), Tube Fluid Velocity (fi/sec):
Air Density at Inlet T, Other Properties at Average T 06-29-2005 11:13:08 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 2 ComEd -- LaSalle Calculation Report for I(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF 6/29/05 Extrapolation Calculation Summary Air-Side Tube-Side Mass Flow (lbm/hr) 102,942.64 13,564.38 Tube-Side hi (BTU/hr-ft 2.0 F) 0.00 Inlet Temperature (IF) 133.38 104.00 j Factor 0.0000 Outlet Temperature 
(&deg;F) 121.98 125.67 Air-Side ho (BTU/hr-ft 2 -F) 0.00 Inlet Specific Humidity Tube Wall Resistance (hr-ft 2.&deg;F/BTU' 0.00024732 Outlet Specific Humidity Overall Fouling (hr-Rf 2.&deg;F/BTU) 0.07479374 U Overall (BTU/hr-ft2.
0 F)Effective Area (ft 2) 5,453.10 LMTD 0.00 Total Heat Transferred (BTU/hr) 293,637 Surface Effectiveness (Eta) 0.0000 Sensible Heat Transferred (BTU/hr) 293,637 Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)Extrapolation Calculation for Row l(Dry)Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (ibm/fi-hr)
Density (lbm/ft 3)Cp (BTU/Ibm.'F)
K (BTU/hr-ft-&deg;F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 102,942.64 133.38 132.33 0.020263 0.020263 132.86 130.52 5.643.15 1.564 0.7265 0.0483 0.0000 0.0632 0.2402 0.0160 18.56 19.08 Tube-Side 13,564.38 122.26 126.24 124.2458 127.4947 0.5309 3,998 3.4807 1.2943 1.2566 61.6447 0.9989 0.3714 Tube-Side hi (BTU/hr ft 2.&deg;F) 184.45 j Factor 0.0117 Air-Side ho (BTU/hr.ft 2.&deg;F) 19.56 Tube Wall Resistance (hr-ft 2-&deg;F/BTU' 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.07479374 U Overall (BTU/hr ft 2.&deg;F)Effective Area (it2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.68 681.64 8.45 26,967 0.8828 26,967 q7 -/f 40_&#xfd;*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 11:13:08 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 3 ComEd -- LaSalle Calculation Report for l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @; 104 F, 5% Plug, 5% reduction in air, MAX FF 6/29/05 Extrapolation Calculation for Row 2(Dry)Air-Side Tube-Side Mass Flow (lbm/hr) 102,942.64 13,564.38 Tube-Side hi (BTU/hr-ft 2.&deg;F) 182.15 Inlet Temperature (OF) 132.33 121.11 j Factor 0.0117 Outlet Temperature 
(&deg;F) 131.28 125.11 Air-Side ho (BTU/hr ft2.&deg;F) 19.55 Inlet Specific Humidity 0.020263 Tube Wall Resistance (hr-ftF.&deg;F/BTU, 0.00024732 Outlet Specific Humidity 0.020263 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.07479374 Average Temp (OF) 131.81 123.1085 Skin Temperature 
(&deg;F) 129.46 126.4156 U Overall (BTU/hr.ft 2.&deg;F) 4.66 Velocity *** 5.643.15 0.5308 Effective Area (ft 2) 681.64 Reynold's Number 1.566 3,956 LMTD 8.53 Prandtl Number 0.7265 3.5208 Total Heat Transferred (BTU/hr) 27,113 Bulk Visc (lbm/ftihr) 0.0482 1.3079 Skin Visc (lbm/ftihr) 0.0000 1.2690 Surface Effectiveness (Eta) 0.8829 Density (Ibm/fl 3) 0.0633 61.6629 Sensible Heat Transferred (BTU/hr) 27,113 Cp (BTU/lbm'&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft-&deg;F) 0.0159 0.3711 Heat to Condensate (BTU/hr)Relative Humidity In (%) 19.08 Relative Humidity Out (%) 19.62 I Extrapolation Calculation for Row 3(Dry)Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbmr/fthr)
Density (Ibm/fl 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-fti.F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 102,942.64 131.28 129.99 0.020263 0.020263 130.63 127.75 5.643.15 1.568 0.7266 0.0482 0.0000 0.0635 0.2402 0.0159 19.62 20.30 Tube-Side 13,564.38 117.34 122.26 119.7964 124.0103 0.5303 3,836 3.6421 1.3490 1.2971 61.7148 0.9988 0.3700 Tube-Side hi (BTU/hr.ft 2.&deg;F) 175.58 j Factor 0.0116 Air-Side ho (BTU/hr-ft2.&deg;F) 19.54 Tube Wall Resistance (hr-ft2.&deg;F/BTU' 

==0.0 0024732==
Overall Fouling (hr ft 2.&deg;F/BTU) 0.07479374 U Overall (BTU/hr ft 2 .F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.60 681.64 10.64 33,318 0.8829 33,318 V-46t11A4;
*** Air Mass Velocity (Lbm/hrRfi 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 11:13:08 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 4 CornEd -- LaSalle Calculation Report for 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF 6/29/05 Extrapolation Calculation for Row 4(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftfhr)
Skin Visc (lbm/ftfhr)
Density (lbm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft-.F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 102,942.64 129.99 128.72 0.020263 0.020263 129.35 126.53 5.643.15 1.571 0.7267 0.0481 0.0000 0.0636 0.2402 0.0159 20.30 21.00 Tube-Side 13,564.38 116.30 121.11 118.7025 122.8763 0.5302 3,796 3.6837 1.3631 1.3108 61.7317 0.9988 0.3696 Tube-Side hi (BTU/hr-ft 2'-F) 173.32 j Factor 0.0116 Air-Side ho (BTU/hr-ft 2.&deg;F) 19.53 Tube Wall Resistance (hr-ft 2.&deg;F/BTU' 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.07479374 U Overall (BTU/hr ft 2 -F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.57 681.64 10.46 32,584 0.8830 32,584 11 Extrapolation Calculation for Row 5(Dry)Air-Side Mass Flow (lbm/hr) 102,942.64 Inlet Temperature (OF) 128.72 Outlet Temperature (OF) 127.14 Inlet Specific Humidity 0.020263 Outlet Specific Humidity 0.020263 Average Temp (OF) 127.93 Skin Temperature (OF) 124.39 Velocity *** 5.643.15 Reynold's Number 1.574 Prandtl Number 0.7268 Bulk Visc (lbm/ftihr) 0.0480 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft')
0.0638 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0159 Relative Humidity In (%) 21.00 Relative Humidity Out (%) 21.92 Tube-Side 13,564.38 111.32 117.34 114.3267 119.8243 0.5296 3,640 3.8580 1.4218 1.3487 61.7975 0.9988 0.3681 Tube-Side hi (BTU/hr.ft 2.&deg;F) 164.61 j Factor 0.0116 Air-Side ho (BTU/hr ft2.0 F) 19.51 Tube Wall Resistance (hr-ft 2-&deg;F/BTU,' 

==0.0 0024732==
Overall Fouling (hr-ft 2.&deg;F/BTU) 0.07479374 U Overall (BTU/hrftl 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.48 681.64 13.36 40,788 0.8831 40,788 6q 7 7i /~,Ao?' d, 46tA i3/4,,c ' i/0*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 11:13:08 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 5 ComEd -- LaSalle Calculation Report for 1 (2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF 6/29/05 Extrapolation Calculation for Row 6(Dry)Air-Side Tube-Side Mass Flow (Ibm/hr) 102,942.64 13,564.38 Tube-Side hi (BTU/hr-ft 2.&deg;F) 162.74 Inlet Temperature (0 F) 127.14 110.60 j Factor 0.0116 Outlet Temperature (0 F) 125.64 116.30 Air-Side ho (BTU/hr ft 2.&deg;F) 19.50 Inlet Specific Humidity 0.020263 Tube Wall Resistance (hr-ft2- F/BTUV 0.00024732 Outlet Specific Humidity 0.020263 Overall Fouling (hr-ft 2 l-F/BTU) 0.07479374 Average Temp (7F) 126.39 113.4468 Skin Temperature (0 F) 123.04 118.7115 U Overall (BTU/hr-ft 2-&deg;F) 4.46 Velocity *** 5.643.15 0.5295 Effective Area (f1 2) 681.64 Reynold's Number 1.577 3,608 LMTD 12.72 Prandtl Number 0.7270 3.8946 Total Heat Transferred (BTU/hr) 38,623 Bulk Visc (Ibm/ft hr) 0.0479 1.4341 Skin Visc (Ibm/fr hr) 0.0000 1.3630 Surface Effectiveness (Eta) 0.8831 Density (Ibm/fl 3) 0.0639 61.8104 Sensible Heat Transferred (BTU/hr) 38,623 Cp (BTU/Ibm.&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr-fr' 0 F) 0.0158 0.3678 Heat to Condensate (BTU/hr)Relative Humidity In (%) 21.92 Relative Humidity Out (%) 22.83 Extrapolation Calculation for Row 7(Dry)Air-Side Mass Flow (lbm/hr) 102,942.64 Inlet Temperature (7F) 125.64 Outlet Temperature 
(&deg;F) 123.72 Inlet Specific Humidity 0.020263 Outlet Specific Humidity 0.020263 Average Temp (0 F) 124.68 Skin Temperature (7F) 120.41 Velocity *** 5.643.15 Reynold's Number 1.580 Prandtl Number 0.7271 Bulk Visc (lbm/ft.hr) 0.0478 Skin Visc (lbm/ft-hr) 0.0000 Density (Ibm/fl 3) 0.0642 Cp (BTU/lbm-'F) 0.2402 K (BTU/hr-ft-&deg;F) 0.0158 Relative Humidity In (%) 22.83 Relative Humidity Out (%) 24.05 Tube-Side 13,564.38 104.05 111.32 107.6813 114.9004 0.5288 3,406 4.1497 1.5193 1.4138 61.8924 0.9988 0.3657 Tube-Side hi (BTU/hr.ft 2.'F) 151.17 j Factor 0.0116 Air-Side ho (BTU/hr-ft2.'F) 19.48 Tube Wall Resistance (hr-ft 2.&deg;F/BTU' 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.07479374 U Overall (BTU/hr.fl 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.32 681.64 16.72 49,249 0.8832 49,249 Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (fi/sec);
Air Density at Inlet T, Other Properties at Average T 06-29-2005 11:13:08 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)
Page 6 CornEd -- LaSalle Calculation Report for 1 (2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% Plug, 5% reduction in air, MAX FF 6/29/05 Extrapolation Calculation for Row 8(Dry) I Mass Flow (Ibm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (lbm/fl-hr)
Density (lbM/ft 3)Cp (BTU/lbm.0 F)K (BTU/hr-ft-&deg;F)
Relative Humidity In (%)Relative Humidity Out (%)Air-Side 102,942.64 123.72 121.98 0.020263 0.020263 122.85 118.95 5.643.15 1.584 0.7272 0.0477 0.0000 0.0643 0.2402 0.0157 24.05 25.23 Tube-Side 13,564.38 103.95 110.60 107.2752 113.9127 0.5288 3,392 4.1687 1.5256 1.4275 61.8981 0.9989 0.3655 Tube-Side hi (BTU/hr ft 2.&deg;F) 150.20 j Factor 0.0116 Air-Side ho (BTU/hr112. 
'F) 19.46 Tube Wall Resistance (hr-ft 2 0.F/BTU', 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.07479374 U Overall (BTU/hr ft 2 .F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.31 681.64 15.32 44,995 0.8833 44,995 q,7~ F/m*** Air Mass Velocity (Lbni/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T CC-AA-309 -ATTACHMENT I -Des.ign Analysis Approval Page I of 2 DESIGN ANALYSIS NO.: Cakc. #97-198 PAGE NO. i Major REV Number: A Minor Rev Numbqr: 01 BRAIDWOOD STATIQN -.[ ] BYRON STATION DESCRIPTION CODE:(cola)
M10[ CLINTONSTATION 
' " '_____________
DRESDEN STATION[X ] LASAL.LE CO. STATION DISCIPLINE.
CQ. (coji) M], QUAD CmES STATION -... ....Unit: 30 [XIl"[X]2 SYSTEMCODE:
0,11) VY TITLE: VY COOLER THERMA, PERFORMANCE MODEL -,.1(2)VY04A 
.[X ] Safety Related [. 1Augmented Quality [ jNonn-Safety Related ATTRIBUTES (C016) ...... ..._'_"_ __TYPE VALUO., TYPE VALUE Elevation 694'Software PROTO-HX __ ____,-i COMPONENT EPN: (c01 6Panel) DOcUMENTNUMBERS: 
((412 Panel) (Design Analyses References)
EPN TYPE Type/Sub Document Number Input (Y/N)IVY04A H15 DCD/ EC#337494 Y 2VY04A H15 -1 "_ _ _ _ _ __....RI.A REMARKS: " -
CC-AA-309 
-ATTACHMENT I -Design Analysis Approval Page 2 of 2 DESIGN ANALYSIS NO. 97-198 REV: A01 PAGE NO. 2,U,, Revision Summary (including EC's incorporated):
Equation 22 (page 18 of Rev. A) in the body of this calculation, indicates Ln, and Ln is the function being used by the program. The 'Data Report*output for the air coolers (example Attachment G. page 2) indicates a LOG (base 10) in the -Fin Configuration" equation for the Colbum 'j' factor- A check of the J' factor numbers indicated on the computer output in the calculation show that the program is using the natural log Ln. The program manufacturer.
Proto-Power, has indicated that the LOG on the Data Report represents indefinite text output and they confirmed that the program is indeed using the natural log (Ln) function for its calculations. (A letter/fax was obtained from Proto-Power on 4-03-02 confirming this discussion.
The fax has been assigned file number SEAG 02-000086).
A copy of this letter is attached (Attachment A to this minor revision).
The calculation results are acceptable as-is.IMI I Electronic Calculation Data Files: Proto-Hx (This data is same as previous minor revision; no computer runs were performed for this minor revision).(Program Name, Version. File Name extension/sizeldatelhourimin)
Design Impact review completed? 
[ ] Yes [x ] NIAI Per EC#:_337494 (If yes, attach impact review sheet)Prepared by: 8._L. Davenport 
/ .N>,,. /Print / Sign Date Reviewed by: D. J. Schmit i ,I-_,,__ _/_---si-gn bate Method of Review. [,Detailed 
[ j Alternate I J Test EThis, Design Analyss At m N In Athed)Reviewed by: Required?.,_ 
),YesVI o P'4nt S- n Data Approved by: _ / /Print SigrD Date Do any ASSUMPTIONS I ENGINEERING JUOGEMENTS require later verification? 
[ I Yes [ X.J No Tracked By: AT<. EC# etc)_ _ _PrintS~ignDt Apr-03-02 08:55 P.01 4) PROTO-POWIER CORPORATION ino A Utility Engineering Subsidiary SZAG Number MEMORANDUM 15 THAMES S1-RMF ("H)i oN, C;i 0u3.40 P-H: M6O.44fl9725 i-X: P00440.8292 WWWPr1t0P0W~r.CA'M F"ilc No. 908SOF/050119/M02001 To: Brian Davenport From: Joseph G. Fay, Date: April 3, 2002 

==Subject:==
PROTO-HX Air Coil Module Brian, The PROTO-IX Data Sheet Output Rcport for Air Coils shows the equation for"Configuration (for Air-Side h)" with the "LOG" term in the equation.
This in fact represents the "Natural Log" and not "Log Base 10." The equation actually uses the Natural Log (LN) term, however, the output rcport is armbiguous in printing "LOG".If you have any other questions, please feel free to give me a call.Sorry for the con fusion.JGF:baj CC: Joseph G. Fayan Job File REQUEST FOR VOID OF A CALCULATION RESERVATION qj-lq&#xfd;PLEASE VOID MY RESERVATION FOR CALCULATION NUMBER_REV IS ION&Ok REASON FOR VOID PRINT NAME-!V)4\ .Z SIGNATU -&#xfd;DATE 1 OF 1 (FINAL)h:\wordperf\cancel.wpf CC-AA-309 
-ATTACHMENT I -Design Analysis Approval Page 1 of 2 DESIGN ANALYSIS NO.: Calc. #97-198 PAGE NO. 1 Major REV Number: A Minor Rev Number: 00[ ] BRAIDWOOD STATION[ ] BYRON STATION DESCRIPTION CODE:(co08)
M10[ ] CLINTON STATION[ ] DRESDEN STATION[X ] LASALLE CO. STATION DISCIPLINE CODE: (c01l) M[ ] QUAD CITIES STATION Unit:[ 10 [Xii [X ]2 [ 13 SYSTEM CODE: (CO11) VY TITLE: VY COOLER THERMAL PERFORMANCE MODEL -1(2)VY04A[ X ] Safety Related [ ] Augmented Quality [ ] Non-Safety Related ATTRIBUTES (C016)TYPE VALUE TYPE VALUE Elevation 694'Software PROTO-HX COMPONENT EPN: (co14 Panel) DOCUMENT NUMBERS: (C012 Panel) (Design Analyses References)
EPN TYPE TypelSub Document Number Input (YIN)1VY04A H15 DCD/DCP EC#334017 Y 2VY04A H 15 /I/I REMARKS:
CC-AA-309 
-ATTACHMENT 1 -Design Analysis Approval Page 2 of 2 DESIGN ANALYSIS NO. 97-198 REV: A00 PAGE NO. 2 Revision Summary (including EC's incorporated):
Updated ProtoHX model for 104 0 F Service Water inlet temperature and calculated Unit I and 2 LPCS Pump Room Cooler thermal margins for design fouling factor and 5% tubes plugged.Electronic Calculation Data Files: ProtoHX 3,02, vyO4a-f.phx.
1088 KB. 4/23/2002, 7:18 pm, vyO4a-b.phx, 1088 KB, 4/23/2002.
7:25 pm (Program Name. Version, File Name extension/sizeidatelhour/min)
Design Impact review completed? 
[ I Yes [X ] NIA. Per ECU: 334017 (If yes, attach impact review sheet)Prepared by: Jeff W. VanStrien 
/ \. ',A. .I PId .Date Reviewed by: Brian L,.Davenpooa I Vo,- ,,-7,--- .I- -n Print -ADate Method of Review: -X ] Detailed [ Alternate 
[ Test This Dei n uersedes:
N/A In Itenie External Desian Analysis Review (Attachment 3 Attached)Reviewed by: I I 911e rPfrfl q Approved by:&#xfd; It tL-Print 1- Sign IDite Do any ASSUMPTIONS 
/ ENGINEERING JUDGEMENTS require later verfication? 
[ I Yes [XJ No Tracked By: AT#, EC# etc.)Page 2 of 2 E-Form CC-AA-309-1 v1.1 for use with CC-AA-309 Revision 1 and above.
CornEd NES-G-14.01 Effective Date: 04/14/00 CALCULATION TABLE OF CONTENTS CALCULATION NO. 97-198 REV. NO. AOO PAGE NO. 3 SECTION: PAGE NO. SUB-PAGE I NO.DESIGN ANALYSIS APPROVAL / TITLE PAGE DESIGN ANALYSIS APPROVAL / REVISION 

==SUMMARY==
TABLE OF CONTENTS 1.0 PURPOSE / OBJECTIVE 2.0 METHODOLOGY AND ACCEPTANCE CRITERIA 3.0 ASSUMPTIONS 
/ ENGINEERING JUDGEMENTS 4.0 DESIGN INPUT 

==5.0 REFERENCES==

==6.0 CALCULATIONS==
7.0 

==SUMMARY==
AND CONCLUSIONS

==8.0 ATTACHMENTS==
Attachment "A" -Proto-Hx Calc. Report for 1(2)VY04A (CSCS=104&deg;F 
@ Design Fouling)Attachment "B" -Proto-Hx Calc. Report for 1 (2)VY04A (CSCS=104 0 F @ Design FF, w/ 5% plugged)Attachment "C" -Proto-Hx Calc. Report for 1(2)VY04A (CSCS=104 0 F @ Max. Allowable FF, w/ 5% plugged)1 2 3 4 4 4 4 4 5 6 6 Al to A14 B1 to B14 C1 to C14 II E-FORM I CornEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO. 97-198 REV. NO. AOO PAGE NO. 4 of 6 1.0 PURPOSE/OBJECTIVE The purpose of this minor revision is to revise the thermal model of the LPCS Pump Room Coolers (1VY04A, 2VY04A) for a 104 0 F Service Water inlet temperature.
This assessment will evaluate the adequacy of these heat exchangers during a maximum allowable inlet service water temperature of 104 0 F. Also an acceptable maximum design fouling factor will be determined.
2.0 METHODOLOGY AND ACCEPTANCE CRITERIA The existing heat exchanger model will be revised by changing the input of the "Tube Inlet Temp." from 100OF to 104OF and simulated for the following conditions:
design fouling factor and design fouling factor with 5% of the tubes plugged. The acceptance criteria will be for the thermal margin at each stated condition to exceed the LaSalle design heat load of 633,288 BTU/hr (Ref.1, Table 1). Additional conservatism was built into this acceptance criteria by assuming a 5% uncertainty in the Proto-HX heat transfer calculations.
The original benchmark model developed for this heat exchanger demonstrated a correlation to vendor performance specification well within this assumed 5% margin.A final case will be evaluated which determines the maximum acceptable fouling factor at which the design heat load can be accommodated including heat transfer model uncertainty and a 5%tube plugging allowance.
3.0 ASSUMPTIONS I ENGINEERING JUDGMENTS The assumptions indicated in section 5.0 of Reference 1 are still valid.4.0 DESIGN INPUTS The design inputs consist of References 1 listed below.

==5.0 REFERENCES==
: 1. Calculation No. 97-198, Rev. A, "Thermal Model of COMED / LaSalle Station Unit 1 and 2 LPCS Pump Room Coolers." E-FORM I1 CornEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO. 97-198 REV. NO. AOO PAGE NO. 5 of 6 6.0 CALCULATIONS The current calculation model is based on a Service Water inlet temperature of 1 00&deg;F with varying cooling water flow rates. Based on Reference 1 Calculations, the limiting flow rate for this unit is 66.5 gpm. At this flow rate, temperature and at an assumed overall fouling factor of 0.03171750 hr*fe*OF/BTU, the amount of heat transferred is 818,271 BTU/hr compared with a LaSalle Station Design Heat Load of 633,288 BTU/hr giving a 29.2% thermal margin (Ref. 1, Table 10).Thermal margin is calculated by the following method: Required Heat Load -Calculated Heat Transfer = Thermal Margin[Equation 1]To express this as a percent of the required heat load, the following method is used: ThermalVf arginf_ x 100% = %Thermalk arg in Re quiredieatLoad
[Equation 2]When the service water inlet temperature is increased to 104OF for the same limiting flow rate, but with a design fouling factor of 0.02228812 hr*ft2*OF/BTU, the heat transfer reduces to 759,971 BTU/hr which represents a 20% thermal margin over the required heat transfer of 633,288 BTU/hr[Attachment A]. With a plugging allowance of 5% of the total tubes in the heat exchanger and running the model again at the design fouling factor and 104OF inlet temperature resulted in a 758,635 BTU/hr heat transfer, a 19.8% thermal margin above the design heat load [Attachment B].The maximum fouling factor (at 104 0 F & 5% plugged) was found to be 0.005 hr*f*&deg;F/BTU tube-side and 0.0005 hr*fte*OF/BTU air-side (0.07479374 hr*ft 2*OF/BTU overall) [Attachment C].I E-FORM I CornEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO. 97-198 REV. NO. AOO PAGE NO. 6 of 6 7.0 

==SUMMARY==
AND CONCLUSIONS The LPCS Pump Room Cooler Model was found to have adequate thermal margin for a maximum lake temperature of 104OF when operated at design fouling conditions.
The maximum fouling factor was found to be 0.005 hr*ft 2*OF/BTU tube-side and 0.0005 hr*ft 2*OF/BTU air-side (0.07479374 hr*ff 2*OF/BTU overall) while maintaining the required heat transfer rate at 104 0 F inlet temperature and with a 5% plugging allowance.

==8.0 ATTACHMENTS==
Attachment "A" -Proto-Hx Calc. Report for 1 (2)VY04A (CSCS=104 0 F @ Design Fouling)Attachment "B" -Proto-Hx Calc. Report for 1(2)VY04A (CSCS=104 0 F @ Design FF, w/ 5% plugged)Attachment "C" -Proto-Hx Calc. Report for 1 (2)VY04A (CSCS=104 0 F @ Max. Allowable FF, w/ 5% plugged)Final Page (Last Page)II E-FORM I CornEd CALCULATION NO.97-198 REVISION NO. AOO PAGE NO. Al of A14 Attachment "A" Proto-Hx Calc. Report for I(2)VY04A (CSCS=104&deg;F 
@ Design Fouling)I E-FORM I 18:22:40 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Data Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [FRONT]04/23/02 II Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 33,546.00 acfm 118.00 gpm Inlet Dry Bulb Temp 150.00 OF 105.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature OF OF Outlet Wet Bulb Temp OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ftr.F)
Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 20.00 0.5270 0.6250 2.000 1.370 2.000 225.00 Calculation No. 97-198 Revision No. AOO Attachment A.L Page No. z of _!
18:22:40 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/23/02 CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [FRONT]Calculation Specifications I Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfin)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out (&deg;F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out (*F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm) 39.20 Air Flow (acfm) 29,321.00 Tube Inlet Temp ('F) 104.00 Air Inlet Temp (&deg;F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ('F) 0.00 Atmospheric Pressure 14.315 Calculation No. 97-198 Revision No. AO0 Attachment Page No. A- of 18:22:40 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [FRONT]04/23/02 I. ii II Extrapolation Calculation Summary II II Air-Side Mass Flow (lbmihr) 108,350.99 Inlet Temperature 
(*F) 148.00 Outlet Temperature (0 F) 130.98 Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ft-&deg;F)
Tube-Side 19,475.71 104.00 127.69 Tube-Side hi (BTU/hr-ft 2&deg;F)j Factor Air-Side ho (BTU/hr-ft2-&deg;F)
Tube Wall Resistance (hr-ft 2.&deg;F/BTU, Overall Fouling (hr-ft 2.0 F/BTU)U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00024732

==0.0 2228812==
2,870.05 461,273 461,273 II Extrapolation Calculation for Row l(Dry)II I.-Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature 
('F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft.hr)
Skin Visc (lbmn/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr'ft-'F)
Air-Side 108,350.99 148.00 143.76 0.0203 0.0203 145.88 135.56 5,642.64 2,050 0.7253 0.0491 0.0620 0.2402 0.0163 Tube-Side 19,475.71 117.29 129.09 123.19 131.86 0.72 5,400 3.5179 1.3070 1.2089 61.6616 0.9990 0.3711 Tube-Side hi (BTU/hr.ft 2-&deg;F) 281.55 j Factor 0.0106 Air-Side ho (BTU/hr.ft 2" 0 F) 17.84 Tube Wall Resistance (hr-ft 2-&deg;F/BTU, 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr.ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.24 717.51 22.12 114,846 0.8917 114,846 Calculation No. 97-198 Revision No. AOO Attachment A Page No. _ of _A) 4*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:22:40 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [FRONT]04/23/02 I Extrapolation Calculation for Row 2(Dry)Mass Flow (lbml/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ftihr)
Skin Vise (lbm/ftrhr)
Density (lbm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr'ft-F)
Air-Side 108,350.99 143.76 139.89 0.0203 0.0203 141.83 132.37 5,642.64 2,061 0.7257 0.0489 0.0624 0.2402 0.0162 Tube-Side 19,475.71 115.49 126.29 120.89 128.99 0.72 5,286 3.6013 1.3352 1.2399 61.6978 0.9988 0.3703 Tube-Side hi (BTU/hr.ft 2.&deg;F) 275.29 j Factor 0.0106 Air-Side ho (BTU/hrft 2-&deg;F) 17.80 Tube Wall Resistance (hr-ft2-0 F/BTUP 0.00024732 Overall Fouling (hr-ft2-*F/BTU) 

==0.0 2228812==
U Overall (BTU/hr-ft 2-&deg;F)Effective Area (fI 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.17 717.51 20.42 105,010 0.8919 105,010 lw__II Extrapolation Calculation for Row 3(Dry)Air-Side Mass Flow (Ibm/br) 108,350.99 Inlet Temperature 
(*F) 139.89 Outlet Temperature (0 F) 135.11 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 137.50 Skin Temperature (0 F) 125.83 Velocity *** 5,642.64 Reynold's Number 2,072 Prandtl Number 0.7261 Bulk Vise (lbm/ft-hr) 0.0486 Skin Vise (lbm/ft-hr)
Density (lbm/ft 3) 0.0629 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr-fr&deg;F) 0.0161 Tube-Side 19,475.71 103.96 117.29 110.62 121.66 0.72 4,786 4.0164 1.4748 1.3257 61.8512 0.9988 0.3668 Tube-Side hi (BTU/hr-ft 2.F) 248.93 j Factor 0.0106 Air-Side ho (BTU/hr-ft 2.F) 17.76 Tube Wall Resistance (hr-ft 2-&deg;F/BTU, 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.88 717.51 26.26 129,631 0.8921 129,631 Calculation No. 97-198 Revision No. AOO Attachment A__Page No. _ of A14*** Air Mass Velocity (Lbm/hr-fi 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:22:40 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [FRONT]04/23/02 Extrapolation Calculation for Row 4(Dry)Mass Flow (lbm/hr)Inlet Temperature (7F)Outlet Temperature (7F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (7F)Skin Temperature (7F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Vise (lbm/ffthr)
Density (Ibm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 108,350.99 135.11 130.98 0.0203 0.0203 133.04 122.96 5,642.64 2,084 0.7264 0.0483 0.0634 0.2402 0.0160 Tube-Side 19,475.71 104.00 115.49 109.74 119.37 0.72 4,744 4.0554 1.4878 1.3545 61.8636 0.9988 0.3664 Tube-Side hi (BTU/hr-ft 2.&deg;F) 246.12 j Factor 0.0106 Air-Side ho (BTU/hr-ft 2.&deg;F) 17.72 Tube Wall Resistance (hr-ft 2.&deg;F/BTU, 0.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr-ft 2.'F)Effective Area (ft)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.84 717.51 22.77 111,787 0.8923 111,787 Calculation No. 97-198 Revision No. AO0 Attachment Page No. _6 of -414 Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Inlet Air Flowrate Calculator 
-1 (2)VY04A [front]Relative Humidity Calculator 
-1 (2)VY04A [back)Total P: Dry Bulb T OUT: Specific Hum.: H20 Vap P: Dry Air P: Dry Air rho OUT: Dry Air rho IN: Dry Bulb T IN: Outlet Air Flow: Sat Air P: Moist Air Rel. Humidity: Equation Coeff.: T=W=Pv = (W*Rv*P)(Ra+(W*Rv) 
=Pa = P -Pv =rho a = (144/Ra)*(Pa/(459.67+T) 
=rho a = (144/Ra)*(Pa/(459.67+T) 
=T=V =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv/Ps =a=14.315 psia Inlet Air Flow 130.98 F 29321 acfm 0.020273629 0.451874527 psia Rv = 85.778 (ft-lbf)I(Ibm-R)
Ra = 53.352 (ft-lbf)/(Ibm-R) 13.86312547 psia 0.0633 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 28500 cfm 2.28 psia 19.78%2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-1 1 Calculation No. 97-198 Revision No. AOO Attachment A Page No. A-7_of Alf 18:30:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Data Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [BACK]04/23/02 I] Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 32,483.00 acfin 82.00 gpm Inlet Dry Bulb Temp OF 105.00 OF Inlet Wet Bulb Temp OF Inlet Relative Humidity %Outlet Dry Bulb Temperature OF OF Outlet Wet Bulb Temp OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-&deg;F)
Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 20.00 0.5270 0.6250 1.500 1.370 2.000 225.00 Calculation No. 97-198 Revision No. AOO Attachment A Page No. AY oft_.
18:30:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/23/02 ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [BACK]Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfmn)Air Dry Bulb Temp In ("F)Air Dry Bulb Temp Out ("F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ("F)Tube Temp Out ("F)Condensate Temperature 
("F)Extrapolation Data Tube Flow (gpm) 27.30 Air Flow (acfmi) 28,500.00 Tube Inlet Temp ("F) 104.00 Air Inlet Temp ("F) 131.0 Inlet Relative Humidity (%) 19.78 Inlet Wet Bulb Temp ("F) 0.00 Atmospheric Pressure 14.315 Calculation No. 97-198 Revision No. AOO Attachment A Page No. f__ of _!_
18:30:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
Com-Ed -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [BACK]04/23/02 Extrapolation Calculation Summary 1 Air-Side Tube-Side Mass Flow (lbm/hr) 108,352.49 13,563.44 Tube-Side hi (BTU/hr-ft 2.0 F)Inlet Temperature (0 F) 130.98 104.00 j Factor Outlet Temperature (0 F) 119.96 126.06 Air-Side ho (BTU/hr-ft2-&deg;F)
Inlet Specific Humidity Tube Wall Resistance (hr-ft 2 -F/BTU, 0.00024732 Outlet Specific Humidity Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02228812 Average Temp (fF)Skin Temperature (0 F) U Overall (BTU/hr-ft 2.&deg;F)Velocity *** Effective Area (W 2) 5,740.10 Reynold's Number LMTD Prandtl Number Total Heat Transferred (BTU/hr) 298,698 Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft-hr)
Surface Effectiveness (Eta)Density (lbrn/ft)
Sensible Heat Transferred (BTU/hr) 298,698 Cp (BTU/lbm'&deg;F)
Latent Heat Transferred (BTU/hr)K (BTU/hr'ft'&deg;F)
Heat to Condensate (BTU/hr)Extrapolation Calculation for Row l(Dry)Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/fbhr)
Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr'ft-&deg;F)
Air-Side 108,352.49 130.98 130.11 0.0203 0.0203 130.54 128.57 5,642.72 1,568 0.7266 0.0482 0.0635 0.2402 0.0159 Tube-Side 13,563.44 123.10 126.59 124.85 127.80 0.50 3,819 3.4599 1.2872 1.2533 61.6350 0.9989 0.3716 Tube-Side hi (BTU/hr-ftl 2-F) 171.91 j Factor 0.0116 Air-Side ho (BTU/hr-ft2-&deg;F) 19.54 Tube Wall Resistance (hr.ft2-&deg;F/BTU, 0.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.99 717.51 5.51 23,662 0.8829 23,662 Calculation No. 97-198 Revision No. AOO Attachment
_Page No. A of*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:30:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [BACK]04/23/02 I Extrapolation Calculation for Row 2(Dry)Mass Flow (ibm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp ("F)Skin Temperature 
("F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (ibm/if hr)Density (Ibm/fr)Cp (BTU/lbm-&deg;F)
K (BTU/hr.ft-&deg;F)
Air-Side 108,352.49 130.11 129.20 0.0203 0.0203 129.65 127.60 5,642.72 1,570 0.7267 0.0481 0.0636 0.2402 0.0159 Tube-Side 13,563.44 121.90 125.52 123.71 126.80 0.50 3,779 3.4996 1.3007 1.2645 61.6533 0.9989 0.3713 Tube-Side hi (BTU/hrft 2.F) 169.71 j Factor 0.0116 Air-Side ho (BTU/hr-ft1 2.F) 19.53 Tube Wall Resistance (hr-ft 2-&deg;F/BTUP 0.00024732 Overall Fouling (hr-ft 2."F/BTU) 0.02228812 U Overall (BTU/hr-ft 2."F)Effective Area (W)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.95 717.51 5.75 24,543 0.8830 24,543 A I.II Extrapolation Calculation for Row 3(Dry)II Mass Flow (ibm/hr)Inlet Temperature 
("F)Outlet Temperature 
("F)Inlet Specific Humidity Outlet Specific Humidity Average Temp ('F)Skin Temperature 
('F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fl hr)Skin Visc (lbm/ft-hr)
Density (lbmift 3)Cp (BTU/lbm-'F)
K (BTU/hrift.&deg;F)
Air-Side 108,352.49 129.20 128.02 0.0203 0.0203 128.61 125.94 5,642.72 1,572 0.7268 0.0480 0.0637 0.2402 0.0159 Tube-Side 13,563.44 118.38 123.10 120.74 124.91 0.50 3,676 3.6068 1.3371 1.2865 61.7001 0.9988 0.3703 Tube-Side hi (BTU/hr-ft 2.&deg;F) 164.13 j Factor 0.0116 Air-Side ho (BTU/hr-ft 2.&deg;F) 19.52 Tube Wall Resistance (hr-f42.&deg;F/BTUP, 0.00024732 Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.85 717.51 7.62 31,949 0.8830 31,949 Calculation No. 97-198 Revision No. AOO Attachment A Page No. //_ of A4_*** Air Mass Velocity (Lbm/hr'ft2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:30:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: l(2)VYO4A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [BACK]04/23/02 lI Extrapolation Calculation for Row 4(Dry) [Mass Flow (ibm/hr)Inlet Temperature (fF)Outlet Temperature 
('F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ftuhr)
Skin Visc (ibm/ft.hr)
Density (Ibm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr'ft'&deg;F)
Air-Side 108,352.49 128.02 126.85 0.0203 0.0203 127.44 124.78 5,642.72 1,575 0.7269 0.0480 0.0638 0.2402 0.0158 Tube-Side 13,563.44 117.20 121.90 119.55 123.75 0.50 3,635 3.6514 1.3522 1.3002 61.7186 0.9988 0.3699 Tube-Side hi (BTU/hr-ft 2-&deg;F) 161.79 j Factor 0.0116 Air-Side ho (BTU/hr-ft 2.&deg;F) 19.51 Tube Wall Resistance (br-ftW-F/BTU, 0.00024732 Overall Fouling (hr-ft 2-1F/BTU) 0.02228812 U Overall (BTU/hr.ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.80 717.51 7.64 31,781 0.8831 31,781 11W .-r II Extrapolation Calculation for Row 5(Dry)II Mass Flow (ibm/hr)Inlet Temperature (fF)Outlet Temperature 
("F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (ibm/ft-hr)
Density (lbm/f 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 108,352.49 126.85 125.28 0.0203 0.0203 126.07 122.52 5,642.72 1,577* 0.7270 0.0479 0.0640 0.2402 0.0158 Tube-Side 13,563.44 112.11 118.38 115.25 121.15 0.50 3,488 3.8202 1.4091 1.3320 61.7838 0.9988 0.3684 Tube-Side hi (BTU/hr-ft 2-&deg;F) 153.65 j Factor 0.0116 Air-Side ho (BTU/hr.ftl 2.F) 19.49 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr.ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.64 717.51 10.49 42,46-1 0.8832 42,461 Calculation No. 97-198 Revision No. AOO Attachment A Page No. iLof Ai4*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:30:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [BACK]04/23/02.1 Extrapolation Calculation for Row 6(Dry)II I.Air-Side Mass Flow (lbm/hr) 108,352.49 Inlet Temperature (0 F) 125.28 Outlet Temperature (0 F) 123.80 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 124.54 Skin Temperature (0 F) 121.19 Velocity *** 5,642.72 Reynold's Number 1,581 Prandtl Number 0.7271 Bulk Visc (Ibm/if hr) 0.0478 Skin Visc (Ibm/rfrhr)
Density (Ibm/ft 3) 0.0641 Cp (BTU/lbm 0'F) 0.2402 K (BTU/hr'ft-F) 0.0158 Tube-Side 13,563.44 111.28 117.20 114.24 119.89 0.50 3,454 3.8616 1.4230 1.3478 61.7988 0.9988 0.3681 Tube-Side hi (BTU/hr-ft2.
0 F) 151.60 j Factor 0.0116 Air-Side ho (BTU/hr.ft 2.0 F) 19.48 Tube Wall Resistance (hr-ft 2"&deg;F/BTU , 0.00024732 Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.60 717.51 10.00 40,153 0.8832 40,153 IN -Extrapolation Calculation for Row 7(Dry)II 1.Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft hr)Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 108,352.49 123.80 121.77 0.0203 0.0203 122.79 118.20 5,642.72 1,584 0.7272 0.0477 0.0644 0.2402 0.0157 Tube-Side 13,563.44 103.99 112.11 108.05 116.43 0.50 3,248 4.1324 1.5135 1.3930 61.8873 0.9988 0.3658 Tube-Side hi (BTU/hr''&deg; 0 F) 139.79 j Factor 0.0116 Air-Side ho (BTU/hr.ft 2.0 F) 19.46 Tube Wall Resistance (hr-ft 2.&deg;F/BTU, 0.00024732 Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.35 717.51 14.33 55,001 0.8833 55,001 Calculation No. 97-198 Revision No. AOO Attachment A Page No. All of Alf*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:30:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, DESIGN FF [BACK]04/23/02 I1 Extrapolation Calculation for Row 8(Dry) ]Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftfhr)
Skin Visc (lbm/ftfhr)
Density (Ibm/ft 3)Cp (BTU/Ibm 0'F)K (BTU/hr'ft-&deg;F)
Air-Side 108,352.49 121.77 119.96 0.0203 0.0203 120.87 116.77 5,642.72 1,588 0.7274 0.0475 0.0646 0.2402 0.0157 Tube-Side 13,563.44 104.02 111.28 107.65 115.18 0.50 3,234 4.1513 1.5198 1.4100 61.8929 0.9988 0.3657 Tube-Side hi (BTU/hr-ft 2.&deg;F) 138.82 j Factor 0.0116 Air-Side ho (BTU/hr.ft 2-&deg;F) 19.44 Tube Wall Resistance (hr-fR 2.-F/BTU, 0.00024732 Overall Fouling (hr.ft 2.-F/BTU) 0.02228812 U Overall (BTU/hr'ft 2."F)Effective Area (ft')LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.32 717.51 12.86 49,148 0.8834 49,148 Calculation No. 97-198 Revision No. AOO Attachment Page No. *** Air Mass Velocity (Lbm/hrftW), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T CornEd CALCULATION NO.97-198 REVISION NO. AOO PAGE NO. B1 of B14 Attachment "B" Proto-Hx Calc. Report for 1 (2)VY04A (CSCS=104 0 F @ Design FF, w/ 5% plugged)II E-FORM I 18:41:07 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 04/23/02 CornEd -- LaSalle Data Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 33,546.00 acfm 118.00 gpm Inlet Dry Bulb Temp 150.00 OF 105.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature OF OF Outlet Wet Bulb Temp OF Outlet Relative Humidity %Tube Fluid Name Fresh Water Tube Fouling Factor 0.001500 Air-Side Fouling 0.000000 Design Heat Transfer (BTU/hr)Atmospheric Pressure 14.315 Sensible Heat Ratio 1.00 Performance Factor (% Reduction) 0.000 Heat Exchanger Type Counter Flow Fin Type Circular Fins Fin Configuration LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in) 105.000 Fin Pitch (Fins/Inch) 10.000 Fin Conductivity (BTU/hr-ft-&deg;F) 128.000 Fin Tip Thickness (inches) 0.0120 Fin Root Thickness (inches) 0.0120 Circular Fin Height (inches) 1.347 Number of Coils Per Unit 2 Number of Tube Rows 4 Number of Tubes Per Row 20.00 Active Tubes Per Row 19.00 Tube Inside Diameter (in) 0.5270 Tube Outside Diameter (in) 0.6250 Longitudinal Tube Pitch (in) 2.000 Transverse Tube Pitch (in) 1.370 Number of Serpentines 2.000 Tube Wall Conductivity (BTU/hr-ft.&deg;F) 225.00 Calculation No. 97-198 Revision No. AOO Attachment 6 Page No. Bz of B 64 18:41:07 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/23/02 CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF Calculation Specifications I Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfmn)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm) 39.20 Air Flow (acfmn) 29,316.00 Tube Inlet Temp ('F) 104.00 Air Inlet Temp (&deg;F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ('F) 0.00 Atmospheric Pressure 14.315 Calculation No. 97-198 Revision No. AO0 Attachment
_Page No. B3 of _B4_
18:41:07 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VYO4 @ 104 F, 5% PLUG, DESIGN FF 04/23/02 1I Extrapolation Calculation Summary I Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (1bm./fthr)
Density (Ibm/fl 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr'ft-&deg;F)
Air-Side 108,332.51 148.00 131.09 Tube-Side 19,475.71 104.00 127.57 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU , Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00024732

==0.0 2228812==
2,726.55 458,168 458,168 II Extrapolation Calculation for Row l(Dry)II Mass Flow (lbm/hr)Inlet Temperature (7F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ftfhr)
Density (lbrn/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-fi.&deg;F)
Air-Side 108,332.51 148.00 143.80 0.0203 0.0203 145.90 135.45 5,938.61 2,158 0.7253 0.0491 0.0620 0.2402 0.0163 Tube-Side 19,475.71 117.26 128.96 123.11 131.59 0.76 5,680 3.5208 1.3079 1.2118 61.6628 0.9990 0.3711 Tube-Side hi (BTU/hr-ft 2 I-F) 300.31 j Factor 0.0104 Air-Side ho (BTU/hr.R 2.&deg;F) 18.45 Tube Wall Resistance (hr-fi2-&deg;F/BTU, 0.00024732 Overall Fouling (hr.f2.&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr.ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.52 681.64 22.23 113,890 0.8885 113,890 Calculation No. 97-198 Revision No. AO0 Attachment
_Page No. f4 of _.iA*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:41:07 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF 04/23/02 Extrapolation Calculation for Row 2(Dry)II Air-Side Mass Flow (lbm/hr) 108,332.51 Inlet Temperature (0 F) 143.80 Outlet Temperature (0 F) 139.95 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 141.87 Skin Temperature (7F) 132.28 Velocity *** 5,938.61 Reynold's Number 2,169 Prandtl Number 0.7257 Bulk Visc (lbm/ft-hr) 0.0489 Skin Visc (lbrn/ft-hr)
Density (lbm/ft 3) 0.0624 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr-ft 0'F) 0.0162 Tube-Side 19,475.71 115.44 126.17 120.81 128.74 0.76 5,560 3.6044 1.3363 1.2427 61.6991 0.9988 0.3703 Tube-Side hi (BTU/hr.ft 2.&deg;F) 293.78 j Factor 0.0104 Air-Side ho (BTU/hr-ft 2-&deg;F) 18.41 Tube Wall Resistance (hr.ft2-&deg;F/BTUP 

==0.0 0024732==
Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.45 681.64 20.55 104,374 0.8887 104,374 Extrapolation Calculation for Row 3(Dry)II II II Mass Flow (Ibmrhr)Inlet Temperature 
('F)Outlet Temperature 
('F)Inlet Specific Humidity Outlet Specific Humidity Average Temp ('F)Skin Temperature 
('F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft--F)
Air-Side 108,332.51 139.95 135.20 0.0203 0.0203 137.57 125.75 5,938.61 2,181 0.7261 0.0486 0.0629 0.2402 0.0161 Tube-Side 19,475.71 104.03 117.26 110.64 121.40 0.76 5,039 4.0154 1.4745 1.3288 61.8509 0.9988 0.3668 Tube-Side hi (BTU/hr.ft 2.&deg;F) 266.60 j Factor 0.0104 Air-Side ho (BTU/hr.ft 2-.F) 18.37 Tube Wall Resistance (hr.ft 2.F/BTU, 0.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr.ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.17 681.64 26.32 128,606 0.8890 128,606 Calculation No. 97-198 Revision No. AOO Attachment 
?Page No. Rj of (__/*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:41:07 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF 04/23/02 Extrapolation Calculation for Row 4(Dry)Mass Flow (lbm/hr)Inlet Temperature 
('F)Outlet Temperature 
('F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
('F)Velocity ***Reynold's Number Prandtl Number Bulk Vise (Ibm/ft hr)Skin Visc (Ibml/fthr)
Density (Ibm/Ift 3)Cp (BTU/lbm'F)
K (BTU/hr'ft'&deg;F)
Air-Side 108,332.51 135.20 131.09 0.0203 0.0203 133.15 122.90 5,938.61 2,193 0.7264 0.0483 0.0634 0.2402 0.0160 Tube-Side 19,475.71 104.00 115.44 109.72 119.13 0.76 4,992 4.0566 1.4882 1.3575 61.8640 0.998.8 0.3664 Tube-Side hi (BTU/hr-ft 2.&deg;F) 263.55 j Factor 0.0104 Air-Side ho (BTU/hr-ft 2.&deg;F) 18.33 Tube Wall Resistance (hr-ft 2"&deg;F/BTU, 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hrft 2 0-F)Effective Area (ft)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.13 681.64 22.91 111,298 0.8892 111,298 Calculation No. 97-198 Revision No. AOO Attachnment 0, PageNo.U of U*** Air Mass Velocity (Lbm/hr'ftV), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Inlet Air Flowrate Calculator 
-1 (2)VY04A [front)Relative Humidity Calculator 
-1(2)VY04A 
[back]Total P: Dry Bulb T OUT: Specific Hum.: H20 Vap P: Dry Air P: Dry Air rho OUT: Dry Air rho IN: Dry Bulb T IN: Outlet Air Flow: Sat Air P: Moist Air Rel. Humidity: Equation Coeff.: W=Pv = (W*Rv*PY(Ra+(W*Rv) 
=Pa = P -Pv =rho a = (144/Ra)*(Pa/(459.67+T) 
=rho a = (144/Ra)*(Pa/(459.67+T) 
=T=V =Ps = a+(b*T)+(c*T2)+(d*T 3)+(e*T 4)+(f*T 5)RH = Pv/Ps =a =14.315 psia Inlet Air Flow 131.09 F 29316 acfm 0.020273629 0.451874527 psia Rv = 85.778 (ft-lbf)/(Ibm-R)
Ra = 53.352 (ft-lbf)I(lbm-R) 13.86312547 psia 0.0633 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 28500 cfm 2.29 psia 19.73%2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-1 I Calculation No. 97-198 Revision No. AOO Attachment 
, Page No. 87 of 8,4 18:51:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Data Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF 04/23/02 I Air Coil Heat Exchanger Input Parameters 
-1 Air-Side Tube-Side Fluid Quantity, Total 32,483.00 acfm 82.00 gpm Inlet Dry Bulb Temp OF 105.00 OF Inlet Wet Bulb Temp OF Inlet Relative Humidity %Outlet Dry Bulb Temperature OF OF Outlet Wet Bulb Temp OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-fI-&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ftV.F)
Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 19.00 0.5270 0.6250 1.500 1.370 2.000 225.00 Calculation No. 97-198 Revision No. AOO Attachment
_Page No. ay of g1 18:51:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/23/02 CornEd -- LaSalle Calculation Report for: 1 (2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm) 27.30 Air Flow (acfmn) 28,500.00 Tube Inlet Temp (IF) 104.00 Air Inlet Temp (IF) 131.1 Inlet Relative Humidity (%) 19.73 Inlet Wet Bulb Temp (IF) 0.00 Atmospheric Pressure 14.315 Calculation No. 97-198 Revision No. AOO Attachment 0 Page No. A 1 3 of M 18:51:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF 04/23/02 I Extrapolation Calculation Summary I1 Mass Flow (ibm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (Ibm/ftrhr)
Skin Vise (lbm/ft-hr)
Density (ibm/fl 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr'ft'&deg;F)
Air-Side 108,330.92 131.09 120.00 Tube-Side 13,563.44 104.00 126.15 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr.ft 2.&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU, 0.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr--f2-.F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/Ir)Heat to Condensate (BTU/hr)5,453.10 300,467 300,467 li.&#xfd;Extrapolation Calculation for Row l(Dry)II II II Mass Flow (lbmlhr)Inlet Temperature (1F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (*F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/flthr)
Skin Visc (lbm/ift hr)Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 108,330.92 131.09 130.22 0.0203 0.0203 130.65 128.63 5,938.52 1,650 0.7266 0.0482 0.0634 0.2402 0.0159 Tube-Side 13,563.44 123.19 126.69 124.94 127.82 0.53 4,023 3.4565 1.2861 1.2530 61.6335 0.9989 0.3717 Tube-Side hi (BTU/hr.ft1 2-F) 185.77 j Factor 0.0114 Air-Side ho (BTU/hr.ft 2-&deg;F) 20.21 Tube Wall Resistance (hr-ft1 2-F/BTU, 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.30 681.64 5.52 23,686 0.8796 23,686 Calculation No. 97- 198 Revision No. AOO Attachment 
%Page No. OiD of *** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:51:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF 04/23/02 I Extrapolation Calculation for Row 2(Dry) I Mass Flow (ibm/hr)Inlet Temperature (IF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (ibm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (ibm/fl 3)Cp (BTU/lbm 0'F)K (BTU/hr'ft'&deg;F)
Air-Side 108,330.92 130.22 129.31 0.0203 0.0203 129.76 127.66 5,938.52 1,652 0.7267 0.0481 0.0635 0.2402 0.0159 Tube-Side 13,563.44 121.98 125.61 Tube-Side hi (BTU/hr-ft 2.-F) 183.46 j Factor 0.0114 Air-Side ho (BTU/hr.ft 2-.F) 20.20 Tube Wall Resistance (hr-ft2-00.00024732 Overall Fouling (hr-ft 2-.F/BTU) 0.02228812 123.79 126.82 0.53 3,981 3.4966 1.2997 1.2643 61.6519 0.9989 0.3713 U Overall (BTU/hr.ft 2-IF)Effective Area (fW 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.26 681.64 5.77 24,610 0.8796 24,610 U" Extrapolation Calculation for Row 3(Dry)II Mass Flow (ibm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ftihr)
Density (lbm/f')Cp (BTU/lbm-&deg;F)
K (BTU/hr'ft-&deg;F)
Air-Side 108,330.92 129.31 128.13 0.0203 0.0203 128.72 125.98 5,938.52 1,654 0.7268 0.0480 0.0637 0.2402 0.0159 Tube-Side 13,563.44 118.47 123.19 120.83 124.89 0.53 3,873 3.6035 1.3360 1.2867 61.6987 0.9988 0.3703 Tube-Side hi (BTU/hrft 2 F-F) 177.64 j Factor 0.0114 Air-Side ho (BTU/hr-ft 2.&deg;F) 20.19 Tube Wall Resistance (hr-ft 2-&deg;F/BTUY 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.15 681.64 7.63 32,014 0.8797 32,014 Calculation No. 97-198 Revision No. AOO Attachment a Page No. 8j of3A&#xfd;*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:51:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1 (2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF 04/23/02 I[ Extrapolation Calculation for Row 4(Dry)Air-Side Mass Flow (Ibm/hr) 108,330.92 Inlet Temperature 
('F) 128.13 Outlet Temperature 
('F) 126.95 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp ('F) 127.54 Skin Temperature (0 F) 124.81 Velocity *** 5,938.52 Reynold's Number 1,657 Prandtl Number 0.7269 Bulk Visc (ibm/ft hr) 0.0480 Skin Visc (lbm/fifhr)
Density (lbm/ft) 0.0638 Cp (BTU/lbm'&deg;F) 0.2402 K (BTU/hr-ft-&deg;F) 0.0159 Tube-Side 13,563.44 117.26 121.98 119.62 123.72 0.53 3,829 3.6487 1.3513 1.3006 61.7175 0.9988 0.3699 Tube-Side hi (BTU/hr-ft 2.&deg;F) 175.17 j Factor 0.0114 Air-Side ho (BTU/hr.ft 2 -F) 20.17 Tube Wall Resistance (hr-ft2-&deg;F/BTL., 0.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.11 681.64 7.67 31,920 0.8797 31,920 1.Extrapolation Calculation for Row 5(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/ft3)Cp (BTU/lbm.'F)
K (BTU/hr..&deg;F)
Air-Side 108,330.92 126.95 125.38 0.0203 0.0203 126.16 122.52 5,938.52 1,660 0.7270 0.0479 0.0640 0.2402 0.0158 Tube-Side 13,563.44 112.17 118.47 115.32 121.07 0.53 3,675 3.8172 1.4081 1.3330 61.7828 0.9988 0.3684 Tube-Side hi (BTU/hr-ft 2.&deg;F) 166.69 j Factor 0.0114 Air-Side ho (BTU/hr.ft 2.F) 20.16 Tube Wall Resistance (hr-ft2-&deg;F/BTU, 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft1 2-F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.95 681.64 10.51 42,647 0.8798 42,647 Calculation No. 97-198 Revision No. AOO Attachment A Page No. Bt- of 6i#*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:51:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF 04/23/02 I Extrapolation Calculation for Row 6(Dry) I Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (7F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/nlhir)
Skin Visc (lbm/ft.hr)
Density (lbm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr'fl'&deg;F)
Air-Side 108,330.92 125.38 123.88 0.0203 0.0203 124.63 121.18 5,938.52 1,663 0.7271 0.0478 0.0641 0.2402 0.0158 Tube-Side 13,563.44 111.29 117.26 114.28 119.80 0.53 3,638 3.8599 1.4224 1.3490 61.7982 0.9988 0.3681 Tube-Side hi (BTU/hr.f1f.F) 164.49 j Factor 0.0114 Air-Side ho (BTU/hrfl 2.&deg;F) 20.14 Tube Wall Resistance (hr.ft 2.&deg;F/BTUI, 0.00024732 Overall Fouling (hr.ft 2-0 F/BTU) 0.02228812 U Overall (BTU/hrIft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.91 681.64 10.04 40,433 0.8799 40,433 W1.Extrapolation Calculation for Row 7(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft.hr)
Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft--F)
Air-Side 108,330.92 123.88 121.84 0.0203 0.0203 122.86 118.13 5,938.52 1,667 0.7272 0.0477 0.0644 0.2402 0.0157 Tube-Side 13,563.44 103.98 112.17 108.08 116.25 0.53 3,419 4.131.3 1.5131 1.3955 61.8869 0.9988 0.3658 Tube-Side hi (BTU/hr.ft2-&deg;F) 152.18 j Factor 0.0114 Air-Side ho (BTU/hr-ft 2-&deg;F) 20.12 Tube Wall Resistance (hr.ft 2-F/BTU' 0.00024732 Overall Fouling (hr.ft 2.F/BTU) 0.02228812 U Overall (BTU/hr.ft 2.&deg;F)Effective Area (Wt 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.66 681.64 14.38 55,478 0.8800 55,478 Calculation No. 97-198 Revision No. AOO Attachment g Pagle No. (1W of 64*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:51:02 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, DESIGN FF 04/23/02 I Extrapolation Calculation for Row 8(Dry)Mass Flow (ibm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (7F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr'ft 0'F)Air-Side 108,330.92 121.84 120.00 0.0203 0.0203 120.92 116.68 5,938.52 1,671 0.7273 0.0475 0.0646 0.2402 0.0157 Tube-Side 13,563.44 103.96 111.29 107.63 115.00 0.53 3,404 4.1522 1.5201 1.4125 61.8932 0.9988 0.3657 Tube-Side hi (BTU/hr.ft 2.&deg;F) 151.07 j Factor 0.0114 Air-Side ho (BTU/hr'ft 2-0 F) 20.10 Tube Wall Resistance (hr-ft 2.&deg;F/BTUQ 0.00024732 Overall Fouling (hr.ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr'f2.&deg;F)
Effective Area (W)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTUihr)5.64 681.64 12.93 49,680 0.8801 49,680 Calculation No. 97-198 Revision No. AOO Attachment 
&Page No. j1-ofi_4*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T CornEd CALCULATION NO.97-198 REVISION NO. AOO PAGE NO. Cl of C14 Attachment "C" Proto-Hx Caic. Report for 1(2)VY04A (CSCS=104&deg;F 
@ Max. Allowable FF, w/ 5% plugged)II E-FORM II 19:14:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Data Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF 04/23/02 I Air Coil Heat Exchanger Input Parameters 
:: Air-Side Tube-Side Fluid Quantity, Total 33,546.00 acfm 118.00 gpm Inlet Dry Bulb Temp 150.00 OF 105.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature OF OF Outlet Wet Bulb Temp OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft 0.F)Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F)
Fresh Water 0.005000 0.000500 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 19.00 0.5270 0.6250 2.000 1.370 2.000 225.00 Calculation No. 97-198 Revision No. AOO Attachment c Page No. Cz of'.1 19:14:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/23/02 ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (&deg;F)Wet Bulb Temp Out (&deg;F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (&deg;F)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm) 39.20 Air Flow (acfin) 29,179.00 Tube Inlet Temp (&deg;F) 104.00 Air Inlet Temp (IF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (IF) 0.00 Atmospheric Pressure 14.315 Calculation No. 97-198 Revision No. AO0 Attachment Page No. C3 of C14 19:14:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF 04/23/02 Extrapolation Calculation Summary Air-Side Mass Flow (lbm/hr) 107,826.25 Inlet Temperature (OF) 148.00 Outlet Temperature (OF) 133.86 Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/f-ihr)
Skin Vise (lbm/itfhr)
Density (ibm/fl 3)Cp (BTU/lbm.0 F)K (BTU/hr'ft.'F)
Tube-Side 19,475.71 104.00 123.60 Tube-Side hi (BTU/hr.ft.F) j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr.ft.&deg;F/BTUt, Overall Fouling (hr-ft-&deg;F/BTU)
U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00024732

==0.0 7479374==
2,726.55 381,356 381,356 rMM.11 Extrapolation Calculation for Row l(Dry)II Air-Side Mass Flow (ibm/hr) 107,826.25 Inlet Temperature (0 F) 148.00 Outlet Temperature 
(&deg;F) 144.46 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 146.23 Skin Temperature (OF) 137.55 Velocity *** 5,910.86 Reynold's Number 2,147 Prandtl Number 0.7253 Bulk Vise (lbrn/ft-hr) 0.0491 Skin Vise (lbm/ftlhr)
Density (Ibm/fl 3) 0.0620 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hrift-&deg;F) 0.0163 Tube-Side 19,475.71 114.72 124.54 119.63 126.89 0.76 5,499 3.6484 1.3512 1.2635 61.7174 0.9989 0.3699 Tube-Side hi (BTU/hr-ft 2.&deg;F) 290.29 j Factor 0.0105 Air-Side ho (BTU/hr-ft 2-&deg;F) 18.39 Tube Wall Resistance (hr-ft 20.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 7479374==
U Overall (BTU/hrft2-&deg;OF)
Effective Area (fW2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.34 681.64 26.26 95,530 0.8888 95,530 Calculation No. 97-1 98 Revision No. AOO Attachment C Page No. C4 ofC Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 19:14:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1 (2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF 04/23/02 I[ Extrapolation Calculation for Row 2(Dry) I Air-Side Tube-Side Mass Flow (lbm/hr) 107,826.25 19,475.71 Tube-Side hi (BTU/hr.ft 2.&deg;F) 285.98 Inlet Temperature (OF) 144.46 113.59 j Factor 0.0104 Outlet Temperature (OF) 141.19 122.66 Air-Side ho (BTU/hr'ft 2-&deg;F) 18.36 Inlet Specific Humidity 0.0203 Tube Wall Resistance (hr-ft 2-&deg;F/BTU, 0.00024732 Outlet Specific Humidity 0.0203 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.07479374 Average Temp (OF) 142.82 118.12 Skin Temperature (OF) 134.79 124.94 U Overall (BTU/hr.ft 2-&deg;F) 5.31 Velocity *** 5,910.86 0.76 Effective Area (ft 2) 681.64 Reynold's Number 2,156 5,421 LMTD 24.39 Prandtl Number 0.7256 3.7059 Total Heat Transferred (BTU/hr) 88,293 Bulk Visc (Ibm/ft-hr) 0.0489 1.3706 Skin Vise (lbm/ft-hr) 1.2861 Surface Effectiveness (Eta) 0.8890 Density (lbm/ft) 0.0623 61.7405 Sensible Heat Transferred (BTU/hr) 88,293 Cp (BTU/lbm'&deg;F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K 0.0162 0.3694 Heat to Condensate (BTU/hr)Extrapolation Calculation for Row 3(Dry)Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (ibm/fPl)Cp (BTU/lbm-&deg;F)
K (BTU/hr.ft-&deg;F)
Air-Side 107,826.25 141.19 137.32 0.0203 0.0203 139.25 129.75 5,910.86 2,166.0.7259 0.0487 0.0627 0.2402 0.0161 Tube-Side 19,475.71 103.99 114.72 109.35 118.13 0.76 4,974 4.0729 1.4937 1.3705 61.8691 0.9988 0.3663 Tube-Side hi (BTU/hr-ft 2-&deg;F) 262.31 j Factor 0.0104 Air-Side ho (BTU/hr.ft 2.&deg;F) 18.33 Tube Wall Resistance (hr-ft 2-&deg;F/BTU. 0.00024732 Overall Fouling (hr1ft2-&deg;F/BTU) 

==0.0 7479374==
U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.18 681.64 29.54 104,292 0.8892 104,292 Calculation No. 97-198 Revision No. AOO Attachment C PageNo. C5 oftc4*** Air Mass Velocity (Lbm./hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 19:14:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF 04/23/02 I. .3 II Extrapolation Calculation for Row 4(Dry)II Mass Flow (ibm/hr)Inlet Temperature (7F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (7F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbmr/fthr)
Skin Visc (lbm/ft hr)Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 107,826.25 137.32 133.86 0.0203 0.0203 135.59 127.08 5,910.86 2,176 0.7262 0.0485 0.0631 0.2402 0.0160 Tube-Side 19,475.71 104.00 113.59 108.79 116.69 0.76 4,946 4.0985 1.5022 1.3895 61.8770 0.9988 0.3661 Tube-Side hi (BTU/hr.ft 2-&deg;F) 260.43 j Factor 0.0104 Air-Side ho (BTU/hr'ft 2-&deg;F) 18.29 Tube Wall Resistance (hr-ft 2-&deg;F/BTUL, 0.00024732 Overall Fouling (hr.ft2-&deg;F/BTU) 

==0.0 7479374==
U Overall (BTU/hr.ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.17 681.64 26.48 93,241 0.8893 93,241 Calculation No. 97-198 Revision No. AOO Attachment C Page No. C6 of C_Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Inlet Air Flowrate Calculator 
-1(2)VY04A 
[front]Relative Humidity Calculator 
-1(2)VY04A 
[back]Total P: Dry Bulb T OUT: Specific Hum.: H20 Vap P: Dry Air P: Dry Air rho OUT: Dry Air rho IN: Dry Bulb T IN: Outlet Air Flow: Sat Air P: Moist Air Rel. Humidity: Equation Coeff.: T=W=Pv = (W*Rv*PY(Ra+(W*Rv) 
=Pa = P -Pv =rho a = (144/Ra)*(PaI(459.67+T) 
=rho a = (144/Ra)*(Pa/(459.67+T) 
=T=V=Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f-T 5) =RH = Pv/Ps =a=b=14.315 psia Inlet Air Flow 133.86 F 29179 acfm 0.020273629 0.451874527 psia Rv = 85.778 (ft-lbf)/(Ibm-R)
Ra = 53.352 (ft-lbf)/(Ibm-R) 13.86312547 psia 0.0630 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 28500 cfm 2.47 psia 18.33%2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071 E-1 1 Calculation No. 97-198 Revision No. AOO Attachment c.Page No. CI of C- 14 19:13:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Data Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF 04/23/02 I] Air Coil Heat Exchanger Input Parameters I Air-Side Tube-Side Fluid Quantity, Total 32,483.00 acfm 82.00 gpm Inlet Dry Bulb Temp OF 105.00 OF Inlet Wet Bulb Temp OF Inlet Relative Humidity %Outlet Dry Bulb Temperature OF OF Outlet Wet Bulb Temp OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F)
Fresh Water 0.005000 0.000500 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 19.00 0.5270 0.6250 1.500 1.370 2.000 225.00 Calculation No. 97-198 Revision No. AOO Attachment C Page No. cy of C_14 19:13:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/23/02 CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF Calculation Specifications I Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfin)Air Dry Bulb Temp In (OF)Air Dry Bulb Temp Out (OF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (OF)Wet Bulb Temp Out (OF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm) 27.30 Air Flow (acfm) 28,500.00 Tube Inlet Temp (OF) 104.00 Air Inlet Temp (&deg;F) 133.9 Inlet Relative Humidity (%) 18.33 Inlet Wet Bulb Temp (OF) 0.00 Atmospheric Pressure 14.315 Calculation No. 97-198 Revision No. AOO Attachment C Page No. _j of 19:13:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF 04/23/02 11 Extrapolation Calculation Summary 11 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ifthr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hrift-&deg;F)
Air-Side 107,826.38 133.86 122.69 Tube-Side 13,563.44 104.00 126.25 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr-ft 2-&deg;F/BTU, 0.00024732 Overall Fouling (hr.ft 2-&deg;F/BTU) 0.07479374 U Overall (BTU/hrft2-&deg;F)
Effective Area (W 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5,453.10 301,411 301,411 MI. .Extrapolation Calculation for Row 1(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft'&deg;F)
Air-Side 107,826.38 133.86 132.86 0.0203 0.0203 133.36 131.07 5,910.87 1,637 0.7264 0.0483 0.0632 0.2402 0.0160 Tube-Side 13,563.44 122.79 126.79 124.79 128.03 0.53 4,018 3.4618 1.2879 1.2506 61.6359 0.9989 0.3716 Tube-Side hi (BTU/hr.ft-&deg;F) 185.54 j Factor 0.0115 Air-Side ho (BTU/hr-ft 2.&deg;F) 20.17 Tube Wall Resistance (hr.ft2-F/BTU, 0.00024732 Overall Fouling (hrP.t2-&deg;F/BTU) 

==0.0 7479374==
U Overall (BTU/hr-ft2.&deg; F)Effective Area (fI)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.73 681.64 8.40 27,083 0.8797 27,083 Calculation No. 97-198 Revision No. AOO Attachment c Page No. Cio of C 14*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 19:13:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF 04/23/02 Extrapolation Calculation for Row 2(Dry)Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fthr)
Skin Visc (ibm/ft.hr)
Density (Ibm/ft')Cp (BTU/lbm'&deg;F)
K (BTU/hr'ft-&deg;F)
Air-Side 107,826.38 132.86 131.85 0.0203 0.0203 132.35 130.05 5,910.87 1,639 0.7265 0.0483 0.0633 0.2402 0.0160 Tube-Side 13,563.44 121.68 125.70 123.69 127.00 0.53 3,977 3.5001 1.3009 1.2623 61.6535 0.9988 0.3713 Tube-Side hi 2-F) 183.32 j Factor 0.0115 Air-Side ho (BTU/hr-ft 2.'F) 20.16 Tube Wall Resistance (hr-ft 2-&deg;F/BTU, 0.00024732 Overall Fouling (hr-ft1 2.F/BTU) 0.07479374 U Overall (BTU/hr'ft 2"&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.71 681.64 8.49 27,242 0.8798 27,242.3 Extrapolation Calculation for Row 3(Dry)II 1. _ _Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (1bm/fl-hr)
Skin Visc (lbmr/flhr)
Density (lbm/ft)Cp (BTU/1bm-'F)
K (BTU/hr'ft'&deg;F)
Air-Side 107,826.38 131.85 130.59 0.0203 0.0203 131.22 128.36 5,910.87 1,641 0.7266 0.0482 0.0634 0.2402 0.0159 Tube-Side 13,563.44 117.78 122.79 120.29 124.55 0.53 3,853 3.6237 1.3428 1.2907 61.7072 0.9988 0.3701 Tube-Side hi (BTU/hr-ft 2-&deg;F) 176.58 j Factor 0.0115 Air-Side ho (BTU/hr.ft 2-&deg;F) 20.15 Tube Wall Resistance (hr-ft 2.&deg;F/BTU, 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.07479374 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.64 681.64 10.73 33,912 0.8798 33,912 Calculation No. 97-198 Revision No. AOO Attachment C Page No. c.ii of it A*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 19:13:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF 04/23/02 Extrapolation Calculation for Row 4(Dry)Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/f1.hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr'ft."F)
Air-Side 107,826.38 130.59 129.36 0.0203 0.0203 129.97 127.18 5,910.87 1,644 0.7267 0.0481 0.0635 0.2402 0.0159 Tube-Side 13,563.44 116.79 121.68 119.24 123.46 0.53 3,815 3.6633 1.3562 1.3037 61.7235 0.9988 0.3698 Tube-Side hi (BTU/hr-ft 2.F) 174.41 j Factor 0.0115 Air-Side ho (BTU/hr.ft1 2.F) 20.14 Tube Wall Resistance (hr-1f 2.&deg;F/BTU, 0.00024732 Overall Fouling (hr.ft 2.&deg;F/BTU) 0.07479374 U Overall (BTU/hr-ft 2-F)Effective Area (WV)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.62 681.64 10.54 33,160 0.8799 33,160 Y 1 .1 Extrapolation Calculation for Row 5(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number -Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft.hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft&deg;F)
Air-Side 107,826.38 129.36 127.80 0.0203 0.0203 128.58 125.03 5,910.87 1,647 0.7268 0.0480 0.0637 0.2402 0.0159 Tube-Side 13,563.44 111.58 117.78 Tube-Side hi (BTU/hr.ft1 2-F) 165.35 j Factor 0.0115 Air-Side ho (BTU/hr-ft 2-&deg;F) 20.12 Tube Wall Resistance (hr-ft2-&deg;F/BTU, 0.00024732 Overall Fouling (hr.ft1 2.F/BTU) 0.07479374 114.68 120.32 0.53 3,652 3.8433 1.4168 1.3423 61.7922 0.9988 0.3682 U Overall (BTU/hr-ft2-OF)
Effective Area (Wt 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.52 681.64 13.65 42,037 0.8800 42,037 Calculation No. 97-198 Revision No. AOO Attachment
_&#xa3;_Page No. Ci of __*** Air Mass Velocity (Lbrn/hrf1 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 19:13:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
ComEd -- LaSalle Calculation Report for: 1 (2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF 04/23/02 IF Extrapolation Calculation for Row 6(Dry) -1 Mass Flow (lbm/hr)Inlet Temperature 
("F)Outlet Temperature 
("F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (7F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft hr)Skin Visc (lbm/ft-hr)
Density (lbmi/ft)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 107,826.38 127.80 126.33 0.0203 0.0203 127.06 123.71 5,910.87 1,650 0.7269 0.0479 0.0639 0.2402 0.0158 Tube-Side 13,563.44 110.91 116.79 113.85 119.25 0.53 3,622 3.8777 1.4284 1.3560 61.8045 0.9988 0.3679 Tube-Side hi (BTU/hr.ft 2.'F) 163.58 j Factor 0.0114 Air-Side ho (BTU/hr-ft 2-&deg;F) 20.11 Tube Wall Resistance (hr-ft 2."F/BTU , 0.00024732 Overall Fouling (hr.ft2-"F/BTU) 

==0.0 7479374==
U Overall (BTU/hr.ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.50 681.64 12.98 39,788 0.8801 39,788 F Extrapolation Calculation for Row 7(Dry)It Mass Flow (lbm/hr)Inlet Temperature 
("F)Outlet Temperature 
("F)Inlet Specific Humidity Outlet Specific Humidity Average Temp ("F)Skin Temperature 
("F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr.ft .F)Air-Side 107,826.38 126.33 124.42 0.0203 0.0203 125.37 121.05 5,910.87 1,654-. 0.7270 0.0478 0.0641 0.2402 0.0158 Tube-Side 13,563.44 104.00 111.58 107.79 115.30 0.53 3,410 4.1446 1.5176 1.4083 61.8909 0.9988 0.3657 Tube-Side hi (BTU/hr.ft 2-&deg;F) 151.44 j Factor 0.0114 Air-Side ho (BTU/hr-ft 2.&deg;F) 20.09 Tube Wall Resistance (hr-ft 2.&deg;F/BTU, 0.00024732 Overall Fouling (hr.ft 2.F/BTU) 0.07479374 U Overall (BTU/hr-ft 2.'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)..
Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.35 681.64 17.29 51,316 0.8801 51,316 Calculation No. 97-198 Revision No. AOO Attachment c_Page No. C i_ of _&#xfd;*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Averaize T 19:13:36 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils VY04 @ 104 F, 5% PLUG, MAX FF 04/23/02.1 Extrapolation Calculation for Row 8(Dry)II Mass Flow (Ibm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (ibm/ft hr)Skin Visc (lbm/ft-hr)
Density (Ibm/ift3)
Cp (BTU/lbm-'F)
K (BTU/hr-ftP'F)
Air-Side 107,826.38 124.42 122.69 0.0203 0.0203 123.55 119.60 5,910.87 1,658 0.7272 0.0477 0.0643 0.2402 0.0158 Tube-Side 13,563.44 103.99 110.91 107.45 114.35 0.53 3,398 4.1603 1.5228 1.4214 61.8956 0.9989 0.3656 Tube-Side hi (BTU/hr-ft 2"&deg;F) 150.61 j Factor 0.0114 Air-Side ho (BTU/hr-ft 2.0 F) 20.07 Tube Wall Resistance (hr'ft 2-*F/BTUP, 0.00024732 Overall Fouling (hr-ft 2.0 F/BTU) 0.07479374 U Overall (BTU/hr-ft 2.0 F)Effective Area (WV)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.34 681.64 15.84 46,873 0.8802 46,873 Calculation No. 97-108 Revision No. AOO Attachment C Page No. c 4 of C 14*** Air Mass Velocity (Lbmihr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T PROTO-POWER CORPORATION CALCULATION TITLE SHEET CLIENT: PROJECT: Commonwealth Edison LaSalle Station GL 89-13 Heat Exchanger Testing Program CALCULATION TITLE: CALCULATION NO.: VY Cooler Thermal Performance Model -- 1(2)VY04A 97-198 FILE NO.: 31-003 COMPUTER CODE & VERSION (if applicable):
PROTO-HX T M , Version 3.01 REV TOTAL NO. OF ORIGINATOR/DATE VERIFIER/DATE APPROVAI/DATE PAGES A 240 Lloyd Philpot MerdAby A &#xfd;2 7// t/, "1131f, -/t $ 4 4 Page i of vi Form No.: P1050101 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALCNO. 97-198 REV A PAGE ii OF vi GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB No. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A Revision History Revision Revision Description A Original Issue Form No.: P1050102 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION c"cNo 97-198 REV A PAGE iii OF Vi GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TIT'LE VY Cooler Thermal Performance Model -- I(2)VY04A CALCULATION VERIFICATION FORM REVIEW METHOD: EXTENT OF VERIFICATION:
Approach Checked: [j N/A E] Complete Calculation:
Logic Checked: a N/A rl Arithmetic Checked: G- N/A C] Revised areas only: El Alternate Method 0 N/A 3" (Attach Brief Summary)Computer Program Used El N/A (3/ Other (describe below): E](Attach Listing)Other N/A [*Errors Detected *Error Resolution
*Other Comments*Extra References Used*(Attach extra sheets if needed)CALCULATION FOUND TO BE VALID AND CONCLUSIO S TO BE CORRECT AND REASONABLE:
IDV Signature:
77' Initials: L~zz Printed Name: U-I, '.f$1c-Azjb A-10o't Date: &#xfd; -/3- Form No.: P1050103 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO. 97- 198 REV A PAGE iv OF vi GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 vERIFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJEcT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A TABLE OF CONTENTS CALCULATION TITLE SHEET ...........................................................................................
i CALCULATION REVISION HISTORY ...................................................................................
ii CALCULATION VERIFICATION SHEET .............................................................................
iii TABLE OF CONTENTS .........................................................................................................
iv LIST OF ATTACHM ENTS ........................................................................................................
vi Total Number of Pages in Preface of Calculation:
6 1. PURPOSE ...................................................................................................................................
1 2. BACKGROUND 
........................................................................................................................
1 3. DESIGN INPUTS .............................................................................................................
2 4. APPROACH ...............................................................................................................................
5 5. ASSUM PTIONS .........................................................................................................................
5 6. ANALYSIS .................................................................................................................................
6 6.1 Tube Pitch .............................................................................................................................
6 6.2 Coil Configuration 
.......................................................................................................
6 6.3 Sensible Heat Ratio ...............................................................................................................
7 6.4 Derivation of Benchmarking Inputs -- Front Coil ...........................................................
8 6.5 M odel Benchmarking 
....................................................................................................
14 6.6 Derivation of Back Coil Benchmarking Inputs .............................................................
19 6.7 Effective Coil Finned Length .........................................................................................
19 6.8 Extrapolation Conditions 
...............................................................................................
19 6.9 Thermal M argin Assessment 
.........................................................................................
22 6.10 Limiting Cooling W ater Flow Analysis ......................................................................
23 6.1 1 Fouling Sensitivity Analysis ........................................................................................
23 7. RESULTS .................................................................................................................................
23 7.1 M odel Benchm arking ....................................................................................................
23 7.2 Thermal M argin Analysis ...............................................................................................
25 7.3 Limiting Cooling W ater Flow Rate Analysis ...............................................................
26 7.4 Fouling Sensitivity Analysis ...........................................................................................
27 Form No.: P1050104 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE V o vi GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJECt LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A 8. C O N C LU SIO N S ......................................................................................................................
28 9. R EFERE N C ES .........................................................................................................................
28 Total Number of Pages in Body of Calculation:
30 Form No.: P1050104 Rev.: 10 Date: 10/21/97e Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE vI OF vi GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERUFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A LIST OF ATTACHMENTS Attachment Subject Matter Total Pages A Attachment A to Proto-Power Calculation 97-198 Rev. A: II Design Input Data -- Selected References B Attachment B to Proto-Power Calculation 97-198 Rev. A: 2 Cooler Inspection Photographs 
-- 1VYOIA and 1VY02A C Attachment C to Proto-Power Calculation 97-198 Rev. A: 14 PROTO-HXTm Reports -- Initial Benchmark Case D Attachment D to Proto-Power Calculation 97-198 Rev. A: 2 Excerpt from Compact Heat Exchangers, Kays and London E Attachment E to Proto-Power Calculation 97-198 Rev. A: 27 PROTO-HXTm Reports -- Final Benchmark Case F Attachment F to Proto-Power Calculation 97-198 Rev. A: 14 PROTO-HXTm Reports -- Thermal Margin Assessment (Clean)G Attachment G to Proto-Power Calculation 97-198 Rev. A: 14 PROTO-HXTm Reports -- Thermal Margin Assessment (Service)H Attachment H to Proto-Power Calculation 97-198 Rev. A: 13 Derivation of Moist Air Properties I Attachment I to Proto-Power Calculation 97-198 Rev. A: 14 PROTO-HXT M Reports -- Limiting Flow Analysis Attachment J to Proto-Power Calculation 97-198 Rev. A: 55 PROTO-HXTM Analytical Uncertainty Analysis K Attachment K to Proto-Power Calculation 97-198 Rev. A: 4 Comparing Surface Areas of Spiral and Circular Fins L Attachment L to Proto-Power Calculation 97-198 Rev. A: 5 Walkdown Data for Coil Physical Dimensions M Attachment M to Proto-Power Calculation 97-198 Rev. A: 27 PROTO-HXTM Reports -- Fouling Sensitivity Analysis N Attachment N to Proto-Power Calculation 97-198 Rev. A: 2 PROTO-HXTm Model Database Disk (plus 4 disks)Complete Calculation (total number of pages): 240 Form No.: P1050104 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 1 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A 1. PURPOSE The purpose of this calculation is to develop a thermal performance analysis model for the Commonwealth Edison (CornEd) LaSalle Station NE cubicle area coolers 1(2)VY04A.
This model can be used for the analysis of heat exchanger thermal performance test data as part of the LaSalle Station GL 89-13 heat exchanger testing program or for any other engineering analysis subject to the limitations itemized at the end of this section.Once developed, the model is used to identify the thermal margin of the heat exchanger at specified performance conditions as follows: " at LaSalle Station Reference Conditions as currently defined in the LaSalle Station design and licensing basis; and* at lower service water flow rates (with increased fouling) to support service water system re-balancing efforts.The thermal performance model documented in this calculation has been created and used with PROTO-HX, Version 3.01. The model can be used with previous versions of PROTO-HX and produce identical results as long as the following restriction is upheld:* Air coils analyzed in Version 3.0 or earlier can be analyzed only in non-condensing modes of operation.
Current limitations of use for PROTO-HX are established by the limits on fluid properties included within the software.
Fluid properties contained within PROTO-HX are currently limited to the following temperature ranges: " Air: 32-320&deg;F* Water: 32-500&deg;F 2. BACKGROUND LaSalle Station is in the process of implementing a heat exchanger thermal performance monitoring program and a service water system flow balancing program in response to the requirements of NRC Generic Letter 89-13. Development of an analytical model in PROTO-HXTM, Version 3.01, will allow timely analysis of data resulting from the test program and will ensure the limiting flow requirements for the coolers are adequately defined.
PROTO-POWER CORPORATION CALC NO. 97-198 PA A AGE 2 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye Jo03 NO 31-003 CLIENT Conmmonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A 3. DESIGN INPUTS The thermal performance model is developed using PROTO-HX T M , Version 3.01. PROTO-HX T M was developed and validated in accordance with Proto-Power's Nuclear Software Quality Assurance Program (SQAP). This program meets the requirements of I OCFR50 Appendix B, IOCFR21, and ANSI NQA-1, and was developed in accordance with the guidelines and standards contained in ANSI/IEEE Standard 730/1984 and ANSI NQA-2b-1991.
PROTO-HX T M Version 3.01 was verified and approved for use as documented in Reference (1).The design inputs for this calculation consist of the heat exchanger design basis performance requirements (Tablel), performance specifications (Table 2) and construction details (Table 3)provided by the heat exchanger manufacturer data sheet (Attachment A) or other design documents as referenced.
Construction details give the necessary information for model construction while performance specifications are used to benchmark the model.VY cooler thermal performance in this calculation will be assessed only with respect to the nominal accident conditions (i.e., design basis LOCA) with no tubes plugged. Condensing modes of operation and tube plugging margins are not addressed.
Since the 1(2)VY04A cooler is made up of two separate and unique coil sections (a 4-row front coil and an 8-row back coil), two separate models will be developed.
Table 1: LaSalle Station Reference Conditions Parameter Value Reference*
Heat Rate (BTU/hr) 633,288 2 Atmospheric Pressure (in-w.g.) 
-0.4 4 Air-Side Inlet Temperature 
-- Dry Bulb ('F) 148 4 Fan Volumetric Flow Rate (cfm) 28,500 18,19 Tube-Side Flow Rate (gpm) 200 (total) 5 Tube-Side Inlet Temperature (0 F) 100 6*Selected references included as Attachment A
PROTO-POWER CORPORATION CALCNO. 97-198 REV A PAGE 3 OF 30 GROTON, CONNECTICUT ORJGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROlEc LaSalle Station GL 89-13 Heat Exchanger Testing TYTLE VY Cooler Thermal Performance Model -- 1(2)VY04A Table 2: Vendor Specified Performance Parameter Back Coil Front Coil Reference*
Air-Side Fouling Factor (Design) 0 0 Assumption (1)Air-Side Entering Fluid Flow Rate (scfm) 27,450 27,450 7 Air-Side Inlet Dry Bulb Temperature 
('F) -150 7 Air-Side Inlet Wet Bulb Temperature 
('F) -92 7 Air-Side Outlet Dry Bulb Temperature (0 F) 109.0 -7 Air-Side Outlet Wet Bulb Temperature 
('F) 84.0 -7 Tube Side Fouling Factor (Design) 0.0015 0.0015 8 Tube Side Fluid Type Service Water Service Water 9,10 (Fresh) (Fresh)Tube Side Fluid Flow Rate (gpm) Note (1) Note (1) -Tube Side Inlet Temperature (0 F) 105 105 7 Tube Side Outlet Temperature 
('F) Note (2) Note (2) -Design Q (BTU/hr) Note (3) Note (3) -Notes: '(1) A combined flow of 200 gpm is reported on the vendor data sheet (Reference (7))(2) A combined outlet temperature of 117.3 1&deg;F is reported on the vendor data sheet (Reference (7))(3) A combined heat load of 1,194,000 BTU/hr is reported on the vendor data sheet (Reference (7))*Selected references included as Attachment A
PROTO-POWER CORPORATION CALCNO. 97-198 REV A PAGE 4 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB No 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VY04A Table 3: Construction Details Parameter Back Coil Front Coil Reference"'
Heat Exchanger Type and relative Carrier Air Coil Carrier Air Coil 7,11 direction of Tube-side and Air flow. Counter flow Counter flow Fin Type Spiral Spiral 7,8 Coil Finned Length (in) 108.00 -specified (2) 108.00 -specified (2) 7 105.00 -effective (2) 105.00 -effective (2) 20 Fin Pitch (fins/in) 10.0 10.0 7 Fin Material ASTM B209 Al. ASTM B209 Al. 7 Fin Conductivity (BTU/hr-ft-&deg;F) 128 128 16 Fin Thickness (in) 0.012 0.012 7 Fin Height (in) 1.347 1.347 20 Number of Coils per Unit 2 2 7 Number of Tube Rows 8 4 7 Number of Tubes per Row 20 20 7 Number of Plugged Tubes 0 0 I'ube Outside Diameter (in) 0.625 (3) 0.625 (3) 7 Tube Wall Thickness (in) 0.049 0.049 7 Tube Inside Diameter (in) 0.527 0.527 7 Longitudinal (horiz.) Tube Pitch (in) see Section 6 see Section 6 -Transverse (vertical)
Tube Pitch (in) 1.370 1.370 20 Tube Layout Staggered Staggered 20 Number of Serpentines 2 (i.e., Double Circuiting) 2 (i.e., Double Circuiting) 7 Tube Wall Material SB75 Copper SB75 Copper 7 Tube Wall Conductivity (BTU/hr-ft-0 F) 225 225 12 Sensible Heat Ratio I I (Section 6.3)Notes: (1) Selected references included as Attachment A (2) The Reference 7 coil finned length will be used for benchmarking to vendor performance data per Section 6.0. The Reference 20 effective coil finned length will be used for subsequent analyses.(3) The Reference 7 tube OD is within the tolerance of Reference 20 and will be used in lieu of Ref. 20.
PROTO-POWER CORPORATION CALCNO. 97-198 REV A FAGE oF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DA{ E 7/13/98 VERIFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PRo1ECT LaSalle Station GL 89-13 Heat Exchanger Testing TILE VY Cooler Thermal Performance Model -- 1(2)VY04A 4. APPROACH This calculation utilizes plant/vendor fabrication specifications provided in Section 3.0 to develop a thermal performance prediction model for the 1(2)VY04A coolers. The calculation then benchmarks the model by comparing the heat transfer rate calculated by PROTO-HXTM Version 3.01 with the manufacturer's specifications for thermal performance.
The Colburnj-factor vs. Reynolds Number relationship is adjusted as necessary to meet the manufacturer's performance specifications.
After the model is benchmarked, it will be used to determine the margin between the available and required heat removal rates and to establish a revised limiting flow rate in support of service water system re-balancing efforts.5. ASSUMPTIONS
: 1. The fouling factor specified in Reference (8) is for the tube-side only and design air-side fouling is zero. This is typical for air coils of this type and application.
Future validation of this assumption is not required.2. The vendor-supplied performance specifications of Reference (7) (included as Attachment A) are considered to be an accurate reflection of the as-built performance of the VY Cooler. Future validation of this assumption is not required.3. The slope of the "Colburn j-factor vs. Reynolds Number" curve is the same for the current coil and the standard coil represented by curve "CF-9.05-3/4 J-A" in the PROTO-HXTM "h-configurations" Library. This assumption is based on physical similarities between the VY coolers and the standard configuration represented by "CF-9.05-3/4 J-A" as elaborated in Section 6, below. The model benchmarking process described in Section 6 brings the model into precise agreement with the vendor performance data making initial configuration selection immaterial.
The only difference caused by initial configuration selection that would be detectable in analysis results is when analyses are performed over a very wide range (orders of magnitude) of air-side Reynolds numbers. A wide range of Reynolds numbers causes the slight variation in slopes of the j-factor equations of different configurations to become more obvious. Given the fixed fan flow rate and a relatively tight band of normal operating and Reference conditions, along with the fact that benchmarking conditions are extremely close to Reference conditions, such wide variations in Reynolds numbers are not anticipated.
Future validation of this assumption is not required.4. The portion of the total flow that is directed toward the front coil section will equally divide between the top and bottom coils since these coils are identical with no tubes PROTO-POWER CORPORATION CALCNO- 97-198 REV A PAGE 6 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERJFIED BY M. Aboye JOB No 31-003 CLIENT Commonwealth Edison PROJEcT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A plugged. The portion of the total flow that is directed toward the back coil section will equally divide between the top and bottom coils since these coils are identical with no tubes plugged. Future validation of this assumption is not required.5. The front and back coil sections have the same Colburn j-factor vs. Reynolds Number relationship.
This assumption is based on physical similarities between the VY coolers and the standard configuration represented by "CF-9.05-3/4 J-A" as elaborated in Assumption 3 above and Section 6, below. Future validation of this assumption is not required.6. The VY cooler spiral fin geometry is closely approximated by the PROTO-HX T M circular fin configuration.
This is due to the relatively tight fin pitch configuration resulting in a negligible difference in fin/tube outside surface area. This assumption is supported in Attachment K. Future validation of this assumption is not required.7. In transitioning from the original vendor specified inlet air temperature of 150'F to the current licensing limit of 148&deg;F, the inlet air vapor density is assumed to have remained unchanged.
This increases the inlet relative humidity causing a slight reduction in the air mass flow rate. Future validation of this assumption is not required.6. ANALYSIS 6.1 Tube Pitch The transverse and longitudinal tube pitches are not directly available from the coil data sheet.They can be estimated based on the geometry of the coil. Per Reference (7), the coil stack depth is 8.00 inches for the front coil and 12.00 inches for the back coil. Dividing the stack depth evenly between 4 and 8 tube rows yields a longitudinal (horizontal) tube pitch of 2.00 and 1.500 inches for the front and back coils respectively.
6.2 Coil Configuration The coil configuration for modeling coolers 1 (2)VY04A is selected based on the physical characteristics of the coil. There are no coils in the PROTO-HXTM library that exactly match the configuration of the VY coolers. The configuration "CF-9.05-3/4 J-A" shown in Figure 1 provides the closest match based on similarities of layout geometry:
staggered tube rows, horizontal tube pitch slightly greater than vertical tube pitch, similar fin height, identical fin thickness and similar fin pitch. The "CF-9.05-3/4 J-A" configuration also represents a relatively PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 7 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VElIUFED BY M. Aboye JOB NO. 31-003 CENT Commonwealth Edison PROECT LaSalle Station GL 89-13 Heat Exchanger Testing TInE VY Cooler Thermal Performance Model -- 1(2)VY04A compact coil which correlates well to the VY coils as evidenced in the coil photographs included as Attachment B.Figure 1 Coil Configuration CF-9.05-3/4 J-A--0.012 T)v 0O.774J 7 _CF-9.05- 3/ 4J- A PROTO-HXTM does not include spiral fin configurations in the analytical methodology employed.
However, for the given fin pitch, the difference in calculated fin surface area and outside heat transfer film coefficient between the VY cooler spiral fin configuration and the ,PROTO-HXTM circular fin configuration is negligible.
The negligible difference is illustrated further in Attachment K using a simplified area comparison.
6.3 Sensible Heat Ratio The value input in the model for the Sensible Heat Ratio (SHR) is used only when one of the"Constant Heat Load" calculation/extrapolation methods of PROTO-HXTM is used (i.e.,"Constant Heat and Cold Inlet Temperature" or "Constant Heat and Hot Outlet Temperature").
The SHR can be assigned any value between 0 and I and represents the fraction of the total specified (constant) heat load that is due to sensible cooling alone. An input of 1.0 in the SHR field tells PROTO-HX T M that the specified constant heat is 100% sensible heat with no condensation occurring.
Use of any value less than 1.0 presumes some knowledge as to what fraction of the specified heat load is due to condensation (i.e., latent heat transfer).
The value of SHR currently in the model is 1.0, but like any other model input, the SHR can be changed at any time.
PROTO-POWER CORPORATION cALc NO- 97-198 REV A PAGE 8 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECt LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A 6.4 Derivation of Benchmarking Inputs -- Front Coil The PROTO-HXTM model is benchmarked using the performance data provided by the cooler manufacturer.
In order to benchmark the model, the vendor specified conditions must be converted into appropriate units for PROTO-HXTM input. The only input requiring adjustment is the specified air-side flow rate of 27,450 scfm. PROTO-HXTM requires air-side flow rate to be given at actual inlet air conditions (units of acfmn).The correction of scfm to acfm is made as follows (holding mass flow rate constant for the defining case): mh = (scfm) x(psi) x6OiJ (acfmi) x (p.ac,.) x 60 minh J Equation (1)where: rh = mass flow (lbm/hr)scfm = volumetric flow rate at standard conditions (ft 3/min)Pst = standard density of 0.075 Ibm/ft 3 acfm = volumetric flow rate at specified (non-standard) conditions (ft 3/min)Pactua = density of dry air at specified inlet temperature and humidity (lbm/ft 3)Rearranging terms yields the following correction factor for converting scfm to inlet acfm: (acfm) = (scfm) x (Ptd)Equation (2)Local Standard Atmospheric Pressure To derive the dry air density for the inlet air conditions, the amount of moisture in the air and the local atmospheric pressure must be accounted for. Per Reference (13), local atmospheric pressure was accounted for by specifying a flow at standard density (27,450 scfm) as well as an PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 9 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye Jo0 NO 31-003 C(IEW Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A actual flow (28,500 acfm at 70'F and 40% relative humidity at site elevation).
The difference between the two flow rates will provide the assumed air density as follows: (pactuai) 
= (scfm) x (Pmd)(acfm)(27,450) x 0.07500 28,500= 0.0722  The local atmospheric pressure is found by iterative solution using Reference (14) as shown in Attachment H. Pressure input is varied with the specified temperature and humidity conditions held constant until a dry air density of 0.0722 Ibm/ft 3 is reached. The result of the iterative process is as follows: Given per Reference (13)Dry Bulb Temperature:
Relative Humidity: 70.00&deg;F 40.00%Derived above Dry Air Density;Derived per Attachment H Specific Humidity: Atmospheric Pressure: Dry Air Pressure: Vapor Pressure: Vapor Density: 0.0722 Ibm./ftA3 0.00638 lbmv/lbma 14.3150 psia 14.1697 psia 0.1453 psia 0.00046 1bm/ftA3 The result is that an atmospheric pressure of 14.315 psia at 70'F and 40% relative humidity will give the requisite air density.Actual Air-Side Flow Rate The next step is to define the actual air flow rate at the inlet conditions included by the vendor in the Reference (7) performance specification (Table 2). The moist air conditions corresponding to the vendor specified performance conditions are as follows: Given per Reference (7)Dry Bulb Temperature:
Wet Bulb Temperature:
150.00&deg;F 92.00&deg;F PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 10 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO-31-003 CLIENT Commonwealth Edison PROE LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I(2)VY04A Derived above Atmospheric Pressure: Derived per Attachment H Relative Humidity: Specific Humidity: Dry Air Pressure: Vapor Pressure: Dry Air Density: Vapor Density: 14.315 psia 12.18%0.02034 lbmv/lbma 13.8617 psia 0.4533 psia 0.06137 lbm/ftA3 0.001248 lbm/fW^3 The actual volumetric flow rate at vendor specified inlet conditions is then calculated as:____ 0.07500 _ 3m (acfin) = (scfln) x ) -(27,450) x -33,546 f mm (Pactai) 0.06137 Actual Tube-Side Flow Rate In accordance with Reference (7), both the front and back coil sections are double circuited (double serpentine) coils with 20 tubes per row. A plan view of this configuration is shown in Figure 2. Both the front and back coil sections have an equal number of open tube circuits'available to the incoming flow. The flow split between the coil sections, therefore, will be a function of the flow resistance of each coil with the majority of the flow going to the coil section that offers the least resistance to flow. By inspection, the majority of the incoming flow will go to the front coil due to the shorter length of tube and fewer tube bends. A quantitative derivation of the flow split is possible by accounting for the sources of flow resistance in each flow path.Given that the top and bottom and front and back coil sections are located in parallel, the total flow to the VY04A cooler splits four ways as follows: Qtotal = Qfront-top 
+ Qfront-bottom 
+ Qback-top 
+ Qback-bottom Equation (3)
PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 1 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIE Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing"tITLE VY Cooler Thermal Performance Model -- 1(2)VY04A Figure 2 Top View of Back and Front Coil Sections (Double Serpentine Tube Arrangement)
Air Flow Air Flow ]As given on page 3-4 of Reference (3), the relation between head loss (or differential pressure)across a flow path and flow is given as: AP oc KQ2 where: AP =K =Q -Equation (4)differential pressure resistance coefficient flow PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 12 OF 30 GROTON, CONNECTICUT ORICGNATOR L. Philpot D)ATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing WTLE VY Cooler Thermal Performance Model -- l(2)VY04A Given that the differential pressure across the coil sections will be the same and the symmetry of the tube flow paths between all coil sections (i.e., the same number of tube circuits in each coil section), the analysis of flow resistance reduces to a comparison of a single tube circuit in a front coil section to a single tube circuit in a back coil section.AP cc KFQF 2=K[3Q1 2 Equation (5)where: KF QF KB QB= front coil resistance coefficient
= front coil flow= back coil resistance coefficient
= back coil flow The resistance coefficient is a combination of straight tube length and tube bends as shown in Figure 2. The resistance coefficient for each tube can be expressed as: Ktube = Kstraight tube + Kbend Equation (6)where: K-straight tube KYbend straight length resistance 
[= fx (L/D)], Reference (3), page 3-4= close pattern return bend [= 50 x f], Reference (3), page A-29 Comparing the front and back coil sections in terms of straight length and bends for each tube gives the following per Figure 2: Front Coil Tube: Back Coil Tube: 2 straight lengths and I bend 4 straight lengths and 3 bends Expressing the front and back coil tube resistances in terms of Equation (6) gives the following:
KF = (2 x Kstraighttube) 
+ (1 x Kbend) = (2 x fx (L/D)) + (1 x 50 x f) = f(2L/D + 50) Eq. (7)KB = (4 x Kstraighttube) 
+ (3 x Kbend) = (4 x fx (L/D)) + (3 x 50 x f) = f(4LiD + 150) Eq. (8)
PROTO-POWER CORPORATION CALCNO. 97-198 RV A PAGE 13 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing MiLE VY Cooler Thermal Performance Model -- 1(2)VY04A Substituting into Equation (5) and canceling like terms: KFQF2 = KBQB2 Equation (9)(2L/D + 50)QF 2 = (4L/D + 150)QB 2  Equation (10)Given a straight tube length of 108 inches and a tube inside diameter of 0.527 inches yields the following after substituting and rearranging terms: r (108)) '71 (2)x (0)+ (50)QB L , (0.527)) -459.87]2 
= 0.69 Equation (.1)QF ((4)x (108) +(150) 1 To express the flow split as a function of the total flow, the ratio derived above is substituted into Equation (3) as follows (recognizing the symmetry of top and bottom coil sections):
Qtotal = Qfront-top 
+ Qfront-bottom 
+ Qback-top 
+ Qback-bottom 
= QF + QB Equation (12)_ QF + 2 1 + (0.69) = 1.69 Equation (13)QF QF QF QF -I 0.59 Equation (14)Q1.oal 1.69= -QF 0.59 = 0.41 Equation (15)Q.471, Q,ola, For the case where the cooler is supplied with 200 gpm, the flow split between the front and back coil sections will be: Front Coil Flow = (200 gpm) x (0.59) = 118 gpm Back Coil Flow = (200 gpm) x (0.41) = 82 gpm PROTO-POWER CORPORATION CALCNO. 97-198 REV A PAGE 14 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJEct LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A Summary of PROTO-HXTM Inputs for Model Benchmarkine Front Coil: Tube-Side Flow Rate Tube-Side Inlet Temperature Air-Side Flow Rate Air-Side Inlet Temperature 
-- Dry Bulb Air-Side Inlet Temperature 
-- Wet Bulb Atmospheric Pressure Back Coil: Tube-Side Flow Rate Tube-Side Inlet Temperature Air-Side Flow Rate Air-Side Inlet Temperature 
-- Dry Bulb Air-Side Inlet Temperature 
-- Wet Bulb Atmospheric Pressure 118 gpm 105lF 33,546 acfm 150&deg;F 92 0 F 14.315 psia 82 gpm 105 0 F (Function of front coil performance)(Function of front coil performance)(Function of front coil performance) 14.315 psia 6.5 Model Benchmarking Benchmarking Process Model benchmarking is performed to compare thermal performance as predicted by the model to thermal performance specified by the cooler vendor. A significant impact on the model predicted performance is the outside (air-side) heat transfer coefficient.
The benchmarking process adjusts the model correlation for outside heat transfer coefficient to match vendor performance data.An extensive source of information pertaining to the outside heat transfer coefficient for air coolers is provided by Reference (15). This widely-recognized publication provides heat transfer correlations for specific coil configurations.
The format used in Reference (15), and subsequently adopted by other researchers, is to provide a plot of the Colburnj-factor vs. Reynolds Number for each configuration.
Alternatively, to permit modeling of coils which do not adequately fit the library configurations and for which no test data correlation is available, PROTO-HXTM allows the generation of a coil unique formulation for outside heat transfer coefficient.
This is done through establishing a unique Colbumj-factor for the coil.
PROTO-POWER CORPORATION CALC NO. 97-198 REv A PAGE 15 OF 30 GROTON, CONNECTICUT ORIGINA T OR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CULwr Commonwealth Edison PROJECt LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A Reference (15) defines the Colbum j-factor as follows.Let: cpa = Specific heat of air (Btu/lbm-&deg;F) ka = Thermal conductivity of air (Btu/hr-ft-&deg;F) ma = Absolute viscosity of air (lbm/ft-hr) ra = Density of air (lbmft 3)Amin= Minimum air-side flow area (in 2)Aj= Frontal Area (in2)DH= Hydraulic diameter (ft)do= Tube outside diameter (in)j = Colbumnj-Factor NC = Number of coils per unit NL = Number of active tube rows Qa = Specified air flow rate (acfin)SL = Longitudinal Tube Pitch (in)ST= Transverse Tube Pitch (in)The Prandtl Number for air, Pra, (a dimensionless parameter), is given by: Pra -cpa /U.k,, Equation (16)
PROTO-POWER CORPORATION CALCNO. 97-198 REV A PAGE 16 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECt LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I(2)VY04A The mass flow rate of air per coil, Ma (lbl/hr), is calculated based on the input total air flow and the number of coils per unit: Ma -60pQ, NC Equation (17)The bulk-stream mass flux, G (Ibm / hr-ft 2), is: G = 144 Ma AMIN Equation (18)The Colbum j-factor is defined in terms of the Stanton Number, Sta, as: I=Sta pr,21 3 21~1p)P~3 Equation (19)Therefore, the outside heat transfer coefficient, ho (Btu/hr-ft 2-&deg;F), may be defined in terms of thej-factor: j G cpa o 2/3 Pr, Equation (20)Per Reference (15), the j-factor for the various coil configurations tested are provided as functions of the Reynolds Number based on hydraulic diameter, DH(in): i = f(Re.)where: Rea = G-DH Puo Equation (21)The standard air-side configuration for coil type CF-9.05-3/4 J-A, provided in PROTO-HX T M 's Library, was initially selected based on the physical similarities between the present coil and that represented by CF-9.05-3/4 J-A as described in Section 6.2. However, the heat transfer rate under design operating conditions using the standard configuration was significantly lower than the value specified by the manufacturer (see performance run in Attachment C). For this reason, PROTO-POWER CORPORATION CALCNO. 97-198 REV A PAGE 17 OF 30 -GROTON, CONNECTICUT ORIGINAIOR L. Philpot DATE 7/13/98 VE-RFIED BY M. Aboye Jo0 NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A a new curve relating the Colbum j-factor and Reynolds Number was generated according to the following procedure: " The slope of the linear standard curve was calculated.
* A new curve, parallel to the standard curve, was defined such that the new i-intercept is slightly lower." A design performance run was then executed using the new Colbum j-factor versus Reynolds Number curve, and the resulting heat transfer rate was compared to the manufacturer's value.* The above two steps were repeated until the calculated heat transfer rate closely matched the manufacturer's value.Front and Back Coil Considerations The unique configuration of 1(2)VY04 coolers with front and back coils in parallel for cooling water flow and in series for air flow creates a benchmarking challenge in three ways: ,. The cooling water flow split is derived analytically as demonstrated above and, due to the lack of flow measurement capability, cannot be verified.* The vendor specified performance data does not distinguish between front and back coil sections with regard to total heat transferred by the coil combination or the predicted cooling water outlet temperatures (i.e., what fraction of the total heat load is carried by each coil section).* The vendor specified performance data does not include air-side inlet conditions for the back coil. Inlet conditions for the back coil section must be derived based on the performance of the front coil section.The result of the unique challenges of the I(2)VY04 cooler configuration is that the model benchmarking process becomes iterative in nature and must rely on an assumption of similarity of front and back coil section j-factor corrections 
[Assumption (5)]. Accordingly, the benchmarking method discussed previously will entail the following additional considerations:
0 The front coil section is run with the standard Colbumrj-factor.
PROTO-POWVER CORPORATION CALC NO. 97-198 REV A PAGE 18 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A" Outlet conditions of the front coil section run are used to derive back coil section inlet conditions (i.e., back coil inlet relative humidity is based on front coil outlet temperature and a constant specific humidity across the front coil while back coil inlet air flow is adjusted as necessary to achieve the same mass flow rate as the front coil).* The back coil section is run with the standard Colburn j-factor." The combined heat transfer and cooling water outlet temperature are compared to that specified by the vendor.* Adjustments to both the front and back coil section are made and the process is repeated (the same Colburn j-factor adjustment made to both front and back coil sections).
* The process is repeated until a combined total heat transfer rate close to the specified heat transfer rate is achieved in conjunction with a combined cooling water outlet temperature close to the specified temperature.
The resulting relationship between Reynolds Number and Colburn j-Factor is represented by the following table and associated equation: Table 4: Reynolds Number and Colburn j-Factor Reynolds Number Colburn j-Factor (Standard)
Colburn j-Factor (Custom)1000 0.009 0.01360 8000 0.0044 0.00665 J = e[-1.9210 
-0.3441*Ln(Re)]
Equation (22)Equation (9) was added to the PROTO-HXTM Library for use in conjunction with Area Coolers 1(2)VY04A.
As noted in Assumption (3) and implemented above, the slope of the "Colburn j-factor vs.Reynolds Number" curve is assumed to be the same for the VY coolers and the standard coil represented by curve CF-9.05-3/4 J-A in the PROTO-HXTM "h-configurations" Library. This assumption is considered reasonable based on the following:
* there are only minor variations in the slope of different j-factor correlations; 
: and, PROTO-POWER CORPORATION CALCNO. 97_198 REV A PAGE 19 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I(2)VY04A there is only a slight variation in the air-side Reynolds Number between anticipated test conditions and the extrapolated accident conditions.
The only variation is expected to be caused by air inlet temperature variations (i.e., volumetric flow rate in cfm will be nearly constant, while air flow in acfm will vary with temperature and inlet humidity).
An excerpt from Reference (15), illustrating the Colbum j-factor relationship with Reynolds number, is included as Attachment D.6.6 Derivation of Back Coil Benchmarking Inputs The inlet relative humidity and dry air density for the inlet to the back coil section are derived based on the outlet temperature and specific humidity of the front coil section. The equations of Reference (14) are used with the results included in Attachment H.The inlet air flow rate (acfmn) to the back coil is iterated with subsequent runs of the back coil model until a value is reached that maintains constant mass flow rate through both coil sections.6.7 Effective Coil Finned Length Reference (20) identified the fact that the finned coil length exposed to air flow was less than that specified by the coil vendor in Reference (7). Model benchmarking used the vendor specified length to be consistent with the vendor specified performance.
The effective length is entered into the model for all subsequent analysis.
An effective coil finned length of 105.00 inches is used per Reference (20).6.8 Extrapolation Conditions The LaSalle Station Reference Conditions defined in Table 1 are slightly different than the vendor specified performance conditions listed in Table 2 and require conversion to units for input into PROTO-HX T M.Air-Side Pressure Air-side pressure should account for the local elevation above sea level. Chapter 26, Table LA, of Reference (16) provides elevation and standard atmospheric pressure data for the local area around La Salle.
PROTO-POWER CORPORATION CALCNO.97198 ROV A PAGE 20 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 cLIEr Commonwealth Edison PROJECt LaSalle Station GL 89-13 Heat Exchanger Testing TIME VY Cooler Thermal Performance Model -- l(2)VY04A Interpolating between data points to derive the pressure associated with the elevation of the VY coolers given by Reference (17) provides the following:
Elevation Pressure (feet above sea level) (psia)682 14.337 738 14.308 698 14.329 Reference (16)Reference (16)Interpolation between above points at VY elevation Per Reference (4), the coil pressure is -0.4 inches of water gauge. Using the density of water at 60'F, the specified pressure is calculated as illustrated below: Coil Pressure (inwg)-0.4 Water Density (lbm/ft 3)62.36445 Coil Pressure (psig)-0.014 Atm Pressure (psia)14.329 Coil Pressure (psia)14.315 This pressure matches the pressure derived from the original coil specification in Section 6.4.Air-Side Flow Rate In order for PROTO-HXTM to calculate the air mass flow rate for a given extrapolation condition, the inlet dry bulb temperature, total pressure, and relative humidity or wet bulb temperature must be specified.
The inlet dry bulb temperature and pressure for the LaSalle Station Reference Conditions are listed in Table 1. The inlet relative humidity is adjusted by holding the vapor density constant from the vendor specified condition to the LaSalle Station Reference Condition (i.e., 148&deg;F in lieu of 150'F).Given per Section 6.4 Vapor Density: Reference Condition Dry Bulb Temperature:
Atmospheric Pressure: Derived per Attachment H Wet Bulb Temperature:
Relative Humidity: 0.001248 1bm/ftA3 148.00&deg;F 14.315 psia 91.6 0 F 12.76%
PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 21 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB 31-003 CLIENT Commonwealth Edison pROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I (2)VY04A Since fans are constant volume equipment, the air volumetric flow rate of 28,500 cfm specified in References (18) and (19) remains the same for all coil outlet conditions.
The air mass flow rate through the coil, however, will vary with the temperature of the air going through the fan (i.e., at coil outlet temperature).
Deriving the inlet air flow rate for input to PROTO-HXTM requires an iterative solution as follows: " take an initial guess at the coil outlet air temperature at the same specific humidity as the coil inlet;* calculate the dry air density at the selected coil outlet air temperature;" calculate the coil inlet air flow rate by multiplying the fan capacity (cfm) by the ratio of the coil outlet dry air density to the coil inlet dry air density (to maintain constant mass flow across the coil) [Equation (2)];* run the model with the inlet air flow rate derived above;* check the predicted coil outlet air temperature; and" repeat the process (substituting the predicted coil outlet air temperature for the initial guess)until the coil outlet air temperature does not change from one iteration to the next The iteration process described above was completed twice for this model for a clean (f-= 0.0)and service (f= design) condition with results as follows: Clean: (cflm.) =(cfmo&deg;,) x (P..',) -(pin)(Pc.,x (cfmou, x x (pi")Service: (28,500) x (0.066368695)
(0.061575103)
(28,500) x (0.066134085)
(0.061575103)
= 30,718.00 (Fan Temperature 
= 104.11)(cfmin) == 30,610.12 (Fan Temperature 
= 106.11)Summary of PROTO-HXTM Inputs for Extrapolation to Reference Conditions The Extrapolation conditions are defined as the vendor data sheet conditions without high energy line break modified for ultimate heat sink temperature and room limiting temperature per the LaSalle Station UFSAR Reference (4).
PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 22 OF 30 GROTON, CONNECTICUT ORIGNATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROIECr LaSalle Station GL 89-13 Heat Exchanger Testing TInLE VY Cooler Thermal Performance Model -- 1(2)VY04A The required PROTO-HXTM inputs for these conditions are as follows: Extrapolation 
-- Front Coil Tube-Side Flow Rate Tube-Side Inlet Temperature Air-Side Flow Rate Air-Side Inlet Temperature 
-- Dry Bulb Air-Side Inlet Humidity Atmospheric Pressure Extrapolation 
-- Back Coil Tube-Side Flow Rate Tube-Side Inlet Temperature 118 gpm 100&deg;F (varies with temperature) 148&deg;F 12.76%14.315 psia 82 gpm 100IF It should be noted that the front coil inlet air flow is dependent upon the air temperature exiting the back coil while the back coil inlet air conditions are dependent upon the front coil outlet air conditions.
Inlet air flow is calculated from Equation (1) initial estimates of back coil outlet temperature (fan temperature).
The back coil inlet air flow rate is derived to ensure the air mass flow rate through the back coil is the same as the air mass flow rate through front coil. The resulting back coil outlet temperature is then compared to the initial estimate.
An iterative process is used to ensure all flows are balanced accordingly.
Derivation of the necessary air properties is included in Attachment H.6.9 Thermal Margin Assessment The available thermal margin is defined as the difference between the available and the required heat removal rates at reference conditions.
The maximum available heat removal rate (qclean)is calculated using the benchmarked PROTO-HXTM model and the inlet conditions defined in Section 6.8 with zero fouling. By comparing the available heat removal rate calculated with zero fouling to the required heat removal rate, the maximum available margin is determined.
A similar comparison is made between the required heat load to the available heat load at design fouling conditions (q.service)" For the purposes of this thermal margin assessment, thermal margin is defined as follows: Margin (BTU / hr) = q available 
-q required Equation (23)
PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 23 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIEDBY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A Margin (%) =(q availbe -qrequired ) x 100 Equation (24)K qrequired J where: qavailable 
= the predicted heat capacity of the cooler at the specified conditions (BTU/hr)qrequired 
= the heat capacity required of the cooler to fulfill design basis requirements (BTU/hr)6.10 Limiting Cooling Water Flow Analysis In support of the LaSalle Station efforts to re-balance the CSCS Equipment Cooling Water System, specification of a minimum acceptable cooling water flow to the VY coolers is desired.For conservatism, the design fouling factors associated with the limiting flow analysis are increased to 0.002 on both the tube and air sides of the cooler. Increasing the design fouling factors increases the fouling margin of the cooler at the reduced flow rates.Limiting flows are established by iterating with the performance model. The cooling water flow rate is incrementally reduced with each iteration until the target thermal margin is achieved.
For the case of 1(2)VY04A, the target thermal margin is approximately 30% with the increased design fouling factors.6.11 Fouling Sensitivity Analysis To assess the sensitivity of the 1(2)VY04A coolers to tube-side fouling accumulations, a series of iterations are performed.
With each iteration, the design tube-side fouling factor is incrementally increased from a value of 0.0000 to 0.0040. The heat removal capability resulting from each fouling increment is compared to the required heat load to assess the thermal margin.Thermal margin is calculated using Equations (10) and (11).7. RESULTS 7.1 Model Benchmarking The first model case was based on the standard CF-9.05-3/4 J-A configuration available from the PROTO-HXTM library. The results of this initial benchmarking case are presented in Table 5.The PROTO-HXTM reports associated with the initial benchmark case are included as Attachment C.
PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 24 OF 30 GROTON, CONNECTICUT OIGINA'rOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Comrnmonwealth Edison PROJEcr LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A Table 5: Initial Benchmark Case -- Standard CF-9.05-3/4 J-A Configuration Tube Outlet Temperature Heat Transfer Rate (CF) (BTU/hr)Coil Vendor Data P-HX Predicted Vendor Data P-HX Predicted Front Not specified 116.13 Not specified 651,158 Back Not specified 116.61 Not specified 471,786 Total 117.31 116.25 1,194,000 1,122,944 Design Variance -- -0.90% -- -5.95%(I) Combined outlet temperature is the flow weighted average of the front and back coil sections (front coil = 0.59 and back coil = 0.41 per Equations (14) and (15)).Based on the results of the initial benchmark case with the standard CF-9.05-3/4 J-A configuration, another case was completed using a customized Colburn J-Factor.
This case demonstrated adequate benchmarking of the model to the vendor specified performance.
A subsequent comparison run was made following the adjustment of the coil finned length to match the length identified in Reference 
: 20. The results of the final benchmarking cases are presented in Tables 6 and 7. The PROTO-HXTM reports associated with the final benchmarking cases are included as Attachment E.Table 6: Final Benchmark Case -- Customized Colburn J-Factor Tube Outlet Temperature Heat Transfer Rate (CF) (BTU/hr)Coil Vendor Data P-HX Predicted Vendor Data P-HX Predicted Front Not specified 117.75 Not specified 748,549 Back Not specified 115.94 Not specified 445,586 Total 117.31 117.01 1,194,000 1,194,135 Design Variance --- 0.26% --+ 0.011%(I) Combined outlet temperature is the flow weighted average of the front and back coil sections (front coil = 0.59 and back coil = 0.41 per Equations (14) and (15)).Table 7: Final Benchmark Case -- Effective Finned Tube Length PROTO-POWER CORPORATION CALCNO. 97-198 REV A PAGE 25 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJECt LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A Tube Outlet Temperature Heat Transfer Rate (OF) (BTU/hr)Coil Vendor Data P-HX Predicted Vendor Data P-HX Predicted Front Not specified 117.62 Not specified 740,828 Back Not specified 116.01 Not specified 447,161 Total 117.31 116.96 1,194,000 1,187,989 Design Variance -- -0.30% -- -0.50%(I) Combined outlet temperature is the flow weighted average of the front and back coil sections (front coil = 0.59 and back coil = 0.41 per Equations (14) and (15)).7.2 Thermal Margin Analysis Prior to defining margin, the predicted heat transfer capacity of the cooler (qavailable) is defined.The predicted heat transfer capacities at LaSalle Station Reference Conditions for both clean (zero fouling) and service (design fouling) conditions are summarized in Table 8.Table 8: Heat Transfer Capacity Coil Heat Transfer Capacity Total Heat Transfer Capacity'Conditions (BTU/hr) (BTU/hr)Clean (f = 0) (front) 854,494 1,246,474 (back) 391,980 Service (f = 0.0015) (front) 752,589 1,185,370 (back) 432,781 The thermal margin assessment relates the predicted capacity of the cooler on clean and service conditions to the required capacity under reference conditions.
The comparison is provided in Table 9. The PROTO-HXTM reports associated with the thermal margin assessment are included as Attachments F and G for zero and design fouling conditions, respectively.
PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 26 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED [Y M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJEct LaSalle Station GL 89-13 Heat Exchanger Testing nTIE VY Cooler Thermal Performance Model -- 1(2)VY04A Table 9: Thermal Margin at LaSalle Station Reference Conditions 
-- I(2)VY04A qrequired qavailable Margin Margin Conditions (BTU/hr) (BTU/hr) (BTU/hr) (%)Clean (f = 0) 633,288 1,246,474 613,186 96.83%Service (f = 0.0015) 633,288 1,185,370 552,082 87.18%7.3 Limiting Cooling Water Flow Rate Analysis The limiting cooling water flow analysis calculated the lowest possible cooling water flow that would provide a thermal margin of approximately 30% +/- 5% for the l(2)VY04A coolers with an adjusted design fouling of 0.002 air-side and 0.002 tube-side.
The results of the iterations to identify the limiting flow rate are summarized in Table 10. The PROTO-HX T M reports associated with the limiting flow analysis are included as Attachment I.Table 10: Limiting Cooling Water Flow Rate at Reference Conditions The uncertainty in the analytical methodology used to identify the limiting flow for 1(2)VY04A is presented in Attachment J. The result of the uncertainty assessment is that the uncertainty in the PROTO-HXTM extrapolated heat transfer rate ranges from +/- 5.81% to +/- 6.99% for the front coil and +/- 4.33% to +/- 6.36% for the back coil for the ranges of cooling water flow evaluated.
An uncertainty of+/- 7.00% and +/- 6.40% is used for the front and back coils respectively to conservatively bound the analysis of Attachment J. The combined analytical uncertainty for the two coils together is taken as the square root of the sum of the squares of the front and back coil contributions.
Accordingly, the overall analytical uncertainty for 1(2)VY04A is expressed as: Uanalytical
-(u 1 Y +(Ubak)Uanalytical 
= /(0.070) + (0.064)Y PROTO-POWVVER CORPORATION CALC NO. 97-198 REV A PAGE 27 OF 30 GROTON, CONNECTICUT ORIGUNATOR L. Philpot DATE 7/13/98 VERFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A U analytical
= 0.095 Uanalyfical , 9,5%The adjusted thermal margin is calculated using Equation (11) after subtracting the uncertainty from the available heat rate. The results are presented in Table 10 below.Table 11: Limiting Cooling Water Flow Rate at Reference Conditions (f= 0.0020/0.0020)
Limiting qrequired qavailable Nominal Adjusted Cooler Flow Rate (BTU/hr) (BTU/hr) Margin (%) Margin (%)1(2)VYOIA 66.5 633,288 740,535 107,247 16.93%7.4 Fouling Sensitivity Analysis The results of the fouling sensitivity analysis are included in Table 11. The PROTO-HX T M reports associated with the fouling sensitivity analysis and a graphical presentation of the results are included as Attachment M. It should be noted that neither the Table below or the figure in Attachment M have taken analytical uncertainty into account since the intent of this exercise is to assess the change in thermal margin (i.e., the slope of the curve in Attachment M). Analytical uncertainty treated as a bias on the results will have a negligible effect on the slope of the curve.Consideration of uncertainty would, however, change the point at which a thermal margin of 0%is reached.Table 12: Fouling Sensitivity Analysis -1(2)VY04A at 66.5 gpm Air-Sidef Tube-Sidef Required q Available q %Margin 0.0020 0.0000 633,288 544,475 324,952 869,427 37.29%0.0020 0.0020 633,288 487,103 331,168 818,271 29.21%0.0020 0.0040 633,288 440,315 331, 663 771,978 21.90%
PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 28 O 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB No 31-003 CLIENT Commonwealth Edison PROJEcT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A 8. CONCLUSIONS Two models for the LaSalle County Station Units 1 & 2 NE Cubicle Area Coolers were developed using PROTO-HX T M Version 3.01. The models were benchmarked and validated using the performance specifications provided by the cooler vendor. The close correlation with vendor specified and model predicted thermal performance confirms that the models are to be considered acceptable for use in the GL 89-13 heat exchanger testing program and related performance analysis.The available thermal margin for the coolers has been defined for the nameplate rated flow of 200 gpm and for a reduced flow rate of 66.5 gpm in support of service water system flow requirements.
Inclusion of a conservative assessment of the uncertainty in the analytical methods of PROTO-HX T M has provided high confidence in the thermal margins defined by the model for all cases.The front coil model database is saved under file name vy-04a-f.phx, with a file size of 1,409,024 bytes, and a file date and time of 7/10/98 at 4:09:12 pm. The back coil model database is saved under file name vy-04a-b.phx, with a file size of 1,409,024 bytes, and a file date and time of 7/10/98 at 4:09:30 pm. The saved models are set up to run the 66.5 gpm case with adjusted design fouling factors of 0.002 air-side and 0.002 tube-side.
The database files are included as Attachment N.9. REFERENCES
: 1. Heat Exchanger Thermal Performance Modeling Software Program PROTO-HXTM Version 3.01 Software Validation and Verification Report (SVVR) SQA No. SVVR-93948-02, Revision E, dated 11/5/97 2. LaSalle Calculation L-00 1024, Revision 2, LPCS Pump Cubicle Cooler Ventilation System 3. Crane Technical Paper No. 410, Flow of Fluids Through Valves, Fittings, and Pipe, 25'h Printing, 1991, Crane Company 4. LaSalle Station Updated Final Safety Analysis Report, Table 3.11-7, Harsh Environment Zone H5 -- Bounding Environmental Conditions for HELB Areas in the Reactor Building (Attachment A)
PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 29 OF 30 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 7/13/98 VERIFIED BY M. Aboye JOB No. 31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A 5. LaSalle Station Updated Final Safety Analysis Report, Section 9.2.1, ECCS Equipment Cooling Water System (excerpt -Attachment A)6. LaSalle Station Updated Final Safety Analysis Report, Section 9.2.6, Ultimate Heat Sink (excerpt -Attachment A)7. Drawing 28SW404543, "CSCS Equipment Area Cooling Coils," original issue, 7/21/76 (Attachment A)8. LaSalle Calculation L-000581, Revision 0, Evaluation of the CSCS Cubicle Area Coolers Operation with a Reduced Cooling Water Inlet Temperature
: 9. Drawing M-87, Sheet 3, "CSCS Equipment Cooling Water System," Revision F dated 5/4/88 10. Drawing M-134, Sheet 3, "CSCS Equipment Cooling Water System," Revision F dated 5/25/82 11. Bahnson Drawings 2605-1-11,12,13, & 14 (Attachment A)12. Standards of the Tubular Exchanger Manufacturers Association (TEMA), Seventh Edition, 1988 13. Specification Number J-2582, Heat Exchange Coils and Cabinets, La Salle County -Units I and 2, Revision 1, dated 1/16/75 (excerpt -Attachment A)14. Proto-Power Calculation 96-069, Revision -, Fluid Properties 
-Moist Air -Range 80 to 300OF 15. Compact Heat Exchangers, W.M. Kays and A.L. London, McGraw Hill, Third Edition, 1984. (excerpt -Attachment C)16. 1997 ASHRAE Handbook -- Fundamentals, inch pound Edition, American Society of Heating, Refrigerating and Air Conditioning Engineers, Inc., Atlanta, GA (excerpt -Attachment A)17. Drawing M-1366, Sheet 2, "Reactor Building Ventilation System -- Elevation 694'-6" West," Revision F dated 5/17/82 PROTO-POWER CORPORATION CALC NO. 97-198 REV A PAGE 30 OF 30 GROTON, CONNECTICUT ORIGINAToR L. Philpot DArE 7/13/98 VERIFIED BY M. Aboye JOB NO. 31-003 CLIENT Commonwealth Edison PROJECr LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY04A 18.19.20.Drawing M-1464, "CSCS Equipment Cooling System," Revision B dated 5/12/88 Drawing M-1465, "CSCS Equipment Cooling System," Revision B dated 5/12/88 Coil Walkdown Data, CoinEd NDIT No. LS-0847, dated 7/6/98 (Attachment L)
Attachment A to Proto-Power Calculation 97-198 Revision A Proto-Power Calc: 97-198 

==Attachment:==

A it Rev: A Page I of .--/oh118 LSCS-UFSAR TABLE 3.11-7 HARSH ENVIRONMENT ZONE H5 -BOUNDING ENVIRONMENTAL CONDITIONS FOR HELB AREAS IN THE REACTOR BUILDING Temperature (OF)212 150 150 Pressure 7 in. W.G.*7 in. W.G.Atmospheric Relative Humidity Steam 0-6 hr 100%90%Duration Radiation 6-12 hr 12 hr to 100 days 1 x 10 7 rads gamma (integrated)
NOTE: The bounding radiation dose >- (normal service radiation dose integrated over 40 years + accident dose + 10%margin on the accident dose per IEEE 323-1974, Section 6.3.1.5)*Transient peak pressure of 40 psig can occur within the first 10 seconds of the line break event. However, venting and subsequent depressurization to atmospheric pressure occurs very rapidly.Proto-Power Calc: 97-198 

==Attachment:==

A it Rev: A Page 2 of I& [TABLE 3.11-7 REV. 0 -APRIL 1984 LSCS-UFSAR
: 4. RHR pump seal cooler ('A' and 'B' RHR pumps only) -20 gpm 5. LPCS pump motor cooling coil -7.4 gpm 6. northwest cubicle area cooling coil --150 gpm 7. southwest cubicle area cooling coil -150 gpm 8. northeast cubicle area cooling coil -200 gpm 9. southeast cubicle area cooling coil -180 gpm 10. emergency makeup to fuel pool -50 gpm minimum 11. containment flood -,300 gpm maximum.b. System classifications are as shown in Section 3.2. All portions of this system are protected from the effects of tornados, missiles, pipe whip, and flooding.c. To meet single failure criteria, the CSCS-ECWS for each unit is designed as three independent subsystems, one of which is shared between units (Drawing Nos. M-87 and M-134).d. Strainers are provided to prevent plugging of cooled component heat transfer passages.
All strainers include provisions for backwashing without significantly affecting system operation.
Organic fouling of heat transfer surfaces will be minimized by the chemical feed system which will treat the service water tunnel inlet flow with oxidizing biocides.
However, the chemical feed system should not be considered auxiliary equipment required for the CSCS-ECW systems to perform their function.
Therefore, the operability of the CSCS-ECW systems should not be tied to the operability of the chemical feed system. Connections and isolation valves are also provided immediately upstream and downstream of each cooled component for injection and circulation of biocidal agents, if necessary.
: e. To detect leakage of radioactivity to the environment, radiation monitors are installed in the CSCS-ECWS immediately downstream of cooled components that contain radioactive fluids. The CSCS-ECWS discharge lines from these components are capable of remote madual isolation from the main control room.f. Design of system piping and components is based on a 40-year life.Exterior surfaces of all buried system piping is protected by bituminous coatings and wrappings and provisions for cathodic protection are installed where such protection is found to be required based on electrical potential measurements.
The design of all system piping includes a corrosion allowance of at least 0.08 inches.Proto-Power Caic: 97-198 

==Attachment:==

A kA Rev: A Page 3 of 4T 9.2-2REV.
10 -APRIL 19 LSCS-UFSAR the normally closed portions the integrity and operability are checked.9.2.6 Ultimate Beat Sink The ultimate heat sink (UHS) provides sufficient cooling water to permit the safe shutdown and cooldown of the station for 30 days with no makeup for both normal and accident conditions.
9.2.6.1 Design Bases 9.2.6.1.1 Safety Design Bases The ultimate heat sink has the following design bases: a. to provide sufficient water volume permitting a safe shutdown and cooldown of the station for 30 days with no water makeup for both normal operating and accident conditions permissible water temperature supplied to the-6plant-is taken as 1000 F;b. to withstand the most severe postulated natural phenomenon as discussed in Chapter 2.0;c. to withstand the postulated site-related incidents as discussed in Subsection 2.5.5; and d. to provide water for fire protection equipment.
A more detailed physical description of the ultimate heat sink is provided in Sections 2.4 and 2.5.9.2.6.1.2 Power Generation Design Bases The ultimate heat sink, as a safety system, is not used during normal plant operations.
Therefore, the ultimate heat sink has no power generation bases.9.2.6.2 System Description In the unlikely event that the main dike is breached, the cooling lake for the La Salle County Station is designed to hold 460 acre-feet of water with a surface area of 83 acres. This remaining water constitutes the ultimate heat sink for the station, and has a depth of approximately 5 feet and a top water elevation established at 690 feet. Figures 2.4-4 and 9.2-1 illustrate the physical layout and area capacity of the ultimate heat sink.9.2.6.3 Safety Evaluation The station's ultimate water requirements (Units 1 and 2) in gpm are summarized below.*Proto-Power Calc: 97-198*Attachmnent:
A Rev: A Page 4 of IT 9.2-18 REV. 0 -APRIL 1984 
*1**~.4, ~J or lu 1 MATIERIAL S~PECIFICATIONS TUOi5-10.D.
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GENERAL QUALITY ASSURANCE PROCEDURE CECO[jREK&#xfd;,,LUNDY L~~n.N.NWMuMEu TITLE & APPROVAL PAGE hA. r. M.. --A"SAFETY RELATED ITEMS ARE PART OF THI S SPECIFICATION" 4-Client CECO Specification Title Specification Number Project Identification Heat Exchange Coils and Cabinets J-2582 La Salle County -Units 1 and 2 Project Number DeDa rtment 4266-00/4267-00 Mechanical/RVAC YEVI DATE PREPARER APPROVER IPURPOSE OF ISSUE I 1-16-75 fC(~1~~v)~
-'-Issue to CECO for bids.ver Calc: 97-198 it: AI, Page 8 of .Od Proto-Po Attachme Rev: A ife-' I CSCS Eqpt Function or Service ...........
Equipment Numbers .............
Safety related or Nonsafety related (SR or NSR) ...........
403. PERFORMANCE DATA (HEAT EXCHANGE"Con t.r~o Auxiliary Electric Primary Contain-CSCS Eqpt.I Area 1nnlOn CSCS Eqpt.Area Coolin2 Area Cooling.-.Vent *----n Cooling OVC02AA OVEOIAA 1VP03AA 1VYOIA 1VY03A 1VY04A OVCO2AB OYEOIAB IVP03AB IVY02A 2VY03A 2VY04A 2VP03AA 2VYOIA _2VP03AB 2VYO2&#xfd;A 403.-a COIL CABINETS)1 Mode of Operation 
........... 
...a. Entering Air Dry Bulb ...... (-F)b. Entering Air Wet Bulb ..... (OF)c. Leaving Air Dry Bulb ....... (OF)d. Leaving Air Wet Bulb .......(OF)e. Actual Air Quantity at 7 0 0F,-40% RH and Site Elevation 3............... 
...... (ft /min)f. Standard.
Air Quantity at 075, lb/ft 3  ....... ,(Std ftj/minY)g. Cooling Medium .................
: h. Evaporator Refrigerant Tempera-.ture ....................... (OF)i, Entering Water Temperature.(0 F)j. Maximum Water Quantity(gal/min)
: k. Minimum Total Heat Exchange Capacity ............... (Btu/h)1. Minimum Sensible Heat Exchange Capacity ............... (Btu/h)m. Maximum Coil Face Velocity....................... (ft/min)SR.Cooling 81.8.63.1.52.8 26340 25380 R-22 42 SR Cooling 81.9 63.2 53.2 31300 30100 R-22 42 NSR Cooling 135 92 65 63 50000 48150 Chilled Water 46 1200 6.55x 106 3.63x10 6 600 SR and ASME III Cooling 150 110 SR and SR and ASME III !ASME III 110 110 Cooling 150 Cooling 150 0 10~1 0.00" 18000 17330 Water 105.150.748,700 748,700 700 26400 25420 Water 105.220.1.1 x 10 6 1. 1 X 106 700&#xfd;8500 27450 dater 105.40.19 x Add. 1 Add. 1 Add. I Add. I"%W CLI 797,000 725,000 600 936,000 847,000 600 L.19 x 10 6 700 26.10 I 997 ASIIRAE Fundamentals-Iuaridbo 0 C Table IA Hleating and Wind Design Conditions-Uni1,ed StaCes Ei". StIP Station WMO' Lit. Long. ft pria Date WestI PInm Bezch GEORGLA 4JthanB Aihnts Auigl'so Brunswkk Columbus.
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==Attachment:==

A -W Rev: A Page 10 of I1-it Phys'sical Properties of' MN:teriaks
'&#xa2; fie , ateri~l Elescripion 1 t0.Ahllntmitwoi(allot'y I I( 00) 0.21 4* Ali:,nmIuu i owt z l~le Oat.m Pa I I Table 3 Properties (if Solids cific lit, I)Deusity., Tl'Ierinal CondulIs itily.lF oll'' Ilu/l-fl-'F h, 17t 1 2$" it (76%7 Cu, 22% Zn. 2% All Asbtit)Sl' Fiiber Insulialull Ashes, wood Asphalt Bakelite Dell riwccal rBisnmuth tin liick, building 0.02Y'0.20'0.20'0.221'0.335" 0.OR61S (I22)0.0401*0.2" SO1" 1501 401" 112'81'3 0 097" 0.04 1' (122)0.43'9.7 r cnc m 36.3 Ensi.si vil l IRLaio i .Sitrrl-ce 
(:'imdiriritr 0 LY<*0.932 0.030" Ilighly polished 0.03.3 Hlihly polished 0.02" 0.81" 37.6'04'Brass: Red (85% Cu, 15% Zn)Yellow (65% Cu. 35% Zn)Fronze Cadmium Carbon (gas retort)Cardboard Cellulose Cement (portland clinker)Citalk Charcoal (wood)Chrome brick 0.09'0.090 0,104'0.0551 0.174 0.321, 0.9161 0.215'0.20'o0.17 548v 519'530Y 540'87'69" 17" (32)a.o' (2)0.033'0.0 17'0.48'0.03' (392)0.67" 3.4'120'141''5" zoo'0.34*About 250"F I Clay 0.22r 63'Coal 0.3b 90' 0.098' (32)Coal tars 0.395(104) 75h 0.07h Coke (petroleum, powdered) 0.36h (752) 62" 0.55k (752)Concrete (stone) 0. 156" (392) 1446 0.54h Copper (electrolytic) 0.092v 556" 227' 0.072' Commercial.
shiny Cork (granulated) 0.485' 5.4 (0.028' (23)Cotton (fiber) 0.319% 95' 0.024u Cryooit (AIF,- 3NaFn 0.253" 1811, Diamond 0.147h 151, 277 Eann (dry and packed) 95' 0.037' 0.4O *20.61 0.03" Fhreclay brick 0.198b (212) 112' 0.58h (392) 0.750 At 1832&deg;F Flhrspar (CaF 2) 0.21" 199' 0.63" Genman silver (nickel silver) 0.09, 5451 199 0.135, Polished Claw. C'awua (soda-tnie) 154' 0591(200) 0.940 Smooth Flint Ied) 0.1 117h 267" 0.79" Heasrsistamit 0.20' 139t 0.59' (200)-Wool 0.157b 3.25' 0.022e Gold 0.03120 1208" 172' 0.02? Highly polished Graphite Powder 0.165* 0.1060 Impenriou 0.16" 117' 751 0.75'Gypsum 0.2.59 78b 0.25 0.903b On a smooth plate Hemp (Fiber) 0.323" 93" Icke: 32*? 0.487T 57.5" 1.3" 0.95'-4*F 0.465' 1.410 Iron: Cast 0.12v (212) 27.6h (129) 0.435h Freshly tunned Wrought 485b 34.9b 0.94' Dull. oxidized Lead 00309W 707' 20-1'1 0.2R4 Gray. oxidized Leashes (sole) 62.4' 0.09?g Licstone 0.217" 103", 0.54" 0.36" to 0.90 At 145 to 38(0F Linen o.05" Lithmirge (lead monoxide) 0.0551 490P Magnesia; Powdertd 0.234h (212) 49.7" 0.35" (117)Light carbonate 1.0" 0.034" Magnesite brick 0.222" (212) .58" 2.2" (400)Magnesium Marble Nickel, polished Pai's' White lacquer White enamel Black lacquer Black shellac Flat black lacquer A I uniiiuut lacquef 0.241" 0.21" 0 105l 108, 162" 551, 34.4" 0.15u 0.55" 0.931'0.045, 1.80" 0.91" 0.80" 0_91 0.96'0.319 sxidized E Illt gray, pklkshed Flectroplaird On rough plait: ,M atie" finislh 63" On rough plate*Data suatce unknown.NOIC-: I er r OOIII lenipettuve uniless otlierwise noted in parent eir 2 %isprr'tmript lette, ifdiaicte data toucr. Iront the sttctIO Onk PRuaer 6-k,-. c: o-I r-Attachment B to Proto-Power Calculation 97-198 Revision A Proto-Power Caic: 97-198 

==Attachment:==

B Rev: A Page 1 of 2 S Page No.09122/92 I LA SALLE COUNTY STATION HEAT EXCHANGER (WATER TO AIR)DATABASE EQUIPMENT NUMBER/NAME IVY04C LPCS/RCIC COOLER B P PHOTO INSPECT A H STORAGE DATE 5 0 LOCATION E .09/22/92 N T BTNJXAPSHOI HXNI GENERAL APPEARANCEfltf...l*VERY CLEAN. NO DEBRIS.TUBE CONDITION NO DAMAGE. NOTICED.FINS CONDITION CLEAN, NO DEBRIS. A FEW FINS BENT.CORRECTIVE ACTIONS DErFECrfS RECOMMENDED ACTUAL NONE NONE NEEDED N/A tcu 0 to 0 06 0 k&#xfd;N&#xfd;6qc 16dtrr s i?, i1Hc tic. ccrtrr%4f Attachment C to Proto-Power Calculation 97-198 Revision A Proto-Power Caic: 97-198 

==Attachment:==

C Rev: A Page 1 of 14 08:17:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/10/98 I[ Air Coil Heat Exchanger Input Parameters nlit DQy unltbi-, TeTmpI Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperatur Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 33.524-6700 acfif 150.00 OF 92.00 OF OF OF Tube-Side 18.-00 gpm 105.00 &deg;F Tube Fluid Name Tube Fouling Factor Air-Side Fouling Fresh Water 0.001500 0.000000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins CF-9.05-3/4J A j = EXP[-2.3333 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ftV.F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-&deg;F) 108.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 20.00 0.5270 0.6250 2.000 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

C Rev: A Page 2 of 14 08:17:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/10/98 ComEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (OF)Air Dry Bulb Temp Out (OF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (OF)Wet Bulb Temp Out (OF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm) 118.00 Air Flow (acfmn) 33,546.00 Tube Inlet Temp (&deg;F) 105.00 Air Inlet Temp (OF) 150.0 Inlet Relative Humidity (%) 0.00 Inlet Wet Bulb Temp (OF) 92.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-198 

==Attachment:==

C Rev: A Page 3 of 14 08:17:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/10/98 A .1 Extrapolation Calculation Summary I;*1 I Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Vise (lbm/ftrhr)
Density (lbml/ff)Cp (BTU/lbm 0'F)K (BTU/hr-ft-&deg;F)
Air-Side 123,544.84 150.00 128.93 Tube-Side 58,613.21 105.00 116.13 Tube-Side hi (BTU/hr fl 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft 0-&deg;F)Tube Wall Resistance (hr- ft.&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr. ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)2,952.05 651,158 651,158 10MU" Extrapolation Calculation for Row l(Dry)1I Air-Side Mass Flow (lbm/hr) 123,544.84 Inlet Temperature (OF) 150.00 Outlet "emperature (OF) 143.83 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 146.92 Skin Temperature (OF) 124.56 Velocity *** 6,255.18 Reynold's Number 2,270 Prandtl Number 0.7252 Bulk Visc (lbm/ft-hr) 0.0492 Skin Visc (lbmrft-hr)
Density (lbm/ft 3) 0.0620 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr-ft-&deg;F) 0.0163 Tube-Side 58,613.21 110.48 117.00 113.74 118.70 2.17 14,855 3.8824 1.4299 1.3631 61.8061 0.9988 0.3679 Tube-Side hi (BTU/hr-ft 2.&deg;F) 778.41 j Factor 0.0068 Air-Side ho (BTU/hr ft 2-&deg;F) 12.64 Tube Wall Resistance (hr-ftl 2.F/BTU 0.00024732 Overall Fouling (hr-ft 2-F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-0 F)Effective Area (fV)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.83 738.01 32.98 190,706 0.9200 190,706 Proto-Power Calc: 97-198 

==Attachment:==

C Rev: A Page 4 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:17:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/10/98 Extrapolation Calculation for Row 2(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Vise (lbm/ftrhr)
Density (lbm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 123,544.84 143.83 138.51 0.0203 0.0203 141.17 121.83 6,255.18 2,286 0.7257 0.0488 0.0626 0.2402 0.0162 Tube-Side 58,613.21 109.65 115.27 112.46 116.77 2.17 14,669 3.9365 1.4481 1.3885 61.8248 0.9988 0.3674 Tube-Side hi (BTU/hr ft 2.&deg;F) 772.57 j Factor 0.0068 Air-Side ho (BTUihr-ft 2-OF) 12.60 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr- ft 2-F/BTU) 0.02228812 U Overall (BTU/hr'ft 2-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.81 738.01 28.54 164,550 0.9203 164,550&#xfd;,n&#xfd;Vm Extrapolation Calculation for Row 3(Dry)II I.Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (lbm/ft-hr)
Density (Ibm/ft3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft.&deg;F)
Air-Side 123,544.84 138.51 133.31 0.0203 0.0203 135.91 116.99 6,255.18 2,302 0.7262 0.0485 0.0631 0.2402 0.0160 Tube-Side 58,613.21 105.00 110.48 107.74 112.05 2.17 13,990 4.1470 1.5184 1.4539 61.8916 0.9988 0.3657 Tube-Side hi (BTU/hr.ft 2-F) 753.48 j Factor 0.0068 Air-Side ho (BTU/hr-ft2-&deg;F) 12.57 Tube Wall Resistance (hr-f12- F/BTU 0.00024732 Overall Fouling (hr-ft 2 0-F/BTU) 0.02228812 U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.77 738.01 28.01 160,581 0.9204 160,581 Proto-Power Calc: 97-198 

==Attachment:==

C Rev: A Page 5 of 14*** Air Mass Velocity (Lbrnlhr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:17:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/10/98 WA Extrapolation Calculation for Row 4(Dry)II II 1. 1 Air-Side Mass Flow (lbm/hr) 123,544.84 Inlet Temperature (0 F) 133.31 Outlet Temperature (0 F) 128.93 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 131.12 Skin Temperature (0 F) 115.14 Velocity *** 6,255.18 Reynold's Number 2,316 Prandtl Number 0.7266 Bulk Vise (ibm/ft hr) 0.0482 Skin Visc (1bm/ft-hr)
Density (lbm/ft 3) 0.0636 Cp (BTU/lbm'&deg;F) 0.2402 K (BTU/hr'ft'&deg;F) 0.0159 Tube-Side 58,613.21 105.02 109.65 107.34 110.98 2.17 13,932 4.1658 1.5246 1.4695 61.8972 0.9989 0.3656 Tube-Side hi (BTU/hr'fti 2.F) 751.14 j Factor 0.0067 Air-Side ho (BTU/hr'ft 2'-F) 12.53 Tube Wall Resistance (hr-ft2.'F/BTU 

==0.0 0024732==
Overall Fouling (hr ft2. F/BTU) 0.02228812 U Overall (BTU/hrft2-&deg;'F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.75 738.01 23.65 135,321 0.9206 135,321 Proto-Power Cale: 97-198 

==Attachment:==

C Rev: A Page 6 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Given Dry Bulb and Specific Humidity Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv/Ps =a=b=C=d=e=f=14.315 psia 128.93 OF 0.020337508 0.453253232 psia 13.86174677 psia 0.063563747 Ibm/ft 3 0.001292728 Ibm/ft 3 0.064856475 Ibm/ft 3 2.162352424 psia 20.961 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071 E-1 1 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]0 00/Je 6'~cil~e~
k/'27 ( A 1 Vr"~-(
08:54:10 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 07/10/98 ComEd -- LaSalle Data Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils-Initial Benchmark Case -- Standard Coil Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Flid1-Qiitti-hTy,, Tol-tV 382483_00 82.00 gpm Inlet Dry Bulb Temp OF 105.00 OF Inlet Wet Bulb Temp OF Inlet Relative Humidity %Outlet Dry Bulb Temperature OF OF Outlet Wet Bulb Temp OF Outlet Relative Humidity %Tube Fluid Name Fresh Water Tube Fouling Factor 0.001500 Air-Side Fouling 0.000000 Design Heat Transfer (BTU/hr)Atmospheric Pressure 14.315 Sensible Heat Ratio 1.00 Performance Factor (% Reduction) 0.000 Heat Exchanger Type Counter Flow Fin Type Circular Fins Fin Configuration CF-9.05-3/4J A j EXP[-2.3333 
+ -0.3441
* LOG(Re)]Coil Finned Length (in) 108.000 Fin Pitch (Fins/Inch) 10.000 Fin Conductivity (BTU/hr-ft.&deg;F) 128.000 Fin Tip Thickness (inches) 0.0120 Fin Root Thickness (inches) 0.0120 Circular Fin Height (inches) 1.347 Number of Coils Per Unit 2 Number of Tube Rows 8 Number of Tubes Per Row 20.00 Active Tubes Per Row 20.00 Tube Inside Diameter (in) 0.5270 Tube Outside Diameter (in) 0.6250 Longitudinal Tube Pitch (in) 1.500 Transverse Tube Pitch (in) 1.370 Number of Serpentines 2.000 Tube Wall Conductivity (BTU/hr-ft.&deg;F) 225.00 Proto-Power Calc: 97-198 

==Attachment:==

C Rev: A Page 8 of 14 08:54:10 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 7/10/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (OF)Air Dry Bulb Temp Out (&deg;F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (&deg;F)Wet Bulb Temp Out (&deg;F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (OF)Condensate Temperature 
(&deg;F)Extrapolation Data Tube Flow (gpm)Air Flow (acfin)Tube Inlet Temp (&deg;F)Air Inlet Temp (OF)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (&deg;F)Atmospheric Pressure 82.00 32,386.60 105.00 128.9 20.96 0.00 14.315~E- /1~L~S~Fn'4 cce~i~&#xb6;oss Ft 0 Proto-Power Calc: 97-198 

==Attachment:==

C Rev: A Page 9 of 14 08:54:10 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/10/98 Extrapolation Calculation Summary II\4, Air-Side Mass Flow (lbmlhr) 123,544.82 Inlet Temperature (OF) 128.93 Outlet Temperature (OF) 113.67 Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Vise (Ibm/ft hr)Density (lbmr/fV)Cp (BTU/lbm-0 F)K (BTU/hr-ft'&deg;F)
Tube-Side 40,731.22 105.00 116.61 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr ft 2_-F)Tube Wall Resistance (hr.ft 2.&deg; F/BTU 0.00024732 Overall Fouling (hr' ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5,904.10 471,786 471,786 Extrapolation Calculation for Row l(Dry)11 Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Vise (Ibm/ft-hr)
Density (lbm/ft3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr.ft-&deg;F)
Air-Side 123,544.82 128.93 126.66 0.0203 0.0203 127.79 120.17 6,255.18 1,745 0.7268 0.0480 0.0638 0.2402 0.0159 Tube-Side 40,731.22 113.84 117.29 115.56 118.00 1.51 10,508 3.8074 1.4048 1.3722 61.7791 0.9988 0.3685 Tube-Side hi (BTU/hr-ft2-&deg;F) 585.29 j Factor 0.0074 Air-Side ho (BTU/hr ft2. F) 13.81 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr4ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr ft 2.&deg;F)Effective Area (ff)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.86 738.01.12.12 70,311 0.9134 70,311 Proto-Power Calc: 97-198 

==Attachment:==

C Rev: A Page 10 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:54:10 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/10/98 0 1 Extrapolation Calculation for Row 2(Dry)II I.Air-Side Mass Flow (lbm/hr) 123,544.82 Inlet Temperature (IF) 126.66 Outlet Temperature (OF) 124.56 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 125.61 Skin Temperature (OF) 118.59 Velocity *** 6,255.18 Reynold's Number 1,750 Prandtl Number 0.7270 Bulk Visc (lbm/fthr) 0.0478 Skin Vise (Ibm/ft1hr)
Density (lbm/ffP) 0.0641 Cp (BTU/lbm-&deg;F) 0.2402 K (BTU/hr'ft-&deg;F) 0.0158 Tube-Side 40,731.22 112.74 115.92 114.33 116.59 1.51 10,383 3.8578 1.4217 1.3909 61.7974 0.9988 0.3681 Tube-Side hi (BTU/hr-ft 2.&deg;F) 581.45 j Factor 0.0074 Air-Side ho (BTU/hr-ft 2-F) 13.80 Tube Wall Resistance (hr.ft 2 0-F/BTU 0.00024732 Overall Fouling (hr ft2.&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr'ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.85 738.01 11.17 64,711 0.9135 64,711 11 -- ----Extrapolation Calculation for Row 3(Dry)II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/fV3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ft--F)
Air-Side 123,544.82 124.56 122.48 0.0203 0.0203 123.52 116.52 6,255.18 1,754 0.7272 0.0477 0.0643 0.2402 0.0158 Tube-Side 40,731.22 110.67 113.84 112.25 114.53 1.51 10,172 3.9455 1.4511 1.4190 61.8278 0.9988 0.3673 Tube-Side hi (BTU/hr-.ft2.F) 575.19 j Factor 0.0074 Air-Side ho (BTU/hr ft 2_-F) 13.78 Tube Wall Resistance (hr-ft2.&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft 2 0.F/BTU) 0.02228812 U Overall (BTU/hr.ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.83 738.01 11.17 64,486 0.9136 64,486 Proto-Power Cale: 97-198 

==Attachment:==

C Rev: A Page 11 of 14*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:54:10 PROTO-HX 3.01 by Proto-Powver Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/10/98 Extrapolation Calculation bor l(ow 4tDry)II 1. __Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/frhr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm'0 F)K (BTU/hr'ft-'F)
Air-Side 123,544.82 122.48 120.59 0.0203 0.0203 121.53 115.18 6,255.18 1,759 0.7273 0.0476 0.0645 0.2402 0.0157 Tube-Side 40,731.22 109.87 112.74 111.30 113.38 1.51 10,077 3.9864 1.4648 1.4350 61.8414 0.9988 0.3670 Tube-Side hi (BTU/hr-ft 2-&deg;F) 572.18 j Factor 0.0074 Air-Side ho (BTU/hr'ft 2.&deg;F) 13.77 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2.0 F/BTU) 0.02228812 U Overall (BTU/hr'f12-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.81 738.01 10.13 58,422 0.9137 58,422.i-iI Extrapolation Calculation for Row 5(Dry)II I.Air-Side Mass Flow (lbm/hr) 123,544.82 Inlet Temperature (IF) 120.59 Outlet Temperature 
(&deg;F) 118.66 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 119.63 Skin Temperature (IF) 113.17 Velocity *** 6,255.18 Reynold's Number 1,764 Prandtl Number 0.7274 Bulk Visc (lbmr/fthr) 0.0475 Skin Visc (lbm/ft-hr)
Density (lbm/ft 3) 0.0647 Cp (BTU/Ibm-'F) 0.2402 K (BTU/hr'ft-'F) 0.0157 Tube-Side 40,731.22 107.75 110.67 109.21 111.34 1.51 9,867 4.0797 1.4959 1.4643 61.8712 0.9988 0.3663 Tube-Side hi (BTU/hr.ft2-&deg;F) 565.78 j Factor 0.0074 Air-Side ho (BTU/hr-ft1 2-F) 13.76 Tube Wall Resistance (hr-ft2-&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.79 738.01.10.32 59,363 0.9137 59,363 Proto-Power Calc: 97-198 

==Attachment:==

C Rev: A Page 12 of 14*** Air Mass Velocity (Lbm/hrft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 08:54:10 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: I(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/10/98 am -Extrapolation Calculation for Row 6(Dry)Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (Ibm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 123,544.82 118.66 116.96 0.0203 0.0203 117.81 112.09 6,255.18 1,768 0.7276 0.0473 0.0649 0.2402 0.0156 Tube-Side 40,731.22 107.28 109.87 108.58 110.47 1.51 9,805 4.1083 1.5055 1.4770 61.8800 0.9988 0.3660 Tube-Side hi (BTU/hr-ft 2 -F) 563.58 j Factor 0.0074 Air-Side ho (BTU/hr' ft 2-F) 13.74 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTUihr)7.78 738.01 9.15 52,562 0.9138 52,562.. i .11 Extrapolation Calculation for Row 7(Dry)11*1 Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (Ibm/ft hr)Skin Vise (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr-ft-&deg;F)
Air-Side 123,544.82 116.96 115.19 0.0203 0.0203 116.08 110.09 6,255.18 1,772 0.7277 0.0472 0.0651 0.2402 0.0156 Tube-Side 40,731.22 105.05 107.75 106.40 108.40 1.51 9,589 4.2102 1.5394 1.5082 61.9101 0.9989 0.3652 Tube-Side hi (BTU/hr-ft 2.&deg;F) 556.37 j Factor 0.0074 Air-Side ho (BTU/hr-ft 2-&deg;F) 13.73 Tube Wall Resistance (hr-ft 2 l-F/BTU 0.00024732 Overall Fouling (hr- ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.76 738.01 9.59 54,903 0.9139 54,903 Proto-Power Calc: 97-198 

==Attachment:==

C Rev: A Page 13 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:54:10 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 07/10/98Extrapolation Calculation for Row 8(Dry)*1 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft hr)Density (ibm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 123,544.82 115.19 113.67 0.0203 0.0203 114.43 109.30 6,255.18 1,776 0.7278 0.0471 0.0653 0.2402 0.0156 Tube-Side 40,731.22 104.97 107.28 106.13 107.85 1.51 9,562 4.2230 1.5436 1.5167 61.9137 0.9989 0.3651 Tube-Side hi (BTU/hr'ft 2"&deg;F) 555.21 j Factor 0.0074 Air-Side ho (BTU/hr-ft 2.&deg;F) 13.72 Tube Wall Resistance (hr-ft 2.0 F/BTU 0.00024732 Overall Fouling (hr- ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/tr-.ft 2.F)Effective Area (f12)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.75 738.01 8.22 47,029 0.9140 47,029 Proto-Power Calc: 97-198 

==Attachment:==

C Rev: A Page 14 of 14*** Air Mass Velocity (Lbrn/hr-ft 2), Tube Fluid Velocity (ftlsec);
Air Density at Inlet T, Other Properties at Average T Attachment D to Proto-Power Calculation 97-198 Revision A Proto-Power Calc: 97-198 

==Attachment:==

D Rev: A Page 1 of 2 I 268 Coinpatet Heat Exchangcrs Fig. 10-89 Finned rircu.lar tub~es, surfacs CF-9.05 -3/4J. (Data at .Jameon.)I Tube outside diameter -0.774 in = 19.68 x 1D-3m Fin pitch = 9.05 per in 356 per m Fin thickness-0.012 in -0.305 x 10" m Fin area/total area 0.835 Flow pasW hydraulic A B diameter.
4r = 0,01681 0.02685 5.131x10-1 8.179x 10-3 C 0.0445 13.59 x 70-" 0 0.01 587 4.846)( 10-3 E 0.02108 ft 6.426 x U03 m Free flow area!frontal area a, 0.456 Heat transfer areal iotat volume, a 108= 354 5 0.572 0.688 0.537 0.572 85.1 279 61.9 135 108 ft 2 ttt 3 203 443 354 m~trn 3 NoIc: Miniinum Free-flow a3ea in all ca3so. ccurs the Space, lranlver5e te Unc finw, except for D. in which the nhinimiJmi area its the diageals.Proto-Power Calc: 97-198 

==Attachment:==

D Rev: A Page 2 of 2 Attachment E to Proto-Power Calculation 97-198 Revision A Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 1 of 27 08:40:58 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/10/98 Air Coil Heat Exchanger Input Parameters Fluiid Qu-antiti-ty, Th1NF......
Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side J33,54-6.0 aci-150.00 OF 92.00 OF OF OF Tube-Side.T-87.0gpmf 105.00 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ti.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hrift-&deg;F)
Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-l.9210 
+ -0.3441
* LOG(Re)]108.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 20.00 0.5270 0.6250 2.000 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 2 of 27 08:40:58 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/10/98 CornEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfmn)Air Dry Bulb Temp In (&deg;F)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm) 118.00 Air Flow (acfin) 33,546.00 Tube Inlet Temp (IF) 105.00 Air Inlet Temp (&deg;F) 150.0 Inlet Relative Humidity (%) 0.00 Inlet Wet Bulb Temp (IF) 92.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 3 of 27 08:40:58 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/10/98 is I Extrapolation Calculation Summary II 1.Mass Flow (Ibm/lui)Inlet Temperature (0 F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (Ibm/ft-hr)
Density (lbm/ft3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr'ft'&deg;F)
Air-Side 123,544.84 150.00 125.78 Tube-Side 58,613.21 105.00 117.75 Tube-Side hi (BTU/hr'ft 2-&deg;F)j Factor Air-Side ho (BTU/hr-ft 2-&deg;F)Tube Wall Resistance (hOrft 2.F/BTU Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr'ft 2"&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00024732

==0.0 2228812==
2,952.05 748,549 748,549 Iqupp_-Extrapolation Calculation for Row l(Dry)II II Air-Side Mass Flow (lbm/hr) 123,544.84 Inlet Temperature (IF) 150.00 Outlet Temperature (IF) 142.66 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 146.33 Skin Temperature (IF) 127.97 Velocity *** 6,255.18 Reynold's Number 2,272 Prandtl Number 0.7253 Bulk Visc (Ibm/ft-hr) 0.0491 Skin Visc (lbm/ft-hr)
Density (lbm/ft 3) 0.0621 Cp (BTU/Ibm'&deg;F) 0.2402 K (BTU/hr'f 0'F) 0.0163 Tube-Side 58,613.21 111.22 118.97 115.10 120.97 2.17 15,053 3.8263 1.4111 1.3342 61.7861 0.9988 0.3684 Tube-Side hi (BTU/hr'f 2'-F) 784.81 j Factor 0.0103 Air-Side ho (BTU/hr'ft 2-&deg;F) 19.09 Tube Wall Resistance (hr-ft 2.F/BTU 0.00024732 Overall Fouling (hr'f 2."&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.94 738.01.30.94 226,898 0.8852 226,898 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 4 of 27*** Air Mass Velocity (Lbmihr-ft'), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:40:58 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/10/98 Extrapolation Calculation for Row 2(Dry)11 LI.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbmrrft-hr)
Skin Visc (ibm/ft hr)Density (lbmr/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr.ft-&deg;F)
Air-Side 123,544.84 142.66 136.50 0.0203 0.0203 139.58 124.13 6,255.18 2,291 0.7259 0.0487 0.0628 0.2402 0.0161 Tube-Side 58,613.21 110.03 116.53 113.28 118.26 2.17 14,788 3.9016 1.4364 1.3688 61.8128 0.9988 0.3677 Tube-Side hi (BTU/hr'ft 2'&deg;F) 776.58 j Factor 0.0102 Air-Side ho (BTU/hr'ft 2"&deg;F) 19.02 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr'ft 2.&deg;F/BTU) 0.02228812 U Overall (BTUihr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.90 738.01 26.06 190,348 0.8856 190,348 II Extrapolation Calculation for Row 3(Dry)II*1 Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft'&deg;F)
Air-Side 123,544.84 136.50 130.58 0.0203 0.0203 133.54 118.65 6,255.18 2,309 0.7264 0.0483 0.0634 0.2402 0.0160 Tube-Side 58,613.21 104.97 111.22 108.10 113.02 2.17 14,041 4.1303 1.5128 1.4401 61.8867 0.9988 0.3658 Tube-Side hi (BTU/hr-ft 2.0 F) 755.57 j Factor 0.0102 Air-Side ho (BTU/hr-ft2.&deg;F) 18.97 Tube Wall Resistance (hr-ft 2 -F/BTU 0.00024732 Overall Fouling (hr. ft 2-F/BTU) 0.02228812 U Overall (BTU/hr-ft 2 l-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (iBTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.83 738.01 25.21 182,919 0.8859 182,919 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 5 of 27*** Air Mass Velocity (Lbm/hr~ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:40:58 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/10/98 I Extrapolation Calculation for Row 4(Dry)II II I Air-Side Mass Flow (Ibm/hr) 123,544.84 Inlet Temperature (OF) 130.58 Outlet Temperature (0 F) 125.78 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 128.18 Skin Temperature (OF) 116.08 Velocity *** 6,255.18 Reynold's Number 2,325 Prandtl Number 0.7268 Bulk Vise (lbm/ft'hr) 0.0480 Skin Vise (ibm/ft-hr)
Density (lbm/ft 3) 0.0639 Cp (BTU/Ibm-&deg;F) 0.2402 K (BTU/hr-ft-&deg;F) 0.0159 Tube-Side 58,613.21 104.96 110.03 107.50 111.50 2.17 13,955 4.1584 1.5221 1.4619 61.8950 0.9989 0.3656 Tube-Side hi (BTU/hr ft 2-OF) 752.17 j Factor 0.0102 Air-Side ho (BTU/hr ft 2-&deg;F) 18.91 Tube Wall Resistance (hr-ftV-&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr ft 2.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.81 738.01 20.50 148,385 0.8861 148,385 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 6 of 27*** Air Mass Velocity (Lbnvhrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T I -.Moist Air Properties 
--Total .Pressure:
Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
Given Dry Bulb and Specific Humidity W=.Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T4)+(f*T
: 5) =RH = Pv/Ps a=b=C=d=e=f=14.315 psia 125.78 OF 0.020337508 0.453253232 psia 13.86174677 psia 0.06390575 Ibm/ft 3 0.001299684 Ibm/ft 3 0.065205434 Ibm/ft 3 1.986075574 psia L-22.82155007 
%2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071 E-1 1 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]tTI"-i 0 0 00&#xa2;1.0 00[f 0 1' -Acve-~ Y V\11 F>~ &~c/~n~/C 
-~
09:50:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: I(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/10/98 Air Coil Heat Exchanger Input Parameters Te Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side.....327437 .ac- i 0 F 0 F Tube-Side-. 82700 gpm-105.00 OF OF OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Fresh Water 0.001500 0.000000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ftl-F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr"ft-'F) 108.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 20.00 0.5270 0.6250 1.500 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 8 of 27 09:50:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 7/10/98 r_- Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm)Air Flow (acfm)Tube Inlet Temp ('F)Air Inlet Temp ('F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (&deg;F)Atmospheric Pressure 82.00 32,213.26 .s 105.00 /(125.8 22.82 r C 0 1 y 0.00oo f/o 14.315 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 9 of 27 09:50:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: I(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/10/98 Extrapolation Calculation Summary II N Mass Flow (Ibmnlhr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbml/fthr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F) ir-Side 123,544.82 125.78 111.36 Tube-Side 40,731.22 105.00 115.94 Tube-Side hi (BTU/hr. ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr'ft 2-F/BTU) 0.02228812 U Overall (BTU/hr ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5,904.10 445,586 445,586 i II Extrapolation Calculation for Row l(Dry)11&#xfd;j Mass Flow (Ibm/hr)Inlet Tqmperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbml/ffhr)
Skin Visc (Ibm/ft'hr)
Density (Ibm/If3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-fti.F)
Air-Side 123,544.82 125.78 123.56 0.0203 0.0203 124.67 119.49 6,255.18 1,752 0.7271 0.0478 0.0642 0.2402 0.0158 Tube-Side 40,731.22 113.27 116.65 114.96 117.36 1.51 10,446 3.8320 1.4130 1.3806 61.7882 0.9988 0.3683 Tube-Side hi (BTU/hr.f2.&deg;OF) 583.44 j Factor 0.0112 Air-Side ho (BTU/hr-ft 2-OF) 20.84 Tube Wall Resistance (hr-ft2.&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft2.&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.73 738.01 9.57 68,767 0.8764 68,767 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 10 of 27*** Air Mass Velocity (Lbmihr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 09:50:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/10/98 Extrapolation Calculation for Row 2(Dry)ii Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (ibm/ft hr)Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 123,544.82 123.56 121.53 0.0203 0.0203 122.54 117.83 6,255.18 1,757 0.7272 0.0476 0.0644 0.2402 0.0157 Tube-Side 40,731.22 112.16 115.23 113.69 115.90 1.51 10,318 3.8843 1.4306 1.4002 61.8068 0.9988 0.3679 Tube-Side hi (BTU/hr'ft 2 0-F) 579.49 j Factor 0.0112 Air-Side ho (BTU/hr-ft 2.-F) 20.82 Tube Wall Resistance (hr-ft 2 .F/BTU 0.00024732 Overall Fouling (hr-ft-'&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr. ft 2 i'F)Effective Area (ftf)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.71 738.01 8.73 62,535 0.8765 62,535 W&#xfd;&#xfd;, Extrapolation Calculation for Row 3(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr.ft-&deg;F)
Air-Side 123,544.82 121.53 119.53 0.0203 0.0203 120.53 115.87 6,255.18 1,761 0.7274 0.0475 0.0646 0.2402 0.0157 Tube-Side 40,731.22 110.22 113.27 111.75 113.95 1.51 10,122 3.9672 1.4584 1.4270 61.8351 0.9988 0.3672 Tube-Side hi (BTU/hr-ft 2-&deg;F) 573.61 j Factor 0.0112 Air-Side ho (BTU/hr ft 2.&deg;F) 20.80 Tube Wall Resistance (hr-ft2-&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr4fiV.&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hrft2.&deg;OF)
Effective Area (ftf)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.68 738.01 8.66 61,900 0.8766 61,900 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 11 of 27*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 09:50:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/10/98 i Extrapolation Calculation for Row 4(Dry)_1 I. *8 Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (ibm/ft hr)Density (Ibm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 123,544.82 119.53 117.75 0.0203 0.0203 118.64 114.48 6,255.18 1,766 0.7275 0.0474 0.0648 0.2402 0.0157 Tube-Side 40,731.22 109.45 112.16 110.80 112.77 1.51 10,027 4.0084 1.4721 1.4436 61.8486 0.9988 0.3668 Tube-Side hi (BTU/hr- ft 2 -F) 570.58 j Factor 0.0112 Air-Side ho (BTU/hr-ft 2-&deg;F) 20.78 Tube Wall Resistance (hr-fl 2.&deg;F/BTU 0.00024732 Overall Fouling (hr flt 2.F/BTU) 0.02228812 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.66 738.01 7.73 55,111 0.8767 55,111 Extrapolation Calculation for Row 5(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ftlhr)
Skin Visc (lbm/ft.hr)
Density (Ibm/fl 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 123,544.82 117.75 115.93 0.0203 0.0203 116.84 112.61 6,255.18 1,770 0.7276 0.0473 0.0650 0.2402 0.0156 Tube-Side 40,731.22 107.47 110.22 108.85 110.87 1.51 9,832 4.0960 1.5014 1.4711 61.8762 0.9988 0.3661 Tube-Side hi (BTU/hr-ft 2564.55 j Factor 0.0112 Air-Side ho (BTU/hr-ft 2.0 F) 20.76 Tube Wall Resistance (hr-ft 2 i.F/BTU 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr.ft 2.OF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.63 738.01 7.88 56,053 0.8768 56,053 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 12 of 27*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 09:50:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/10/98 Extrapolation Calculation for Row 6(Dry)_______II 5.Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ftlhr)
Skin Vise (lbm/ft-hr)
Density (lbm/fl 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 123,544.82 115.93 114.37 0.0203 0.0203 115.15 111.51 6,255.18 1,774 0.7277 0.0472 0.0652 0.2402 0.0156 Tube-Side 40,731.22 107.08 109.45 108.26 110.01 1.51 9,774 4.1228 1.5103 1.4838 61.8844 0.9989 0.3659 Tube-Side hi (BTU/hr- ft 2 -F) 562.44 j Factor 0.0112 Air-Side ho (BTU/hr ft2.&deg;F) 20.74 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2-F/BTU) 0.02228812 U Overall (BTU/hr.ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.62 738.01 6.80 48,255 0.8769 48,255~jwT Extrapolation Calculation for Row 7(Dry)II Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ftlhr)
Skin Vise (lbm/ftlhr)
Density (Ibm/fl 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft 0'F)Air-Side 123,544.82 114.37 112.72 0.0203 0.0203 113.54 109.67 6,255.18 1,778 0.7278 0.0471 0.0654 0.2402 0.0155 Tube-Side 40,731.22 104.95 107.47 106.21 108.09 1.51 9,571 4.2191 1.5423 1.5129 61.9126 0.9989 0.3651 Tube-Side hi (BTU/hr.ft 2-'F) 555.62 j Factor 0.0112 Air-Side ho (BTU/hr-ft 2.0 F) 20.72 Tube Wall Resistance (hr-fi2-&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft 2.0 F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.59 738.01.7.23 51,182 0.8770 51,182 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 13 of 27*** Air Mass Velocity (Lbm/hr-ftl 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 09:50:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 07/10/98 Extrapolation Calculation for Row 8(Dry)I1 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fibhr)
Skin Visc (Ibm/ft hr)Density (lbm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hr-fV-&deg;F)
Air-Side 123,544.82 112.72 111.36 0.0203 0.0203 112.04 108.88 6,255.18 1,782 0.7279 0.0470 0.0655 0.2402 0.0155 Tube-Side 40,731.22 105.02 107.08 106.05 107.59 1.51 9,555 4.2269 1.5449 1.5207 61.9148 0.9989 0.3651 Tube-Side hi (BTU/hr- fl2.F) 554.79 j Factor 0.0111 Air-Side ho (BTU/hr-ft 2.F) 20.70 Tube Wall Resistance (hr-ft2-&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr- ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2."F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.58 738.01 5.91 41,784 0.8771 41,784 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 14 of 27*** Air Mass Velocity (Lbm/hrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:18:59 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 07/10/98 Air Coil Heat Exchanger Input Parameters F Dryi ulFbtit, Teompt-Tl Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperal Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 337,546.00 actm 150.00 OF 92.00 OF ture OF OF Tube-Side 1--T8_00 gpm 105.00 OF OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 4-2 4 20.00 20.00 0.5270 0.6250 2.000 1.370 Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-&deg;F) 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 15 of 27 08:18:59 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/10/98 CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length F- Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acflm)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out (&deg;F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm) 118.00 Air Flow (acfm) 33,546.00 Tube Inlet Temp ('F) 105.00 Air Inlet Temp ('F) 150.0 Inlet Relative Humidity (%) 0.00 Inlet Wet Bulb Temp ('F) 92.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 16 of 27 08:18:59 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 07/10/98 Extrapolation Calculation Summary II Mass Flow (Ibm/lr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft.hr)
Skin Visc (lbm/ftrhr)
Density (Ibm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr-ft.&deg;F)
Air-Side 123,544.84 150.00 126.03 Tube-Side 58,613.21 105.00 117.62 Tube-Side hi (BTU/hr-ft2.OF) j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr- ft 2-0 F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (fil)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)2,870.05 740,828 740,828 Extrapolation Calculation for Row l(Dry)11 Mass Flow (ibm/hr)Inlet Terpnerature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)
Skin Visc (lbm/ft-hf)
Density (lbm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr.ft&deg; 0 F)Air-Side 123,544.84 150.00 142.75 0.0203 0.0203 146.38 128.04 6,433.90 2,336 0.7253 0.0491 0.0621 0.2402 0.0163 Tube-Side 58,613.21 111.15 118.80 114.97 120.94 2.17 15,035 3.8314 1.4128 1.3346 61.7879 0.9988 0.3683 Tube-Side hi (BTU/hr.ft 2 .F) 784.40 j Factor 0.0102 Air-Side ho (BTU/hrl-ft 2-F) 19.45 Tube Wall Resistance (hr-ft 2--F/BTU 0.00024732 Overall Fouling (hr- ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-fl 2-&deg;F)Effective Area (f12)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)10.03 717.51.31.12 224,017 0.8834 224,017 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 17 of 27*** Air Mass Velocity (Lbmihr'ft2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:18:59 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 07/10/98 Extrapolation Uaiculation tor Ro0w zkijry)II 1. --Air-Side Mass Flow (Ibm/hr) 123,544.84 Inlet Temperature (0 F) 142.75 Outlet Temperature (0 F) 136.66 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 139.71 Skin Temperature 
(&deg;F) 124.26 Velocity *** 6,433.90 Reynold's Number 2,356 Prandtl Number 0.7259 Bulk Visc (Ibm/ftihr) 0.0487 Skin Vise (Ibm/ft-hr)
Density (Ibm/Ift 3) 0.0628 Cp (BTU/Ibm-&deg;F) 0.2402 K (BTU/hr'ft-&deg;F) 0.0161 Tube-Side 58,613.21 110.02 116.44 113.23 118.29 2.17 14,781 3.9038 1.4371 1.3684 61.8136 0.9988 0.3677 Tube-Side hi (BTU/hr-ft 2 1-F) 776.46 j Factor 0.0101 Air-Side ho (BTU/hr-ft 2-'F) 19.38 Tube Wall Resistance (hr.ft 2-F/BTU 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.99 717.51 26.24 188,187 0.8837 188,187-. -.-. -.-. --ii II Extrapolation Calculation for Row 3(,Dry)11 I I.Mass Flow (Ibm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ftlhr)
Density (Ibm/ift 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft-'F)
Air-Side 123,544.84 136.66 130.80 0.0203 0.0203 133.73 118.81 6,433.90 2,374 0.7264 0.0483 0.0634 0.2402 0.0160 Tube-Side 58,613.21 104.95 111.15 108.05 113.06 2.17 14,034 4.1326 1.5136 1.4395 61.8874 0.9988 0.3658 Tube-Side hi (BTU/hr-ftl 2.F) 755.47 j Factor 0.0101 Air-Side ho (BTU/hr-ft 2 1-F) 19.32 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft2"&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.93 717.51 25.46 181,300 0.8841 181,300 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 18 of 27*** Air Mass Velocity (Lbni/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:18:59 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 07/10/98 0 Extrapolation Calculation for Row 4(,IDry)II 1, Mass Flow (lbm/hr)Inlet Temperature 
('F)Outlet Temperature 
('F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature 
('F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fI-hr)
Skin Vise (lbm/ftbhr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr-fi-PF)
Air-Side 123,544.84 130.80 126.03 0.0203 0.0203 128.42 116.26 6,433.90 2,391 0.7268 0.0480 0.0639 0.2402 0.0159 Tube-Side 58,613.21 104.98 110.02 107.50 111.59 2.17 13,956 4.1582 1.5221 1.4606 61.8950 0.9989 0.3656 Tube-Side hi (BTU/hr- ft 2.&deg;F) 752.27 j Factor 0.0101 Air-Side ho (BTU/hr- ft 2.'F) 19.27 Tube Wall Resistance (hr-ft 2.F/BTU 0.00024732 Overall Fouling (hr'ft 2-FiBTU) 0.02228812 U Overall (BTU/hr'ft 2.'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.90 717.51 20.73 147,324 0.8843 147,324 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 19 of 27*** Air Mass Velocity (Lbn/hr~ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T Moist Air Properties Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
-- Given Dry Bulb and Specific Humidity W=Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv/Ps =a=b=14.315 psia 126.03 OF 0.020337508 0.453253232 psia 13.86174677 psia 0.063878473 Ibm/ft 3 0.001299129 Ibm/ft 3 0.065177602 Ibm/ft 3 1.999601173 psia 22L.66=718172 0/2.358607E-02 1.007276E-03 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]0 C = 1.888033E-05" 0 d = 3.775047E-07
> g e = 4.871208E-10
,-0 : f= 2.109071E-1 1 P_rQ 0) o00 11[ s c.
08:39:08 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 07/10/98 Air Coil Heat Exchanger Input Parameters Fhuinetffr tity, Ttal Inlet Dry Bulb Temp Inlet Wet Bulb Temp, Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Air-Side Tube-Side 32,483.00 acfr0 827.00 gpm OF 105.00 OF OF OF OF OF Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr.ft-PF)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)105.000 10.000 128.000 0.0120 0.0120 1.347 Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row 2 8 20.00 20.00 Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr"ft.&deg;F) 0.5270 0.6250 1.500 1.370 2.000 225.00 Proto-Power Caic: 97-198 

==Attachment:==

E Rev: A Page 21 of 27 08:39:08 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 7/10/98 Calculation Specifications 1 Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (OF)Air Dry Bulb Temp Out (OF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (&deg;F)Wet Bulb Temp Out (&deg;F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out (&deg;F)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm)Air Flow (acfln)Tube Inlet Temp (OF)Air Inlet Temp (&deg;F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (OF)Atmospheric Pressure 82.00 32,227.22 105.00 126.0 22.67 0.00 14.315 A4d -. &#xfd;/.* t0~,L/6A Ft-A/- 4'.(Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 22 of 27 08:39:08 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 07/10/98 Extrapolation Calculation Summary II 1.Air-Side Mass Flow (lbm/hr) 123,544.82 Inlet Temperature (OF) 126.03 Outlet Temperature (IF) 111.56 Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/flrhr)
Skin Vise (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft'&deg;F)
Tube-Side 40,731.22 105.00 116.01 Tube-Side hi (BTU/hmrft 2.&deg;F)j Factor Air-Side ho (BTU/hr'ft 2"&deg;F)Tube Wall Resistance (hr-ft 2.F/BTU Overall Fouling (hr-ft 2 -F/BTU)U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00024732

==0.0 2228812==
5,740.10 447,161 447,161 I-Extrapolation Calculation for Row l(Dry)II II II Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ftt.F)
Air-Side 123,544.82 126.03 123.81 0.0203 0.0203 124.92 119.69 6,433.90 1,801 0.7271 0.0478 0.0641 0.2402 0.0158 Tube-Side 40,731.22 113.35 116.73 115.04 117.51 1.51 10,455 3.8287 1.4119 1.3787 61.7870 0.9988 0.3683 Tube-Side hi (BTU/hr-ft 2-&deg;F) 583.74 j Factor 0.0111 Air-Side ho (BTU/hr.ft 2.&deg;F) 21.23 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr.ft 2.F/BTU) 0.02228812 U Overall (BTU/hr-ft2.IF)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.82 717.51 9.75 68,671 0.8744 68,671 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 23 of 27*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:39:08 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 07/10/98 L Extrapolation Calculation for Row 2(Dry)al IIl!.m Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (0 F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/rfl)Cp (BTU/Ibm-'F)
K (BTU/hr-ft'&deg;F)
Air-Side 123,544.82 123.81 121.78 0.0203 0.0203 122.79 118.02 6,433.90 1,806 0.7272 0.0477 0.0644 0.2402 0.0157 Tube-Side 40,731.22 112.21 115.29 Tube-Side hi (BTU/hr-ft 2.0 F) 579.71 j Factor 0.0111 Air-Side ho (BTU/hr" ft 2" 0 F) 21.21 Tube Wall Resistance (hr ft 2 -F/BTU 0.00024732 Overall Fouling (hr-ft 2 l-F/BTU) 0.02228812 113.75 116.02 1.51 10,324 3.8819 1.4298 1.3985 61.8059 0.9988 0.3679 U Overall (BTU/hr.ft 2 l-F)Effective Area (ft)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.80 717.51 8.92 62,709 0.8745 62,709 Extrapolation Calculation for Row 3(Dry)II Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 123,544.82 121.78 119.78 0.0203 0.0203 120.78 116.06 6,433.90 1,811 0.7274 0.0475 0.0646 0.2402 0.0157 Tube-Side 40,731.22 110.31 113.35 111.83 114.09 1.51 10,130 3.9636 1.4571 1.4250 61.8339 0.9988 0.3672 Tube-Side hi (BTU/hr-fF 2-F) 573.91 j Factor 0.0111 Air-Side ho (BTU/hrft 2-&deg;F) 21.19 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft2. F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (fW 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.77 717.51.8.83 61,878 0.8747 61,878 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 24 of 27*** Air Mass Velocity (Lbm/hrftl), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:39:08 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 07/10/98 W~t Extrapolation Calculation for Row 4(Dry)ii Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/Rfhr)
Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 123,544.82 119.78 117.98 0.0203 0.0203 118.88 114.65 6,433.90 1,816 0.7275 0.0474 0.0648 0.2402 0.0157 Tube-Side 40,731.22 109.48 112.21 110.85 112.89 1.51 10,031 4.0064 1.4715 1.4420 61.8480 0.9988 0.3668 Tube-Side hi (BTU/hr-ft 2-&deg;F) 570.77 j Factor 0.0111 Air-Side ho (BTU/hr'ft 2.&deg;F) 21.17 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr ft 2'F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (tf)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.75 717.51 7.93 55,450 0.8748 55,450 I1 Extrapolation Calculation for Row 5(Dry)II Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Vise (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr.fi.&deg;F)
Air-Side 123,544.82 117.98 116.17 0.0203 0.0203 117.08 112.80 6,433.90 1,820 0.7276 0.0473 0.0650 0.2402 0.0156 Tube-Side 40,731.22 107.55 110.31 108.93 111.01 1.51 9,840 4.0922 1.5001 1.4690 61.8751 0.9988 0.3662 Tube-Side hi (BTU/hr.ft 2"&deg;F) 564.86 j Factor 0.0111 Air-Side ho (BTU/hr ft2. F) 21.15 Tube Wall Resistance (hr-ft 2 .F/BTU 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (fi2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.72 717.51.8.04 56,057 0.8749 56,057 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 25 of 27*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:39:08 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 07/10/98 no .1 Extrapolation Calculation for Row 6(Dry)II II I1 I I Mass Flow (lbnm.hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (Ibm/ft-hr)
Skin Vise (lbm/ftihr)
Density (lbm/ift)Cp (BTU/lbm-&deg;F)
K Air-Side 123,544.82 116.17 114.59 0.0203 0.0203 115.38 111.66 6,433.90 1,824 0.7277 0.0472 0.0652 0.2402 0.0156 Tube-Side 40,731.22 107.09 109.48 Tube-Side hi (BTU/hr-ft 2.&deg;F) 562.57 j Factor 0.0111 Air-Side ho (BTU/hr ft 2 0-F) 21.13 Tube Wall Resistance (hr-ft 2.0 F/BTU 0.00024732 Overall Fouling (hr- ft 2.&deg;F/BTU) 0.02228812 108.29 110.10 1.51 9,776 4.1217 1.5099 1.4825 61.8841 0.9988 0.3659 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.70 717.51 7.00 48,761 0.8750 48,761 II Extrapolation Calculation for Row 7(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Vise (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft'-F)
Air-Side 123,544.82 114.59 112.94 0.0203 0.0203 113.77 109.85 6,433.90 1,828 0.7278 0.0471 0.0654 0.2402 0.0155 Tube-Side 40,731.22 105.04 107.55 106.30 108.23 1.51 9,579 4.2151 1.5410 1.5109 61.9115 0.9989 0.3652 Tube-Side hi (BTU/hr-ft 2.&deg;F) 555.96 j Factor 0.0111 Air-Side ho (BTU/hrft 2 0-F) 21.11 Tube Wall Resistance (hr.ft 2-F/BTU 0.00024732 Overall Fouling (hr-ft2-0 F/BTU) 0.02228812 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.67 717.51 7.37 51,158 0.8750 51,158 Proto-Power Cale: 97-198 

==Attachment:==

E Rev: A Page 26 of 27*** Air Mass Velocity (Lbm/hr.W), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 08:39:08 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Final Benchmark 
-- Effective Length 07/10/98 Extrapolation Calculation for Row 8(Dry)Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ftbhr)
Density (lbm/fP)Cp (BTU/1bm-0 F)K (BTU/hr-ft.&deg;F)
Air-Side 123,544.82 112.94 111.56 0.0203 0.0203 112.25 109.00 6,433.90 1,832 0.7279 0.0470 0.0655 0.2402 0.0155 Tube-Side 40,731.22 105.00 107.09 Tube-Side hi (BTU/hr-ft 2-&deg;F) 554.83 j Factor 0.0110 Air-Side ho (BTU/hr-ft 2.'F) 21.09 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2 7-F/BTU) 0.02228812 106.04 107.65 1.51 9,554 4.2271 1.5450 1.5198 61.9149 0.9989 0.3651 U Overall (BTU/hr.ft 2 .F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.66 717.51 6.13 42,478 0.8751 42,478 Proto-Power Calc: 97-198 

==Attachment:==

E Rev: A Page 27 of 27*** Air Mass Velocity (Lbm/'hrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Attachment F to Proto-Power Calculation 97-198 Revision A Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 1 of 14 14:11:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coilg Thermal Margin Assessment (Clean)07/10/98 Air Coil Heat Exchanger Input Parameters Air-Side FIiiFd-Q-iniTo t-al 33,54700-i-f..
Inlet Dry Bulb Temp 150.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature OF Outlet Wet Bulb Temp OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Tube-Side.r.1.00 gpm 105.00 OF OF Fresh Water 0.001500 0.000000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hrift&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hrlfi.&deg;F) 105.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 20.00 0.5270 0.6250 2.000 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 2 of 14 14:11:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#IIPHX-0000) 7/10/98 CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coil4s Thermal Margin Assessment (Clean)Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (fF)Air Dry Bulb Temp Out (fF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (&deg;F)Wet Bulb Temp Out (fF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (fF)Condensate Temperature (fF)Extrapolation Data Tube Flow (gpm) 118.00 Air Flow (acfm) 30,718.70 Tube Inlet Temp (&deg;F) 100.00 Air Inlet Temp (&deg;F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (&deg;F) 0.00 Atmospheric Pressure 14.315 Input Fouling Factor 0.000000 proto-Powor CaIc: 97-198 

==Attachment:==

F Rev, A Page 3 of 14 14:11:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/10/98 Extrapolation Calculation Summary 11 I.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/fl-hr)
Density (Ibm/fl 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 113,515.96 148.00 117.91 Tube-Side 58,675.06 100.00 114.55 Tube-Side hi (BTU/hr-ftt.&deg;F) j Factor Air-Side ho (BTU/hr''f&deg; 2 F)Tube Wall Resistance (hr-ft2.'F/BTU 

==0.0 0024732==
Overall Fouling (hr'ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2.OF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)2,870.05 854,494 854,494 Extrapolation Calculation for Row l(Dry)U1 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbmlfl-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 113,515.96 148.00 138.27 0.0203 0.0203 143.14 119.20 5,911.62 2,155 0.7256 0.0489 0.0626 0.2402 0.0162 Tube-Side 58,675.06 106.88 116.31 111.60 119.11 2.18 14,559 3.9736 1.4605 1.3578 61.8372 0.9988 0.3671 Tube-Side hi (BTU/hr ft 2.&deg;F) 773.05 j Factor 0.0104 Air-Side ho (BTU/hr ft 2 0-F) 18.37 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr-ftl 2.F/BTU)U Overall (BTU/hr.ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)12.39 717.51 31.08 276,287 0.8890 276,287 Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 4 of 14*** Air Mass Velocity (Lbm/lhr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:11:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/10/98 Extrapolation Calculation for Row 2(Dry)It II II I Air-Side Mass Flow (lbm/hr) 113,515.96 Inlet Temperature (IF) 138.27 Outlet Temperature (IF) 130.49 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 134.38 Skin Temperature (IF) 115.18 Velocity *** 5,911.62 Reynold's Number 2,180 Prandtl Number 0.7263 Bulk Visc (lbm/ft-hr) 0.0484 Skin Visc (lbmn/f-hr)
Density (lbm/fP) 0.0634 Cp (BTU/1bm-&deg;F) 0.2402 K (BTU/hr-fi.&deg;F) 0.0160 Tube-Side 58,675.06 105.24 112.78 109.01 115.10 2.17 14,186 4.0886 1.4989 1.4110 61.8740 0.9989 0.3662 Tube-Side hi (BTU/hr-ft 2.&deg;F) 761.12 j Factor 0.0104 Air-Side ho (BTU/hr-ft 2.&deg;F) 18.28 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU)U Overall (BTU/Ih-'ft 2 'F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)12.31 717.51 25.01 220,818 0.8894 220,818 all Extrapolation Calculation for Row 3(Dry)11 I.Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/f3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 113,515.96 130.49 123.36 0.0203 0.0203 126.93 109.26 5,911.62 2,201 0.7269 0.0479 0.0642 0.2402 0.0158 Tube-Side 58,675.06 99.97 106.88 103.43 109.19 2.17 13,393 4.3557 1.5876 1.4962 61.9499 0.9989 0.3641 Tube-Side hi (BTU/hr-ft2-&deg;F) 738.07 j Factor 0.0104 Air-Side ho (BTU/hr ft 2-&deg;F) 18.21 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2 0.F/BTU)U Overall (BTU/hr.ft2-OF)
Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)12..18 717.51 23.17 202,528 0.8898 202,528 Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 5 of 14*** Air Mass Velocity (Lbm/hr.ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 14:11:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/10/98 a Extrapolation Calculation for Row 4(Dry)11 I, Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (ibm/ft hr)Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr-ft-.F)
Air-Side 113,515.96 123.36 117.91 0.0203 0.0203 120.64 107,09 5,911.62 2,219 0.7274 0.0475 0.0648 0.2402 0.0157 Tube-Side 58,675.06 99.96 105.24 102.60 107.03 2.17 13,277 4.3977 1.6015 1.5293 61.9608 0.9989 0.3638 Tube-Side hi (BTU/hr'ft 2 -F) 733.30 j Factor 0.0103 Air-Side ho (BTU/hr" ft 2.'F) 18.15 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr'ft 2-F/BTU)U Overall (BTU/hr'ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)12.14 717.51 17.78 154,861 0.8901 154,861 Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 6 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Moist Air Properties 
-- Gi'Total Pressure:
P =Dry Bulb Temperature:
T =Specific Humidity:
W: Water Vapor Pressure:
Pv Dry Air Pressure:
Pa Dry Air Density: Rh Water Vapor Density: Rhc Moist Air Density: Rh Saturated Air Pressure:
Ps Moist Air Relative Humidity:
RH Equation Coefficients:
a -b=C=d=)* e " f=ven Dry Bulb and Specific Humidity= (W*Rv*P)/(Ra+(W*Rv)) 
==p- Pv=o a = (144/53.352)*(Pa/(459.67+T)) 
=o v = (144/85.778)*(Pv/(459.67+T)) 
=o = Rho a + Rho v == a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) == Pv /Ps =14.315 117.91 0.020273629 0.451874518 13.86312548

==0.0 64782961==
0.001313386

==0.0 66096347==
1.598498195 28.26869116 2.358607E-02 1 .007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071 E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]Pd CD--j 0 0 0 00 Co 4 (cte-,- )j ISee-~
14:18:28 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHlX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils-Thermal Margin Assessment (Clean)07/10/98[I Air Coil Heat Exchanger Input Parameters I Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 32,483__0 -acfffi OF OF OF OF Tube-Side.. .82 _ gpm 105.00 OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-.F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr ft.&deg;F)105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 20.00 0.5270 0.6250 1.500 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 8 of 14 14:18:28 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)7/10/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (&deg;F)Air Dry Bulb Temp Out (&deg;F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (&deg;F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm)Air Flow (acfin)Tube inlet Temp (IF)Air Inlet Temp (IF)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (IF)Atmospheric Pressure 82.00 29,197.64 
-!100.00 117.9 28.27 0.00 14.315 Yt4A$~C P(o~Input Fouling Factor 0.000000 4: Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 9 of 14 14:18:28 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/10/98 U Extrapolation Calculation Summary II L' *1&#xfd;Air-Side Mass Flow (Ibm/hr) 113,515.94 Inlet Temperature (OF) 117.91 Outlet Temperature (OF) 104.11 Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fibhr)
Skin Visc (ibm/ft hr)Density (lbm/ft 3)Cp (BTU/lbm-0 F)K (BTU/hr-fr'&deg;F)
Tube-Side 40,774.19 100.00 109.65 Tube-Side hi (BTU/hrft 2 0.'F)j Factor Air-Side ho (BTU/ir- ft2.&deg;F)Tube Wall Resistance (hr-ft 2 -F/BTU 0.00024732 Overall Fouling (hr-ftV.&deg;F/BTU)
U Overall (BTU/hr ft2- F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5,740.10 391,980 391,980-11 ----- .1 II Extrapolation Calculation for Row l(Dry)II Mass Flow (Ibm/hr)Inlet Termperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fi-hr)
Skin Visc (Jbm/ft'hr)
Density (Ibm/fl 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-rF)
Air-Side 113,515.94 117.91 115.55 0.0203 0.0203 116.73 111.31 5,911.62 1,673 0.7276 0.0473 0.0651 0.2402 0.0156 Tube-Side 40,774.19 107.13 110.43 108.78 111.29 1.51 9,835 4.0991 1.5024 1.4650 61.8772 0.9988 0.3661 Tube-Side hi (BTU/hr ft2.OF) 565.21 j Factor 0.0114 Air-Side ho (BTU/hr fi 2-OF) 20.00 Tube Wall Resistance (hr-ft 2.F/BTU 0.00024732 Overall Fouling (hr- ft 2.F/BTU)U Overall (BTU/hr. ft 2 .F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)12.00 717.51 7.79 67,057 0.8806 67,057 Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 10 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:18:28 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/10/98 0 ----1 Extrapolation Calculation for Row 2(Dry)H I.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft hr)Density (Ibm/ft3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-fl.
0 F)Air-Side 113,515.94 115.55 113.45 0.0203 0.0203 114.50 109.68 5,911.62 1,678 0.7278 0.0471 0.0653 0.2402 0.0156 Tube-Side 40,774.19 105.95 108.87 107.41 109.66 1.51 9,699 4.1624 1.5235 1.4891 61.8962 0.9989 0.3656 Tube-Side hi (BTU/hr.ft 2 0-F) 560.51 j Factor 0.0114 Air-Side ho (BTU/hr- ft 2.F) 19.98 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr' ft 2.F/BTU)U Overall (BTU/hr-ft 2-.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)11.96 717.51 6.94 59,607 0.8807 59,607 Extrapolation Calculation for Row 3(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 113,515.94 113.45 111.47 0.0203 0.0203 112.46 107.91 5,911.62 1,683 0.7279 0.0470 0.0655 0.2402 0.0155 Tube-Side 40,774.19 104.37 107.13 105.75 107.89 1.51 9,535 4.2411 1.5497 1.5160 61.9189 0.9989 0.3650 Tube-Side hi (BTU/hr-ft 2.&deg;F) 554.75 j Factor 0.0114 Air-Side ho (BTU/hr-ft 2.&deg;F) 19.96 Tube Wall Resistance (hr-ft 2.0 F/BTU 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr ft2.&deg;F)Effective Area (ff1)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)11.92 717.51.6.57 56,181 0.8808 56,181 Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 11 of 14*** Air Mass Velocity (Lbm/hr-ft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:18:28 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/10/98 KA Extrapolation Calculation for Row 4(Dry)*1 i .__Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ftihr)
Skin Visc (Ibm/ft hr)Density (lbm/fV)Cp (BTU/Ibm'&deg;F)
K (BTU/hruft.F)
Air-Side 113,515.94 111.47 109.75 0.0203 0.0203 110.61 106.64 5,911.62 1,687 0.7280 0.0469 0.0657 0.2402 0.0155 Tube-Side 40,774.19 103.54 105.95 Tube-Side hi (BTU/hr ft2.&deg;F) 550.95 j Factor 0.0114 Air-Side ho (BTU/hr'ft 2 -F) 19.94 Tube Wall Resistance (hr-ft 2 .F/BTU 0.00024732 Overall Fouling (hr'ft 2"&deg;F/BTU)104.74 106.62 1.51 9,436 4.2903 1.5660 1.5358 61.9325 0.9989 0.3646 U Overall (BTU/hr-ft 2-OF)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)11.88 717.51 5.75 49,001 0.8809 49,001 Extrapolation Calculation for Row 5(Dry)11 I 'Air-Side Mass Flow (Ibm/hr) 113,515.94 Inlet Temperature (OF) 109.75 Outlet Temperature (OF) 108.07 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 108.91 Skin Temperature (OF) 105.06 Velocity *** 5,911.62 Reynold's Number 1,691 Prandtl Number 0.7281 Bulk Visc (lbm/ft-hr) 0.0468 Skin Visc (lbm/ft-hr)
Density (lbm/ft 3) 0.0659 Cp (BTU/Ibm-&deg;F) 0.2402 K (BTU/hr-ft 0'F) 0.0154 Tube-Side 40,774.19 102.04 104.37 103.21 105.05 1.51 9,286 4.3668 1.5913 1.5610 61.9529 0.9989 0.3640 Tube-Side hi (BTU/hrlft2-&deg;F) 545.30 j Factor 0.0114 Air-Side ho (BTU/hr.ft2.&deg;F) 19.92 Tube Wall Resistance (hr-ft 2 0.F/BTU 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU)U Overall (BTU/hr-ft 2.-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)11.84 717.51.5.59 47,456 0.8810 47,456 Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 12 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average -r 14:18:28 PROTO-IIX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/10/98 r~ii Extrapolation Calculation for Row 6(Dry)11 I.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr'fti-F)
Air-Side 113,515.94 108.07 106.67 0.0203 0.0203 107.37 104.13 5,911.62 1,695 0.7282 0.0467 0.0661 0.2402 0.0154 Tube-Side 40,774.19 101.58 103.54 102.56 104.11 1.51 9,222 4.3999 1.6023 1.5763 61.9614 0.9989 0.3638 Tube-Side hi (BTU/hr.ft 2.&deg;F) 542.64 j Factor 0.0113 Air-Side ho (BTU/hr ft 2.&deg;F) 19.90 Tube Wall Resistance (hr-ft 2.0 F/BTU 0.00024732 Overall Fouling (hr-ft 2 0-F/BTU)U Overall (BTU/hr ft 2-&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)11.81 717.51 4.72 39,978 0.8811 39,978 Extrapolation Calculation for Row 7(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Tlemperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Visc (lbm/ft-ir)
Density (Ibm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr'ftl'F)
Air-Side 113,515.94 106.67 105.24 0.0203 0.0203 105.95 102.66 5,911.62 1,698 0.7282 0.0466 0.0663 0.2402 0.0154 Tube-Side 40,774.19 100.05 102.04 101.05 102.64 1.51 9,076 4.4784 1.6282 1.6008 61.9810 0.9990 0.3632 Tube-Side hi (BTU/hr-ft2.
F) 536.87 j Factor 0.0113 Air-Side ho (BTU/hr-ft 2.0 F) 19.89 Tube Wall Resistance (hr-ft 2.F/BTU 0.00024732 Overall Fouling (hr.ft 2.&deg;F/BTU)U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)11.77 717.51.4.81 40,596 0.8812 40,596 Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 13 of 14*** Air Mass Velocity (Lbbm/hrftl 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:18:28 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Clean)07/10/98 Extrapolation Calculation for Row 8(Dry)1I I.Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 113,515.94 105.24 104.11 0.0203 0.0203 104.67 102.07 5,911.62 1,701 0.7283 0.0465 0.0664 0.2402 0.0153 Tube-Side 40,774.19 100.00 101.58 100.79 102.05 1.51 9,051 4.4920 1.6327 1.6108 61.9843 0.9990 0.3631 Tube-Side hi (BTU/hr- ft 1.&deg;F) 535.60 j Factor 0.0113 Air-Side ho (BTU/hr-ft 2--F) 19.87 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr. ft 2.&deg;F/BTU)U Overall (BTU/hr ft 2.&deg;F)Effective Area (ftf)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)11.75 717.51 3.81 32,105 0.8812 32,105 Proto-Power Calc: 97-198 

==Attachment:==

F Rev: A Page 14 of 14*** Air Mass Velocity (Lbmlhr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Attachment G to Proto-Power Calculation 97-198 Revision A Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 1 of 14 14:40:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/10/98 Air Coil Heat Exchanger Input Parameters F liidQ-U~fifitiyiiT`T T -Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Air-Side 33,546.00--cfi 150.00 OF 92.00 OF OF OF Tube-Side 10 5-8.00 gpm 105.00 0 F Fresh Water 0.001500 0.000000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr.ft 0.F)Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F) 105.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 20.00 0.5270 0.6250 2.000 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 2 of 14 14:40:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/10/98 ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)Calculation Specifications I Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used , Test Data Data Date Air Flow (acfin)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out (&deg;F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (fF)Tube Temp Out ('F)Condensate Temperature (fF)Extrapolation Data Tube Flow (gpm) 118.00 Air Flow (acfmn) 30,610.10 Tube Inlet Temp ('F) 100.00 Air Inlet Temp (0 F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (&deg;F) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 3 of 14 14:40:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/10/98 Extrapolation Calculation Summary 11 Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Visc (lbm/ftrhr)
Density (lbm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr'ft'&deg;F)
Air-Side 113,114.65 148.00 121.40 Tube-Side 58,675.06 100.00 112.83 Tube-Side hi (BTU/hr. ft.'&deg;F)j Factor Air-Side ho (BTU/hr'ft 2-&deg;F)Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr-ft 2-'F)Effective Area (f1 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)2,870.05 752,589 752,589.11 Extrapolation Calculation for Row l(Dry)II I. II Air-Side Mass Flow (lbm/hr) 113,114.65 Inlet Temperature 
(&deg;F) 148.00 Outlet Temperature (0 F) 139.79 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 143.89 Skin Temperature 
(&deg;F) 123.85 Velocity *** 5,890.72 Reynold's Number 2,146 Prandtl Number 0.7255 Bulk Visc (lbm/ft-ihr) 0.0490 Skin Visc (lbm/ft-hr)
Density (lbm/ft 3) 0.0624 Cp (BTU/Ibm-&deg;F) 0.2402 K (BTU/hr.ft.&deg;F) 0.0162 Tube-Side 58,675.06 106.18 114.11 110.14 116.48 2.17 14,350 4.0375 1.4819 1.3923 61.8580 0.9988 0.3666 Tube-Side hi (BTU/hr-ft'.&deg;F) 765.98 j Factor 0.0105 Air-Side ho (BTU/hr-ft 2-.F) 18.33 Tube Wall Resistance (hr-ft 2 l-F/BTU 0.00024732 Overall Fouling (hr-ftV.&deg;F/BTU) 

==0.0 2228812==
U Overall (BTU/hr ft 2.&deg;F)Effective Area (f1 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.68 717.51.33.44 232,327 0.8891 232,327 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 4 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:40:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/10/98 Extrapolation Calculation for Row 2(Dry)II II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/fl 3)Cp (BTU/lbm 0'F)K (BTU/hr-ft.&deg;F)
Air-Side 113,114.65 139.79 132.98 0.0203 0.0203 136.38 119.70 5,890.72 2,166 0.7262 0.0485 0.0632 0.2402 0.0161 Tube-Side 58,675.06 104.98 111.56 108.27 113.59 2.17 14,081 4.1223 1.5102 1.4321 61.8843 0.9989 0.3659 Tube-Side hi (BTU/hr ft 2.&deg;F) 757.33 j Factor 0.0104 Air-Side ho (BTU/hr.ft 2_OF) 18.26 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2 0.F/BTU) 0.02228812 U Overall (BTU/hr ft 2-OF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.64 717.51 27.86 192,721 0.8895 192,721 II Extrapolation Calculation for Row 3(Dry)11~&#xfd;j Mass Flow (Ibm/hr)Inlet Termperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/1bm'&deg;F)
K (BTU/hr-ft'&deg;F)
Air-Side 113,114.65 132.98 126.56 0.0203 0.0203 129.77 113.99 5,890.72 2,185 0.7267 0.0481 0.0638 0.2402 0.0159 Tube-Side 58,675.06 99.98 106.18 103.08 108.24 2.17 13,345 4.3732 1.5934 1.5107 61.9545 0.9989 0.3640 Tube-Side hi (BTU/hr.ft 2-&deg;F) 736.03 j Factor 0.0104 Air-Side ho (BTU/hr.-ft.
0 F) 18.20 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hrft2Z-&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.57 717.51.26.45 181,650 0.8898 181,650 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 5 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ftlsec);
Air Density at Inlet T, Other Properties at Average T 14:40:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PflX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/10/98 Lm&#xfd; i Extrapolation Calculation for Row 4(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbmi/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-fti.F)
Air-Side 113,114.65 126.56 121.40 0.0203 0.0203 123.98 111.28 5,890.72 2,202 0.7271 0.0477 0.0644 0.2402 0.0158 Tube-Side 58,675.06 100.01 104.98 102.49 106.66 2.17 13,263 4.4031 1.6033 1.5353 61.9622 0.9989 0.3637 Tube-Side hi (BTU/hr ft 2.&deg;F) 732.58 j Factor 0.0104 Air-Side ho (BTU/hr-ft 2-&deg;F) 18.14 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/Ir. ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.55 717.51 21.30 145,892 0.8901 145,892 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 6 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Moist Air Properties Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
--Given Dry Bulb and Specific Humidity T=W=Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T))
Rho v = (144/85.778)*(Pv/(459.67+T))
Rho = Rho a + Rho v=Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv /Ps =a=b=C=d=e=f=14.315 121.4 0.020273629 0.451874518 13.86312548

==0.0 64393864==
0.001305497

==0.0 65699362==
1.76150085 25.65281294 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]0D 0 0 40 0 00 r Se.,-"ce-I Se e a ,AcC~ (/V7 14:46:55 PROTO-IHX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/10/98 Air Coil Heat Exchanger Input Parameters Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Air-Side 32,4,83.0--acfm.
OF OF OF OF Tube-Side-....82:0-0 gpm 105.00 OF OF Fresh Water 0.001500 0.000000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F) 105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 20.00 0.5270 0.6250 1.500 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 8 of 14 14:46:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)7/10/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (OF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm)Air Flow (acfm)Tube Inlet Temp (IF)Air Inlet Temp (IF)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (IF)Atmospheric Pressure 82.00 29,270.07 
.&- 4,,j,.,./4 
.4 A 100.00 ., , , 121.4 ca; IX 25.65 Ro 0.00 14.315 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 9 of 14 14:46:55 PROTO-HIX 3.01 by Proto-Power Corporation (SN#PH X-0000)CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/10/98 , -.1 Extrapolation Calculation Summary II I.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm'&deg;F)
K (BTU/hr-ft-&deg;F)
Air-Side 113,114.62 121.40 106.11 Tube-Side 40,774.19 100.00 110.66 Tube-Side hi (BTU/hr.ft 2-&deg;F)j Factor Air-Side ho (BTU/hr-ft 2 'F)Tube Wall Resistance (hr-ft 2-&deg;F/BTU Overall Fouling (hr-ft 2-&deg;F/BTU)U Overall (BTU/hr"ft1.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00024732

==0.0 2228812==
5,740.10 432,781 432,781 Extrapolation Calculation for Row l(Dry)II Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fl'hr)
Skin Visc (lbm/ft-hr)
Density (lbm/fP)Cp (BTU/lbm-&deg;F)
K (BTU/hr.f.&deg;F)
Air-Side 113,114.62 121.40 118.92 0.0203 0.0203 120.16 114.52 5,890.72 1,660 0.7274 0.0475 0.0647 0.2402 0.0157 Tube-Side 40,774.19 107.96 111.41 109.68 112.28 1.51 9,926 4.0581 1.4887 1.4506 61.8645 0.9988 0.3664 Tube-Side hi (BTU/hr.fl 2-F) 568.14 j Factor 0.0114 Air-Side ho (BTU/hr.ft 2-&deg;F) 19.99 Tube Wall Resistance (hr-ft2- F/BTU 0.00024732 Overall Fouling (hr ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.48 717.51.10.34 70,295 0.8807 70,295 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 10 of 14*** Air Mass Velocity (Lbmi/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:46:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/10/98 Extrapolation Calculation for Row 2(Dry)II I.Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (ibm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr.ftF.F)
Air-Side 113,114.62 118.92 116.68 0.0203 0.0203 117.80 112.72 5,890.72 1,665 0.7276 0.0473 0.0649 0.2402 0.0156 Tube-Side 40,774.19 106.79 109.90 108.35 110.70 1.51 9,792 4.1188 1.5090 1.4736 61.8832 0.9988 0.3659 Tube-Side hi (BTU/Iur.ft 2-&deg;F) 563.70 j Factor 0.0114 Air-Side ho (BTU/hr-ft 2-&deg;F) 19.97 Tube Wall Resistance (hrfJV.&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.46 717.51 9.33 63,266 0.8808 63,266_W&#xfd; -Extrapolation Calculation for Row 3(Dry)II V.Air-Side Mass Flow (lbm/hr) 113,114.62 Inlet Temperature (OF) 116.68 Outlet temperature (OF) 114.52 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 115.60 Skin Temperature (OF) 110.70 Velocity *** 5,890.72 Reynold's Number 1,670 Prandtl Number 0.7277 Bulk Visc (Ibm/ft-hr) 0.0472 Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3) 0.0652 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr.ft.&deg;F) 0.0156 Tube-Side 40,774.19 104.96 107.96 106.46 108.76 1.51 9,605 4.2072 1.5384 1.5027 61.9092 0.9989 0.3652 Tube-Side hi (BTU/hr-ft 2.0 F) 557.33 j Factor 0.0114 Air-Side ho (BTU/hr-ft 2.&deg;F) 19.94 Tube Wall Resistance (hr- ft2-F/BTU 

==0.0 0024732==
Overall Fouling (hr- ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr.ft 2.0 F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.42 717.51 9.02 61,001 0.8809 61,001 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 11 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:46:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/10/98 A .--~I Extrapolation Calculation for Row 4(i1ry)11 II Air-Side Mass Flow (lbm/hr) 113,114.62 Inlet Temperature (OF) 114.52 Outlet Temperature (OF) 112.62 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 113.57 Skin Temperature 
(&deg;F) 109.23 Velocity *** 5,890.72 Reynold's Number 1,675 Prandtl Number 0.7278 Bulk Vise (Ibm/ft-hr) 0.0471 Skin Visc (lbm/ftihr)
Density (lbm/ft 3) 0.0654 Cp (BTU/Ibm'&deg;F) 0.2402 K (BTU/hr'ft-0 F) 0.0155 Tube-Side 40,774.19 104.15 106.79 105.47 107.51 1.51 9,508 4.2547 1.5542 1.5218 61.9227 0.9989 0.3649 Tube-Side hi (BTU/hr-ft 2.&deg;F) 553.68 j Factor 0.0114 Air-Side ho (BTU/hr ft 2-&deg;F) 19.92 Tube Wall Resistance (hr-ftl 2.F/BTU 0.00024732 Overall Fouling (hr'ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr'ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.40 717.51 8.00 53,942 0.8810 53,942 Extrapolation Calculation for Row 5(Dry)II 1.Air-Side Mass Flow (ibm/hr) 113,114.62 Inlet Temperature (0 F) 112.62 Outlet 'temperature (OF) 110.74 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 111.68 Skin Temperature 
(&deg;F) 107.39 Velocity *** 5,890.72 Reynold's Number 1,679 Prandtl Number 0.7279 Bulk Visc (Ibm/ft-hr) 0.0470 Skin Visc (lbm/ft-hr)
Density (Ibm/fl 3) 0.0656 Cp (BTU/lbm-'F) 0.2402 K (BTU/hr'ft 0'F) 0.0155 Tube-Side 40,774.19 102.35 104.96 103.65 105.70 1.51 9,330 4.3443 1.5839 1.5505 61.9469 0.9989 0.3642 Tube-Side hi (BTU/hr- ft 2 -F) 547.12 j Factor 0.0114 Air-Side ho (BTU/hr.ft2-F) 19.90 Tube Wall Resistance (hr.ft 2.0 F/BTU 0.00024732 Overall Fouling (hr-ft 2-F/BTU) 0.02228812 U Overall (BTU/hr-ft 2 .F)Effective Area (ft?)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.37 717.51 7.92 53,234 0.8811 53,234 Proto-Power CaIc: 97-198 

==Attachment:==

G Rev: A Page 12 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:46:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PH X-0000)ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/10/98 TI Extrapolation Calculation for Row 6(Dry)'I I, Mass Flow (lbim/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbmr/fthr)
Skin Visc (lbm/ft-hr)
Density (lbm/fV)Cp (BTU/Ibm-'F)
K (BTU/hr-fti.F)
Air-Side 113,114.62 110.74 109.12 0.0203 0.0203 109.93 106.24 5,890.72 1,683 0.7280 0.0468 0.0658 0.2402 0.0155 Tube-Side 40,774.19 101.90 104.15 103.02 104.78 1.51 9,268 4.3762 1.5944 1.5653 61.9553 0.9989 0.3639 Tube-Side hi (BTU/hr'ft 2.&deg;F) 544.55 j Factor 0.0114 Air-Side ho (BTU/hr'ft 2-&deg;F) 19.88 Tube Wall Resistance (hr ft 2.F/BTU 0.00024732 Overall Fouling (hr, ft 2.&deg;F/BTU) 0.02228812 U Overall (BTU/hr. ft 2 i.F)Effective Area (ftf)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.35 717.51 6.82 45,755 0.8812 45,755 F -~-- ----~ I Extrapolation Calculation for Row 7(Dry)UI I.Mass Flow (lbmn/hr)Inlet Temperature (IF)Outlet temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/fV)Cp (BTU/lbm.&deg;F)
K (BTU/hr.fl.F)
Air-Side 113,114.62 109.12 107.46 0.0203 0.0203 108.29 104.52 5,890.72 1,687 0.7281 0.0467 0.0660 0.2402 0.0154 Tube-Side 40,774.19 100.05 102.35 101.20 103.03 1.51 9,090 4.4704 1.6255 1.5944 61.9790 0.9990 0.3632 Tube-Side hi (BTU/hr1ft 2'-F) 537.64 j Factor 0.0114 Air-Side ho (BTU/hr-ftl 2.F) 19.87 Tube Wall Resistance (hr-ft2. F/BTU 0.00024732 Overall Fouling (hr'ftl2.F/BTU) 

==0.0 2228812==
U Overall (BTU/hr. ft 2-IF)Effective Area (ff)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.32 717.51.7.00 46,832 0.8813 46,832 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 13 of 14*** Air Mass Velocity (Lbmi/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 14:46:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Thermal Margin Assessment (Service)07/10/98 n .-I Extrapolation Calculation for Row 8(Dry)I'11 -I Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm./frhr)
Density (Ibm/fW)Cp (BTU/lbm'&deg;F)
K (BTU/hr'tf'PF)
Air-Side 113,114.62 107,46 106.11 0.0203 0.0203 106.79 103.68 5,890.72 1,690 0.7282 0.0466 0.0662 0.2402 0.0154 Tube-Side 40,774.19 100.01 101.90 100.95 102.46 1.51 9,067 4.4832 1.6298 1.6039 61.9822 0.9990 0.3632 Tube-Side hi (BTU/hr. ft 2.&deg;F) 536.44 j Factor 0.0114 Air-Side ho (BTU/hr'ft 2'&deg;F) 19.85 Tube Wall Resistance (hr-ft2.&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr'ft 2-&deg;F/BTU) 0.02228812 U Overall (BTU/hr. ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)9.31 717.51 5.76 38,457 0.8814 38,457 Proto-Power Calc: 97-198 

==Attachment:==

G Rev: A Page 14 of 14*** Air Mass Velocity (Lbrn/hr-ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T Attachment H to Proto-Power Calculation 97-198 Revision A Proto-Power Calc: 97-198 

==Attachment:==

H Rev: A Page 1 of 13 Moist Air Properties Equations for calculating moist air properties are compiled and/or derived in Proto-Power Calculation 96-069, Reference (1), relying on References (2) and (3) as the principal sources of information.
This attachment summarizes the equations pertinent to the moist air conditions calculated for heat exchanger model development.
The applicable material has been extracted from Reference (1) leaving equation numbering as it appears in Reference (1) for ease of cross reference.
: 1. NOMENCLATURE Ma = Mass of Dry Air, Ibm my = Mass of Water Vapor, lbm P = Atmospheric Pressure, lbf/in2 Pa = Dry Air Pressure, lbf/in2 Ps = Saturated Air Pressure, lbf/in 2 Pv = Water Vapor Pressure, lbf/in 2 Ra = Gas constant of Dry Air Rv = Gas constant of Water Vapor T = Dry Bulb Temperature, 'F Tw = Wet Bulb Temperature, 'F V = Moist air Volume, ft 3 W = Moist air Specific Humidity xv = Mole Fraction of Water Vapor in Moist Air xS= Mole Fraction of Water Vapor in Saturated Air= Moist Air Relative Humidity p = Moist air Density, Ibm/ft 3 Pa = Dry Air Density, ibm/ft 3 Pv = Water Vapor Density, Ibm/ft 3 2. REFERENCES (1) Proto-Power Calculation 96-069, Fluid Properties 
-Moist Air -Range 8&deg;F to 300'F, Revision -, dated 12/2/96 (2) Heating Ventilating, and Air Conditioning Analysis and Design, F. C. McQuiston and J. D.Parker, Second Edition, John Wiley & Sons, Inc., 1982 (3) ASHRAE Handbook 1981 Fundamentals, American Society of Heating, Refrigerating and Air Conditioning Engineers, Inc., 1982 Proto-Power Calc: 97-198 

==Attachment:==

H Rev: A Page 2 of 13 
: 3. MOIST AIR DENSITY For dry air: P =P-P, Equation [4]Equation [5](144) P,--R ) (459.67 +T)where: R 2= 53.352 (ft-lbf)/(lbm-&deg;R)
For water vapor: P =(144] P, H=R ,)(459.67 
+T)where: R, = 85.778 (ft-lbf)/(lbm-0 R)For moist air: Equation [6]P =P +p,, 4. SATURATED WATER VAPOR PRESSURE P, (T)= a + bT + cT 2++/-dT' + eT 4+ f 5 Equation [7]Equation [8]Where;a = 0.02358607 b = 0.001007276 c = 0.00001888033 d = 0.0000003775047 e = 4.871208E-10 f= 2.109071E-11 Proto-Power Calc: 97-198 

==Attachment:==

H Rev: A Page 3 of 13 
: 5. WATER VAPOR PRESSURE f (T",)= a + b T, + cT.2 + dlT' + eT+,4 +7f, 5 p, (P, T, T,)= [(2T,. -T- 
-P(T,, -T)(T,, -2800)Equation [9]Equation [10]Where: a = 0.02358607 b = 0.001007276 c = 0.00001888033 d = 0.0000003775047 e = 4.871208E-10 f= 2.109071E-1 1 WR, P R, +(WR 1 ,)Equation [11 ]6. MOIST AIR SPECIFIC HUMIDITY W= m-- p--ma Pa Equation [12]Where: mvR,. (459.67 + T)m R (459.67 + T)Equation [13]Equation [ 14]7. MOIST AIR RELATIVE HUMIDITY xv I&#xfd;x, F&#xfd;Equation [ 15]Proto-Power Calc: 97-198 

==Attachment:==

H Rev: A Page 4 of 13 6 Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Moist Air Relative Humidity: Saturated Air Pressure: Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Specific Humidity: Equation Coefficients:
Given Dry Bulb and Relative Humidity T=RH=Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =Pv = RH*Ps Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =W = Rho v / Rho a =a=b=C=d=e=f=14.315 70 40 0.363236046 0.145294418 14.16970558

==0.0 72204994==
0.000460501

==0.0 72665495==
0.006377682 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-1 1 psia OF psia psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 Equation [8]Equation [151 Equation [41 Equation [5]Equation [6]Equation [7]Equation [12]0 0>-4 g--00:A / e C C / 72 <C),N Cg 1 A, PC) ,A.
Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Wet Bulb Temperature:
Wet Bulb Temp. Function: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Specific Humidity: Moist Air Relative Humidity: Equation Coefficients:
Given Dry Bulb and Wet Bulb Temperatures P =14.315 T =150 Tw= 92.00 F(Tw) = a+(b*Tw)+(c*Tw 2)+(d*Tw 3)+(e*Tw 4)+(f*Tw 5) 0.743918919 Pv = (((2*Tw-T-2800)*F(Tw))-P*(Tw-T))/(Tw-2800) 
= 0.453253224 Pa =P -Pv = 13.86174678 Rho a = (144/53.352)*(Pa/(459.67+T)) 
= 0.061367004 Rho v = (144/85.778)*(Pv/(459.67+T)) 
= 0.001248052 Rho= Rho a + Rho v = 0.062615056 Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) = 3.721743953 W = Rho v / Rho a 0.020337508 RH = Pv /Ps = 12.17852 a = 2.358607E-02 b = 1.007276E-03 C = 1.888033E-05 d = 3.775047E-07 e = 4.871208E-10 f = 2.109071E-1 1 psia OF OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Equation [9]Equation [10]Equation [41 Equation [5]Equation [6]Equation [7]Equation [8]Equation [12]Equation [15]>00 0 00 Coll/ /7 IV A-r Moist Air Properties 
-- Given Dry Bulb and Wet Bulb Temperatures Total Pressure:
P -14.315 Dry Bulb Temperature:
T = 148 Wet Bulb Temperature:
Tw = 91.60 Wet Bulb Temp. Function:
F(Tw) = a+(b*Tw)+(c*Tw 2)+(d*Tw 3)+(e*Tw 4)+(f*Tw 5) 0.7347'Water Vapor Pressure:
Pv = (((2*Tw-T-2800)*F(Tw))-P*(Tw-T))/(Tw-2800) 
= 0.4519" Dry Air Pressure:
Pa =P -Pv = 13.863(Dry Air Density: Rho a = (144/53.352)*(Pa/(459.67+T)) 
= 0.0615 Water Vapor Density: Rho v = (144/85.778)*(Pv/(459.67+T)) 
= Moist Air Density: Rho = Rho a + Rho v = 0.0628, Saturated Air Pressure:
Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) = 3.5413" Moist Air Specific Humidity:
W = Rho v / Rho a 0.0202;Moist Air Relative Humidity:
RH = Pv /Ps =Equation Coefficients:
a = 2.3586(b = 1.0072;C = 1.8880&#xfd;d = 3.7750e e = 4.8712(f = 2.1090-psia OF OF 13202 15914 psia)8409 psia r4919 Ibm/ft 3 18465 Ibm/ft 3 23384 Ibm/ft 3 36347 psia 75546 17 %016)7E-02 76E-03 33E-05 47E-07)8E-10 T 1E-11 Equation [9]Equation [10]Equation [41 Equation [5]Equation [6]Equation [7]Equation [8]Equation [12]Equation [15]0-t g-6 0 00 Ke/~e~t'7 IL~t Moist Air Properties 
-- Given Dry Bulb and Relative Humidity Total Pressure:
P =Dry Bulb Temperature:
T =Moist Air Relative Humidity:
RH =Saturated Air Pressure:
Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =Vapor Pressure:
Pv = RH*Ps Dry Air Pressure:
Pa =P -Pv =Dry Air Density: Rho a = (144153.352)*(PaI(459.67+T)) 
=Water Vapor Density: Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Moist Air Density: Rho = Rho a + Rho v=Specific Humidity:
W = Rho v / Rho a =Equation Coefficients:
a =b=C=d=e=f=14.315 148 12.76 3.541336347 0.451874518 13.86312548

==0.0 61575103==
0.001248351

==0.0 62823454==
0.020273629 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-1 1 psia OF psia psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 Equation [8]Equation [15]Equation [4]Equation [5]Equation [6]Equation [7]Equation [12]0o 0 40 00.0/)&#xfd; / 11, S 1, 1 &#xfd; C-Z&#xfd; -/7 %rl -,- A &#xfd;&#xfd; e,-x C e- C6 /1&#xfd;1 IAI 101 Il-f A7./ eX, Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity:> -x;Equation Coefficients:
0 0 0 Given Dry Bulb and Specific Humidity Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v=Ps a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*Ts) =RH = Pv /Ps =a=b=C=d=e=f=14.315 104.11 0.020273629 0.451874518 13.86312548

==0.0 66368695==
0.001345534

==0.0 67714229==
1.074274081 42.06324307 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-1 0 2.109071E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ib m/ft 3 psia Equation [11]Equation [4]Equation [5]Equation [61 Equation [7]Equation [8]Equation [15]1&#xfd;-;I-(C/ez&#xfd;V-I Moist Air Properties 
-- Given Dry Bulb and Specific Humidity Total Pressure:
P =Dry Bulb Temperature:
T =Specific Humidity:
W =Water Vapor Pressure:
Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Dry Air Pressure:
Pa =P -Pv =Dry Air Density: Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Water Vapor Density: Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Moist Air Density: Rho = Rho a + Rho v =Saturated Air Pressure:
Ps a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =Moist Air Relative Humidity:
RH -Pv /Ps =Equation Coefficients:
a =14.315 106.11 0.020273629 0.451874518 13.86312548

==0.0 66134085==
0.001340778

==0.0 67474863==
1.139525693 39.65461425 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]CD CD 0 0j 0 0.CD0 00 b C d e f 60- f- &#xfd;Ouf/c&#xfd;(&#xfd;O' 4,ell( A&#xfd;o tt J, (S&#xfd;rtli C C )
Moist Air Properti Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidit Equation Coefficients:
00 00 0 0 Cc,, Given Dry Bulb and Specific Humidity..Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv/Ps=a=b=C=d=e=f=14.315 118.45 0.020273629 0.451874518 13.86312548

==0.0 6472245==
0.001312159

==0.0 66034609==
1.622837933 27.8447101 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-11 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]?~ (c~ ,vgr A. ~ ~ &#xa3;/4tu4;e7 Z1j 0-&#xfd;- 'I\Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure;Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
00 0 0 0_Given Dry Bulb and Specific Humidity W=.Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv/Ps a=b=C=d=e=f=14.315 116.7 0.020273629 0.451874518 13.86312548

==0.0 64918963==
0.001316143

==0.0 66235106==
1.545095034 29.2457427 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-11 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Equation [111 Equation [41 Equation [51 Equation [6]Equation [7]Equation [8]Equation [15]0 00 ( 7ZIJ6< f , 6.7-0 coc 
@Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
e o S00 Given Dry Bulb and Specific Humidity Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5)RH = Pv /Ps =a=b=C-d=e=f=14.315 120.05 0.020273629 0.451874518 13.86312548

==0.0 64543819==
0.001308537

==0.0 65852356==
1.696833221 26.63046152 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-1 1 psia OF psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 psia Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]$ ~ ~ ~ ~ ~~~0 /-//( /;6tS 7~~I ow Attachment I to Proto-Power Calculation 97-198 Revision A Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 1 of 14 15:35:59 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHIX-0000)
CornEd -- LaSalle Data Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils.Limiting Flow Analysis -- 66.5 gpm 07/10/98 Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side F 1 l 33.5746710acff 
.........
O0-gpm Inlet Dry Bulb Temp 150.00 OF 105.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature OF OF Outlet Wet Bulb Temp OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr.ft-'F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F)
Fresh Water 0.002000 0.002000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 20.00 0.5270 0.6250 2.000 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 2 of 14 15:35:59 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHIX-0000) 7/10/98 ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 66.5 gpm Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfim)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (IF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm) 39.20 Air Flow (acfin) 29,956.75 Tube Inlet Temp (IF) 100.00 Air Inlet Temp (IF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (IF) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 3 of 14 15:35:59 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 66.5 gpm 07/10/98 W I Extrapolation Calculation Summary tE II I.Mass Flow (Ibm/hr)Inlet Temperature 
("F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft hr)Density (lbmfft 3)Cp (BTU/Ibm"'F)
K (BTU/hr.ft-&deg;F)
Air-Side 110,700.30 148.00 130.41 Tube-Side 19,492.05 100.00 124.99 Tube-Side hi (BTU/hr-ft 2"&deg;F)j Factor Air-Side ho (BTU/hr ft 2-IF)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr. ft 2.&deg;F/BTU)U Overall (BTU/hr-ft2.&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00024732

==0.0 3171750==
2,870.05 487,103 487,103 II Extrapolation Calculation for Row l(Dry)II 1 Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft hr)Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr.ft'OF)
Air-Side 110,700.30 148.00 143.62 0.0203 0.0203 145.81 135.07 5,764.99 2,095 0.7253 0.0491 0.0620 0.2402 0.0163 Tube-Side 19,492.05 113.92 126.39 120.15 129.53 0.72 5,254 3.6287 1.3445 1.2339 61.7093 0.9989 0.3701 Tube-Side hi (BTU/hr-ft2-IF) 274.08 j Factor 0.0105 Air-Side ho (BTU/hr.ft 2."F) 18.09 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr-ft2. F/BTU) 0.03171750 U Overall (BTU/hr.ft2.IF)
Effective Area (f1 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.75 717.51 25.09 121,421 0.8904 121,421 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 4 of 14 Air Mass Velocity (Lbm/hrft'2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:35:59 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 66.5 gpm 07/10/98 0.Extrapolation Calculation for Row 2(Dry)Ii I, Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbrn/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr.ft.'F)
Air-Side 110,700.30 143.62 139.60 0.0203 0.0203 141.61 131.74 5,764.99 2,106 0.7257 0.0488 0.0625 0.2402 0.0162 Tube-Side 19,492.05 112.16 123.60 117.88 126.68 0.72 5,142 3.7155 1.3738 1.2660 61.7443 0.9988 0.3693 Tube-Side hi (BTU/hr.ft 2'0 F) 267.85 j Factor 0.0105 Air-Side ho (BTU/hr' ft 2 -F) 18.05 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr'ft 2-&deg;F/BTU) 0.03171750 U Overall (BTU/hr'ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.68 717.51 23.21 111,304 0.8906 111,304 M -11I Extrapolation Calculation for Row 3(Dry)II Air-Side Mass Flow (lbm/hr) 110,700.30 Inlet Temperature (OF) 139.60 Outlet Temperature 
(&deg;F) 134.69 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 137.14 Skin Temperature (OF) 125.10 Velocity *** 5,764.99 Reynold's Number 2,118 Prandtl Number 0.7261 Bulk Visc (Ibm/ft-hr) 0.0486 Skin Visc (Ibm/ft hr)Density (lbm/ft 3) 0.0630 Cp (BTU/Ibm.&deg;F) 0.2402 K (BTU/hr.ft-&deg;F) 0.0161 Tube-Side 19,492.05 99.96 113.92 106.94 118.92 0.72 4,614 4.1846 1.5309 1.3603 61.9027 0.9988 0.3654 Tube-Side hi (BTU/hr-ft 2.&deg;F) 239.61 j Factor 0.0105 Air-Side ho (BTU/hr.ft 2.0 F) 18.01 Tube Wall Resistance (hr-ft 2_-F/BTU 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.03171750 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.40 717.51 29.60 135,899 0.8908 135,899 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 5 of 14*** Air Mass Velocity (Lbnmlhr ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:35:59 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 66.5 gpm 07/10/98 Extrapolation Calculation for Row 4(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft hr)Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/lbm'0 F)K (BTU/hrlft.&deg;F)
Air-Side 110,700.30 134.69 130.41 0.0203 0.0203 132.55 122.03 5,764.99 2,131 0.7265 0.0483 0.0634 0.2402 0.0160 Tube-Side 19,492.05 99.99 112.16 106.08 116.64 0.72 4,574 4.2255 1.5445 1.3902 61.9144 0.9989 0.3651 Tube-Side hi (BTU/hr ftV-&deg;F) 236.84 j Factor 0.0105 Air-Side ho (BTU/hr-ft 2 -F) 17.97 Tube Wall Resistance (hr-ft2.&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft 2"&deg;F/BTU) 0.03171750 U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTUihr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.36 717.51 25.95 118,479 0.8910 118,479 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 6 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation Coefficients:
Given Dry Bulb and Specific Humidity W=Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps= a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T 5) =RH = Pv /Ps =a=b=C=d=e=f=14.315 psia 130.41 OF 0.020273629 0.451874518 psia 13.86312548 psia 0.063410627 Ibm/ft 3 0.001285563 Ibm/ft 3 0.06469619 Ibm/ft 3 2.249688203 psia L20.0O8609537%
2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071E-1 1 Equation [11]Equation [4]Equation [5]Equation [61 Equation [7]Equation [8]Equation [15]0 0 CD 00 Ile, I Oki Ssr' 15:44:15 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils -Limiting Flow Analysis -- 66.5 gpm 07/10/98 Air Coil Heat Exchanger Input Parameters Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Air-Side Tube-Side-32.49370-0-1 f _ :270 gpmr OF 105.00 OF OF OF OF OF Fresh Water 0.002000 0.002000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr.ft.iF) 105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 20.00 0.5270 0.6250 1.500 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 8 of 14 15:44:15 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 66.5 gpm 7/10/98 IF- Calculation Specifications I Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (OF)Air Dry Bulb Temp Out (OF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (fF)Wet Bulb Temp Out (OF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm)Air Flow (acfm)Tube Inlet Temp (OF)Air Inlet Temp (OF)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (OF)Atmospheric Pressure 27.30 29,089.80 100.00 130.4 20.09 0.00 14.315 ,Gb,,j 4;(o Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 9 of 14 15:44:15 PROTO-HX 3.01 by Proto-Power Corporation (SN#IIPHX-0000)
CornEd -- LaSalle Calculation Report for: I(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 66.5 gpm 07/10/98 NA R Extrapolation Calculation Summary II IL-*Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr-ft.&deg;F)
Air-Side 110,700.34 130.41 118.45 Tube-Side 13,574.82 100.00 124.42 Tube-Side hi (BTU/hr ft 2.&deg;F)j Factor Air-Side ho (BTU/hr ft2-&deg;F)Tube Wall Resistance (hr-ftP-&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr'ft 2 0'F/BTU) 0.03171750 U Overall (BTU/hr-ftl 2.F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5,740.10 331,168 331,168 OWT I Extrapolation Calculation for Row l(Dry)11 Air-Side Mass Flow (lbm/hr) 110,700.34 Inlet Teniperature 
(&deg;F) 130.41 Outlet Temperature (OF) 129.43 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 129.92 Skin Temperature 
(&deg;F) 127.69 Velocity *** 5,764.99 Reynold's Number 1,603 Prandtl Number 0.7267 Bulk Visc (lbm/ft-hr) 0.0481 Skin Visc (Ibm/ft-hr)
Density (lbrn/fl 3) 0.0635 Cp (BTU/lbm.&deg;F) 0.2402 K (BTU/hr-ft.&deg;F) 0.0159 Tube-Side 13,574.82 121.01 125.01 123.01 126.44 0.50 3,758 3.5243 1.3091 1.2686 61.6644 0.9989 0.3710 Tube-Side hi (BTU/hr-ftl 2.F) 168.64 j Factor 0.0116 Air-Side ho (BTU/hr. ft 2-&deg;F) 19.81 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2 0.F/BTU) 0.03171750 U Overall (BTU/hr.ft 2.0 F)Effective Area (f)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.64 717.51 6.70 27,115 0.8816 27,115 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 10 of 14*** Air Mass Velocity (Lbmihr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:44:15 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 66.5 gpm 07/10/98 in Extrapolation Calculation for Row 2(Dry)I[II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ftlhr)
Density (lbm/ft 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft'&deg;F)
Air-Side 110,700.34 129.43 128.42 0.0203 0.0203 128.93 126.63 5,764.99 1,605 0.7268 0.0480 0.0636 0.2402 0.0159 Tube-Side 13,574.82 119.71 123.83 121.77 125.35 0.50 3,715 3.5691 1.3243 1.2813 61.6841 0.9988 0.3706 Tube-Side hi (BTU/hr'ft 2"&deg;F) 166.24 j Factor 0.0116 Air-Side ho (BTU/hr'ft 2-&deg;F) 19.80 Tube Wall Resistance (hr- ft.&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 3171750==
U Overall (BTU/hr. ft2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.60 717.51 6.95 27,904 0.8816 27,904 II Extrapolation Calculation for Row 3(Dry)II.3 Mass Flow (lbm/hr)Inlet Tqmperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (lbm/fP)Cp (BTU/Ibm 0'F)K (BTU/hr-ft-&deg;F)
Air-Side 110,700.34 128.42 127.12 0.0203 0.0203 127.77 124.81 5,764.99 1,608 0.7269 0.0480 0.0638 0.2402 0.0159 Tube-Side 13,574.82 115.70 121.01 118.36 123.16 0.50 3,597 3.6970 1.3676 1.3073 61.7370 0.9988 0.3695 Tube-Side hi (BTU/hr-ft 2-&deg;F) 159.78 j Factor 0.0115 Air-Side ho (BTU/hr.ft 2-&deg;F) 19.79 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr ffV.&deg;F/BTU) 

==0.0 3171750==
U Overall (BTU/hr ft 2-IF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.49 717.51 9.15 36,016 0.8817 36,016 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 11 of 14*** Air Mass Velocity (Lbm/hr-ft2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average 'r 15:44:15 PROTO-HX 3.01 by Proto-Power Corporation (SN#PItX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 66.5 gpm 07/10/98 M Extrapolation Calculation for Row 4(Dry)II I!I.Mass Flow (Ibm/lr)Inlet Temperature (0 F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/firhr)
Density (Ibm/fl 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft.&deg;F)
Air-Side 110,700.34 127.12 125.83 0.0203 0.0203 126.48 123.55 5,764.99 1,611 0.7269 0.0479 0.0639 0.2402 0.0158 Tube-Side 13,574.82 114.45 119.71 117.08 121.91 0.50 3,554 3.7468 1.3844 1.3226 61.7564 0.9988 0.3690 Tube-Side hi (BTU/Ihrft2"&deg;F) 157.26 j Factor 0.0115 Air-Side ho (BTU/hr-ft 2.'F) 19.77 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr- ft 2"&deg;F/BTU) 0.03171750 U Overall (BTU/hr" ft 2.OF)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTUihr)Heat to Condensate (BTU/hr)5.44 717.51 9.14 35,666 0.8817 35,666 1I Extrapolation Calculation for Row 5(Dry)II I. 'I Mass Flow (Ibm/hr)Inlet Tqmperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (Ibm/ftfhr)
Density (Ibm/ft 3)Cp (BTU/Ibm-OF)
K (BTU/hr-fl.&deg;F)
Air-Side 110,700.34 125.83 124.14 0.0203 0.0203 124.99 121.13 5,764.99 1,614 0.7271 0.0478 0.0641 0.2402 0.0158 Tube-Side 13,574.82 108.77 115.70 112.24 118.98 0.50 3,390 3.9460 1.4513 1.3595 61.8280 0.9988 0.3673 Tube-Side hi (BTU/hr.ft 2-&deg;F) 148.04 j Factor 0.0115 Air-Side ho (BTU/hr.ft' 2.F) 19.76 Tube Wall Resistance (hr- ft2.F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft 2.&deg;F/BTU) 0.03171750 U Overall (BTU/hr. ft 2 -F)Effective Area (ff 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.27 717.51.12.41 46,951 0.8818 46,951 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 12 of 14*** Air Mass Velocity (Lbm/hr-ft'), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:44:15 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 66.5 gpm 07/10/98 11 Extrapolation Calculation for Row!6(Dry)
II'is Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Visc (lbm/ifthr)
Density (Ibm/fl3)Cp (BTU/Ibm-0 F)K (BTU/hr'ft--F)
Air-Side 110,700.34 124.14 122.53 0.0203 0.0203 123.34 119.68 5,764.99 1,617 0.7272 0.0477 0.0643 0.2402 0.0158 Tube-Side 13,574.82 107.89 114.45 111.17 117.65 0.50 3,354 3.9922 1.4667 1.3768 61.8433 0.9988 0.3670 Tube-Side hi (BTU/hr-ft 2" 0 F) 145.86 j Factor 0.0115 Air-Side ho (BTU/hr'ft 2 1-F) 19.74 Tube Wall Resistance (hr-ift2.F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft 2.0 F/BTU) 0.03171750 U Overall (BTU/hr. ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.23 717.51 11.85 44,460 0.8819 44,460 1&#xfd;Extrapolation Calculation for Row 7(Dry)II Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/f-hr)
Skin Visc (lbm/ft-hr)
Density (ibm/ift)Cp (BTU/Ibm.0 F)K (BTU/hr. ft-F)Air-Side 110,700.34 122.53 120.39 0.0203 0.0203 121.46 116.59 5,764.99 1,621 0.7273 0.0476 0.0645 0.2402 0.0157 Tube-Side 13,574.82 100.01 108.77 104.39 113.88 0.50 3,130 4.3075 1.5717 1.4280 61.9371 0.9988 0.3645 Tube-Side hi (BTU/hr-ft 2.F) 132.83 j Factor 0.0115 Air-Side ho (BTU/hr-ft2.&deg;F) 19.72 Tube Wall Resistance (hr-fi2.&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr- ft 2.F/BTU) 0.03171750 U Overall (BTU/hr-ft2.
F)Effective Area (fl 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.97 717.51 16.67 59,406 0.8820 59,406 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 13 of 14*** Air Mass Velocity (Lbnfhr.ft), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 15:44:15 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 66.5 gpm 07/10/98 W Extrapolation Calculation for Row 8(Dry)11 I.Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (lbm/ftrhr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr-fl-&deg;F)
Air-Side 110,700.34 120.39 118.45 0.0203 0.0203 119.42 115.02 5,764.99 1,626 0.7274 0.0474 0.0647 0.2402 0.0157 Tube-Side 13,574.82 99.98 107.89 103.94 112.57 0.50 3,115 4.3302 1.5792 1.4465 61.9432 0.9989 0.3643 Tube-Side hi (BTU/hr'ft 2"&deg;F) 131.75 j Factor 0.0115 Air-Side ho (BTU/hr-ft 2 .F) 19.70 Tube Wall Resistance (hr-ft2.&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft 2-F/BTU) 0.03171750 U Overall (BTU/hr'ft 2 -F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.94 717.51 15.13 53,651 0.8821 53,651 Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 14 of 14*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Attachment J to Proto-Power Calculation 97-198 Revision A Proto-Power Catc: 97-198 

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J Rev: A Page 1 of 55 Proto-HX Analytical Uncertainty Calculation
[Circular Fin Air Coil Application]
Purpose The purpose of the following calculation is to evaluate the analytical uncertainty associated with the analysis of test data and the computation of heat transfer rate at a given extrapolation condition.
This calculation focuses only on the parameters that are not measured during the thermal performance test but factor into the analysis of the test results. Test parameter measurement uncertainty is treated separately in the test uncertainty analysis.
The calculation of analytical uncertainty is derived for a typical Air Cooler with "n" tube rows.Governing Heat Transfer Equations Heat transfer calculations associated with a heat exchanger generally reduce to satisfying the following equations:
: 1) q = U A 0 LMTD Where: q = Heat transfer rate at test conditions (BTU/hr)U = Overall heat transfer coefficient at test conditions (BTU/hr-*F-ft 
)Ao = Heat transfer surface area referenced to outside (air-side) surface (ft 2)LMTD = Log Mean Temperature Difference at test conditions 
(&deg;F)and 2) q = riacp (To -T,,,) = pQcp AT Where: q = Heat transfer rate at test conditions (BTU/hr)ri = Mass flow rate at test conditions (lbm/hr)cp = Specific heat of cooling water at test conditions (Btu/lbm 0-F)TCi = Tube-side inlet temperature at test conditions (OF)TCo = Tube-side outlet temperature at test conditions (OF)p = Density of tube-side fluid at average bulk temperature at test conditions (lbm/ft 3)Q = Volumetric flow rate of tube-side fluid at test conditions (gpm)The first equation is used, in Proto-HX, to evaluate the heat transfer rate from test data. The analytical uncertainties associated with evaluating the fluid properties are usually the only contributors to the overall uncertainty when using this equation.
For a given test condition, the right hand side of the second equation is evaluated such that it matches the measured heat Proto-Power Calc: 97-198 

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J Rev: A Page 2 of 55 transfer rate, "q". In Proto-HX, this means iterating on fouling factor, and therefore "U", until the heat transfer equation is satisfied.
The following equations are used for this iteration:
1 A. LMTD Tesi 3) .RR.= -U qTest Where: R = Overall heat transfer thermal resistance at test conditions (hr-&deg;F-ft 2/ BTU)U = Overall heat transfer coefficient at test conditions (BTU/hr-&deg;F-ft 2)A, -- Outside heat transfer surface area (ft 2)LMTD = Log Mean Temperature Difference at test conditions 
('F)q = Heat transfer rate at test conditions (BTU/hr)and 4) Rf=R R_ (A. 1 ho qi -A hi Where: Rf = Fouling resistance (hr-oF-ft 2/ BTU)R = Overall heat transfer thermal resistance at test conditions (hr- F-ft 2/ BTU)ho = Outside convection film coefficient at test conditions (BTU/hr-cF-ft 2)rl, = Fin surface effectiveness Rw = Wall thermal resistance at test conditions (hr-&deg;F-ft 2/ BTU)A0 = Outside heat transfer surface area (ft2 A i  uInside heat transfer surface area (ft)hi Inside convection film coefficient at test conditions (BTU/hr-&deg;F-ft1)
These same equations must be satisfied when evaluating the capacity of a heat exchanger at a given fouling condition (i.e., when extrapolating to the limiting thermal condition).
The following equations are used for the extrapolation process: 5) R*=Rf+ I + RW,+(A. I ho
* q17-Ai hi Where: R* = Overall thermal resistance at extrapolation conditions (hr-F-ft 2/ BTU)Rf = Calculated fouling resistance (hr-&deg;F-fl 2/ BTU)ho* = Outside convection film coefficient at extrapolation conditions (BTU/hr-&deg;F-ft 2)ms = Fin surface effectiveness Rwv* = Wall thermal resistance at extrapolation conditions(hr-&deg;F-ft2 
/ BTU)A 0  = Outside heat transfer surface area (ft 2)Ai = hiside heat transfer surface area (ft )Proto-Power Calc: 97-198 

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J Rev: A Page 3 of 55 Ili* =Inside convection film coefficient at extrapolation conditions (BTU/hr-&deg;F-ft 2)and 6) q* (l/R*) Ao LMTD* = U*A 0 LMTD*where: q* = Heat transfer rate at extrapolation conditions (BTU/hr)R* = Overall thermal resistance at extrapolation conditions (hr-&deg;F-ft 2/ BTU)U* = Overall heat coefficient at extrapolation conditions (BTU/hr-oF-ft 2)Ao = Heat transfer surface area referenced to outside surface (ft 2)LMTD* = Log Mean Temperature Difference at extrapolation conditions 
('F)Analytical Uncertainty Calculation Methodology The method for calculating the analytical uncertainty associated with this performance analysis method is illustrated as follows: Given a function D = f(A,B,C)The effect on D of slight changes in the independent variables A, B, and C may be calculated by taking the partial derivatives of D with respect to each of the independent variables.
Accordingly, the change in the value of D (i.e., AD) due to changes in each of the independent variables (AA, AB, AC) may be represented by the following equation: AD-AA+ -AB + AC cA dB 9C If AA, AB, AC are the known (or estimated) errors of the independent variables, then the error, AD, associated with the derived value, D, is calculated.
The most probable one standard deviation error representative of AD would be the statistical root mean squared value derived as follows: AD= [(-AA + + A = U-C 67A J 9 10C-Expressing the uncertainty in terms of a percentage of the value of D is simply a matter of including division by the value of D as follows: U, = [(,-D 2( AA) 2 + OD)'AB2 (OD 2AC 21/D cA K D) cB) B D) + -C) -D Proto-Power Calc: 97-198 

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J Rev: A Page 4 of 55 The next six sections of this document provide a step by step approach to calculating the analytical uncertainty associated with the six thermal performance equations outlined above.The specific terms to be evaluated from these equations are as follows: 1) Heat transfer area, A. and area uncertainty, U 4 2) Test condition heat transfer rate, q and heat transfer uncertainty, Uq 3) Test condition thermal resistance, R and thermal resistance uncertainty, UR 4) Observed overall fouling resistance, Rf fouling resistance uncertainty, URf 5) Extrapolation condition thermal resistance, R* and thermal resistance uncertainty, UR*6) Extrapolation condition heat transfer rate, q* and heat transfer rate uncertainty, Uq.All uncertainty equations used in this calculation are based on the methods of Reference 
[ 1 ]. It is assumed that all independent variables in each equation have no influence on each other. For example, in Equation (6), LMTD* and the overall heat transfer coefficient, U*, are independent of each other. More specific assumptions are stated in each section as applicable.
For the rating analysis case (i.e., fouling factor is specified and not calculated from test data), equations 2, 3 and 4 above are not applicable because the uncertainty in the specified fouling factor is zero. The analytical uncertainty calculation, therefore, is reduced to an accounting of area uncertainty from equation 1 and the uncertainty in extrapolation terms per equations 5 and 6.Proto-Power Calc: 97-198 

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J Rev: A Page 5 of 55 
: 1) Uncertainty in Calculation of Heat Transfer Area (A.1 Governing Equation q = U Ao LMTD For Air Coolers with circular fins, the outside tube surface area, the fin surface area and the total outside surface area are given by the following expressions:
Ao.,,, = 7r NTNLLcdo(I-AtFR)
=o. /r2NTNLI-CHf~Ftr 
+ (HF~d.)j ~HF -do)2 + (LtFR -tFj j A.TOU, = NT NL Ucdo (I-tFR) + A[HFItFT + (HF + do)j(Fdj (F;tjj where: NT = Number of tubes per row NL = Number of active tube rows Lc = Effective tube (coil) length (in)do = Tube outside diameter (in)XL = Fin pitch (fins/inch)
HF = Fin height (in)tFR = Thickness of fin at root (in)tFT = Thickness of fin at tip (in)For the case where tFR = tFr = tF, the total area equation reduces to the following:
Ao,,, = )NT NLLU do (I- A tF) + A[HF tF + (HF + do) 1}Ao~oW = /fNTNLLc &#xfd;do -A do tF + 2 [2HF tF + HF'2 -do2 Proto-Power Calc: 97-198 

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J Rev: A Page 6 of 55 Assumptions0 UNL = 0 Ual = 0 Analysis U ,. 2(O ,,) ' d A. )' +Y >2____ 6j d & A .'3L A. I2 JA.) 2Y HF A.) 2 A9 )jY where, Cf e )e9d.=zrNTNLL{,(1-AtF)-Ad}
e9LA) = ZNTNLt d. odtF / [2 HFtFH2-d]aA 0=fNTNLL,2 
{HF- d,,}OeA. fN TNLLC2JF F ,rYHF) {F+/-F Proto-Power Calc: 97-198 

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J Rev: A Page 7 of 55 2)Uncertainty in Calculation of Heat Transfer Rate at Test Conditions Governing Equation qres= r ncP (To -T.)= p Qcp AT Assumptions UT =0 UQSw 0 (i.e., temperature and flow rate in the governing equation are measured values with no analytical uncertainites)
Analysis F 2 2 U 2 2 -q estkqes zts' 2Pv '&#xfd;S UQ~~T OC' tes test uq te= (QSW CPAT)2 (UPs +(pQsw AT) 2Kp1 Proto-Power Calc: 97-198 

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J Rev: A Page 8 of 55 
: 3) Uncertainty in Calculation of Thermal Resistance at Test Conditions Governing Equation R I A. U qTest Assumptions ULMTD is negligible Analysis UR _R FE cR fLA 0 1  ( 2 + R ) LITD> )2 R 2 Uqt_2 dA 0 , R dLMTD ) R ~ es URR =[CL M T D 2UAoI + C -A.LM T DD Uq_ 2]qy -UAo (Evaluated in Section 1)Uqw (Evaluated in Section 2)Proto-Power Calc: 97-198 

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J Rev: A Page 9 of 55 4)Uncertainty in Calculation of Fouling Factor at Test Conditions Governing Equation 1 R_ _ -(AO)h 0.o ',f ,hA,)Where, ho'et = effective outside film coefficient 
= (h 0) x (0i)Assumptions O tA) U 0 2 0 C(&#xfd; 2 2 (i.e., the uncertainty in dimensions is negligible compared to the thermal resistance and convection coefficient uncertainties)
Analysis 2,- R f 2 ...&#xfd;f R _2 9 UR (U R 2 + 2o,e----r R + R++; RfI2Uw +(R2[ fJ2 2 2 (AO Y2 1 &#xfd;)2)2 R_( &#xfd;&#xfd;R A i I R f UR (Evaluated in Section 3)Proto-Power Calc: 97-198 

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J Rev: A Page 10 of 55 
: 5) Uncertainty in Calculation of Heat Transfer Resistance at Extrapolation Conditions Governing Equation R* =Rt +- I + R, + o h1 oCf*Al) hi*Assumptions
!9R
* 2___C cR* UA 9A, )~ R&#xfd;*(i.e., the uncertainty in dimensions is negligible compared to the thermal resistance and convection coefficient uncertainties)
Analysis UR R +(OR*) 2 2+ R 2 2 1 2 ]Y2___ U 9R, 2 C 2 + C JC&#xfd;h._2 (UC _ )2 CUA 2  2C; YC2[oR* + _ ,2 AC hi"* K), R*J UR, (Evaluated in Section 4)UR -0 (for extrapolation calculations only, i.e., no fouling calculation)
Proto-Power Calc: 97-198 

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J Rev: A Page 11 of 55 
: 6) Uncertainty in Calculation of Heat Transfer Rate at Extrapolation Conditions Governing Equation q* = (I/R*) (A,) (LMTD*)Assumptions U LMTD ; 0.0 Analysis 2'  2 (UR q.+ q+/A 0)/qCL + (LMTD*)U q R *_- 2A .q* (LMTD")2 R*2 R ii _U 21 LMTD')UR (Evaluated in Section 5)UAo (Evaluated in Section 1)Proto-Power Calc: 97-198 

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J Rev: A Page 12 of 55 7)Uncertainty in Calculation of Extrapolated Heat Transfer for Entire Unit The uncertainties in extrapolated heat transfer, computed for each tube row, are combined in the following manner to yield an overall uncertainty value for the entire air cooler.q lot =qj +q2 +q3 ..i....+qn where," n" is the number of tube rows in the unit.Uqo _ qtot- U__q_ + (Oqlot Uq 2-+ (Oqto, Uq 3 1 ....."....... ( U____,)2 U-q~o k.dq- \, ot qz qoj dq2 \qoj e. qn qtot.[~d ~tot tot 2 tot __~ 21/Assuming that the extrapolated heat transfer rates of the various rows do not depend on each other, the above expression becomes:\2/ 2 2 ~ 21/2.m ..........
U.Uq tot Uq I Uq 2 q 3)q [ totj qtot ) tot )Proto-Power Calc: 97-198 

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J Rev: A Page 13 of 55 FP-R T Co Definition of Analytical Uncertainty Analysis Terms Ao/Ai =di (in) =Ao (ft^2) =do (in) =Udo/do (%) =Udo =Nt=NI=Lambda (fins/in) 
=L (Ft)UL/L (%) =UL(ft) =tfin (in) =Utfin/tfin 
(%) =Utfin (in) =hfin (in) =Uhfin/hfin 
(%) =Uhfin (in) =Mdotc (Ibm/hr) =Q (Ft^3Ihr) 
=DT (DegF) =rho (Ibm/ft^3) 
=Urho/rho (%) =Urho =Cp (Btu/Ibm/DegF) 
=UCp/Cp (%) =bCp =qtest (Btu/hr) =LMTD (DegF) =Uo =R = (I/Uo)=Rf [(hr-DegF-ft^2)/Btuj 
=Etas =ho [Btu/(hr-DegF-ft^2)1 
=ho(eff) [Btu/(hr-DegF-ft^2)j 
=Uho/ho (%)Uho =hi [Btu/(hr-DegF-ftA2)1 
=Uhi/hi (%) =Uhi =Rw [(hr-DegF-ft^2)/Btu=
URw/Rw (%) =URw =Heat transfer area ratio Tube inside diameter Outside heat transfer area Tube outside diameter Uncertainty in tube outside diameter (as a percentage)
Uncertainty in tube outside diameter (absolute)
Number of tubes in given row Number of rows in heat exchanger Fin pitch Tube length Uncertainty in tube length (as a percentage)
Uncertainty in tube length (absolute)
Fin thickness Uncertainty in fin thickness (as a percentage)
Uncertainty in fin thickness (absolute)
Fin height Uncertainty in fin height (as a percentage)
Uncertainty in fin height (absolute)
Cooling water mass flow rate Cooling water volumetric flow rate Cooling water temperature difference (inlet to outlet)Cooling water density Uncertainty in cooling water density (as a percentage)
Uncertainty in cooling water density (absolute)
Cooling water specific heat Uncertainty in cooling water specific heat (as a percentage)
Uncertainty in cooling water specific heat (absolute)
Calculated test heat transfer for coil section Calculated log mean temperature difference Heat transfer coefficient Heat transfer resistance Fouling resistance Outside film coefficient Effective outside film coefficient Uncertainty in outside film coefficient (as a percentage)
Uncertainty in outside film coefficient (absolute)
Inside film coefficient Uncertainty in inside film coefficient (as a percentage)
Uncertainty in inside film coefficient (absolute)
Wall thermal resistance Uncertainty in wall resistance (as a percentage)
Uncertainty in wall resistance (absolute)
Proto-Power Calc: 97-198 

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J Rev: A Page 14 of 55 VY4FRONT.XLS Page I 0 Analytical Uncertainty Analysis -- Uncertainty Inputs Parameter Udo/do ULc/Lc Utfin/tfin Uhfin/hfin Urho/rho UCp/Cp Uho/ho Uhi/hi URw/Rw Notes: (2)(3)(4)(5)(6)(7)Definition Uncertainty in tube outside diameter Uncertainty in coil (tube) length Uncertainty in fin thickness Uncertainty in circular fin height Uncertainty in cooling water density Uncertainty in cooling water specific heat Uncertainty in outside film coefficient Uncertainty in inside film coefficient Uncertainty in wall resistance Value (%)8.00 0.24 4.17 1.48 2.00 2.00 15.00 15.00 2.00 (1)(2)(3)(4)(5)(5)(6)(7)(5)Measurement of 5/8" +/- 0.05" yields an uncertainty of 8.0%Measurement of 105" +/- 0.25" yields an uncertainty of 0.24%Specified as 0.012" with estimated tolerance of 0.0005" yields an uncertainty of 4.17%Measurement of 1.347" +/- 0.02" yields an uncertainty of 1.48%Uncertainty in property values is estimated as 2%Uncertainty in outside film coefficient is estimated as 15%Uncertainty in inside film coefficient is estimated as 15%Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 15 of 55 VY4FRONT.XLS Page 2 PROTO-IIX Report -- Model Inputs 16:04:35 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 07/10/98 CornEd -- LaSalle Data Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Air Coil Heat Exchanger Input Parameters Fluid Quantity, Total Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Air-Side 33546 acfm 150 &deg;F 92 &deg;F*F'F Tube-Side 118 gpm 105 'F Fresh Water 0.002 0.002 14.315 1 0 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-&deg;F) 105 10 128 0.012 0.012 1.347 2 4 20 20 0.527 0.625 2 1.37 2 225 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 16 of 55 VY4FRONT.XLS Page 3 PROTO-HX Report -- Fouling Calculation Output Fouling Calculation Summary There is no fouling calculation for the rating analysis case.Uncertainty in use of design fouling in rating analysis is zero.Proto-Power Ca~c: 97-198 

==Attachment:==

J Rev: A Page 17 of 55 VY4FRONT.XLS Page 4 PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Extrapolation Calculation Summary Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
('F)Inlet Specific Humidity Outlet Specific Humidity Average Temp ("F)Skin Temperature 
(&deg;F)Velocity **" Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (Ibm/ft hr)Density (Ibmlftl)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ft&deg;F)
Tube-Side 110700.3 19492.05 Tube-Side hi (BTU/hr-ft 2.&deg;F)148 100 j Factor 130.4103 124.9938 Air-Side ho (BTU/hr-ftW.&deg;F)
Tube Wall Resistance (hr-ft'.F/BTU)
Overall Fouling (hr.ftV.&deg;F/BTU)
U Overall (BTU/hr-ft'-&deg;F)
Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.000247 0.031717 2870.05 487103.2 487103.2 Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (*F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number PrandtU Number Bulk Visc (Ibm/ft hr)Skin Visc (Ibm/ft hr)Density (Ibm/ft')Cp (BTU/Ibm-&deg;F)
K (BTU/hr.ft.&deg;F) 110700.3 148 143.6154 0.020268 0.020268 145.8077 135.0657 5764.99 2094.879 0.725319 0.049099 0.062037 0.240245 0.016263 Extrapolation Calculation for Row 1(Dry)Tube-Side 19492.05 Tube-Side hi (BTU/hr.ft 2 -F)113.9172 j Factor 126.3906 Air-Side ho (BTU/hr-ft'-"F)
Tube Wall Resistance (hr.ft 2-&deg;F/BTU)Overall Fouling (hr.ft 2-*F/BTU)120.1535 129.5346 U Overall (BTU/hr.ft 2.&deg;F)0.724046 Effective Area (ft 2)5253.983 LMTD 3.628692 Total Heat Transferred (BTU/hr)1.344496 1.233925 Surface Effectiveness (Eta)61.70928 Sensible Heat Transferred (BTU/hr)0.998902 Latent Heat Transferred (BTU/hr)0.370081 Heat to Condensate (BTU/hr)274.0782 0.010545 18.09153 0.000247 0.031717 6.74503 717.5125 25.08881 121420.9 0.89039 121420.9 Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
("F)Velocity **Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/ft')Cp (BTU/Ibm.F)
K (BTU/hr.ft."F) 110700.3 143.6154 139.5961 0.020268 0.020268 141.6058 131.7434 5764.99 2106 0.725703 0.048839 0.062453 0.240245 0.016168 Extrapolation Calculation for Row 2(Dry)Tube-Side 19492.05 Tube-Side hi (BTU/hr.ft 2.OF)112.1624 j Factor 123.5969 Air-Side ho (BTU/hr-ft2.&deg;F)
Tube Wall Resistance (hr-ft=.&deg;F/BTU)
Overall Fouling (hr-ft 2-F/BTU)117.8787 126.6751 U Overall (BTU/hr.ft2.*F) 0.723636 Effective Area (ft')5141.879 LMTD 3.71548 Total Heat Transferred (BTU/hr)1.373809 1.265977 Surface Effectiveness (Eta)61.74425 Sensible Heat Transferred (BTU/hr)0.998801 Latent Heat Transferred (BTU/hr)0.369311 Heat to Condensate (BTU/hr)267.8463 0.010526 18.05222 0.000247 0.031717 6.682724 717.5125 23.21264 111304.1 0.890595 111304.1 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 18 of 55 VY4FRONT.XLS Page 5 PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Extrapolation Calculation for Row 3(Dry)Air-Side Mass Flow (Ibm/hr)Inlet Temperature (fF)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Tempeiature 
(*F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (Ibm/ft-hr)
Density (ibm/ift)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ftA'F) 110700.3 139.5961 134.6887 0.020268 0.020268 137.1425 125.0976 5764.99 2118.008 0.726093 0.048562 Tube-Side 19492.05 Tube-Side hi (BTU/hr.ft 2-"F)99.9568 j Factor 113.9172 Air-Side ho (BTU* : T.K. WaIIl cl R- ant-e lhr.ft2 I/hr ft-'.F)Overall Fouling (hr.ftl-&deg;F/BTU) 106.9361 118.9204 U Overall (BTU/hr-ft'F) 0.721783 Effective Area (ft2)4614.305 LMTD 4.184624 Total Heat Transferred (BTU/hr)1.530883 1.360255 Surface Effectiveness (Eta)61.90271 Sensible Heat Transferred (BTU/hr)0.998808 Latent Heat Transferred (BTU/hr)0.365418 Heat to Condensate (BTU/hr)239.6102 0.010505 18.01047 0.000247 0.031717 6.397715 717.5125 29.6048 135899.1 0.890812 135899.1 0.062969 0.240245 0.016068 Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(*F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (*F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft.hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft-&deg;F) 110700.3 134.6887 130.4103 0.020268 0.020268 132.5496 122.0284 5764.99 2130.582 0.726475 0.048276 0.063425 0.240245 0.015965 Extrapolation Calculation for Row 4(Dry)Tube-Side 19492.05 Tube-Side hi (BTU/hr-ftl'.F) 99.99173 j Factor 112.1624 Air-Side ho (BTU/hr.ft 2.'F)Tube Wall Resistance (hr.ft 2-&deg;F/BTU)Overall Fouling (hr-ftl.&deg;F/BTU) 106.0765 116.6443 U Overall (BTU/hr.ft 2-&deg;F)0.721646 Effective Area (Wft)4573.701 LMTD 4.225521 Total Heat Transferred (BTU/hr)1.544474 1.390163 Surface Effectiveness (Eta)61.91445 Sensible Heat Transferred (BTU/hr)0.998871 Latent Heat Transferred (BTU/hr)0.365098 Heat to Condensate (BTU/hr)236.841 0.010484 17.96752 0.000247 0.031717 6.362774 717.5125 25.95168 118479 0.891036 118479 Air Mass Velocity (Lbm/hr.ft2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Proto-Power Caic: 97-198 

==Attachment:==

J Rev: A Page 19 of 55 VY4FRONT.XLS Page 6 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 1)L PROTO-HX Output -Fouling Calculation di (ft) =Al (ftA2) =Ao (ftA2) =AoIAI : do (ft) =Udo/do (%)Udo (ft)=Nt =N8=Lambda (finsift) 
=L (ft)ULL(%)II. PROTO-HX Output -- Extrapolation Calculation di (ft) = [0.43916667 Al (ft^2) = 2414444854 Ao (ftA2) = 7f75125349 Ao/Ai 29.71749526 do (ft) = 0.052083333 Udo/do (%) =Udo (it) -0004166667 Nt =-NI = L j2]Lambda (fins/ft) j 120 L (ft) = 75 ULL (%024 UL(ft) = .0211 UL(ft) =tfin (ft) =Utfin/tfin 
(%) =hfln (ft) =IUhfAlhflB (i) -Mdotc (Ibm/hr) =o (FtA3/hr)DT (DegF)rho (Ibm/ftA3) 
=Urho/rho (%) =Cp (Btu/Ibm/DegF) a UCp/Cp (%" =Utfin (ft) =(Jhtiu (ft) =Urho =UCp =tfn (ft) =Utfln/tfin 
(%)hfln (ft) =Uhlan/hfin 
(%) =Mdotc" (Ibm/hr)Q* (Ft 3/Fhr) =DT* (DegF) =rho* (Ibm/iftA3) 
=Urho*lrhol 
(%)=Cp*
UCp*lCp* (%) =q" (Btu/hr) =LMTD* ( DegF)Uo* =R* = (1/Uo) =Rf [(hr-DegF-ftA2)/Btuj 
=Etas =ho* [Btu/(hr-DegF-ftA2)] 
=ho*(eff) [Btuf(hr-DegF-ft^2)]
Uho*/hoa (%) =hir [BtuI(hr-DegF-ftA2)] 
=UhI*/hl* (%) =Rw" [(hr-OegF-ft^2)/Btuj 
=URw*/Rw* (%) =S 0.001 4.17L Utfln (if) = zo17 1.48I urhf'i (ft)= -0.o01613I 19492.05275 315.8690532 12.47340151J
~02 Urho" = 1.23438585i U0.g8902258 UCp, =~~z~121420.9121 25.08881468 6.745029518 0.14825732

==0.0 31717495==
0.89M38996 18.09152624
: 16.10851332 15 UhO* = 2.416276998 274.0782o3 Uh rr* ,, URw 000247317 U *=f 4.9464;E061 q (Btulhr) =LMTD (DegF) =Uo =R = (l/Uo) =Rf [(hr-DogF-ftA2)IBtuj Etas =ho [Btu/(hr-DoqF-ft 4 2)1 =ho(eff) [Btu/(hr-DegF-ft^2)J Uho/ho (%) =hi [BtuI(hr-OogF-fa2)I 
=UhlIhi (%) =Rw [(hr-DegF-ff^2)/Btu] 
=URw/Rw (%) =Uho =Uhl =URw =Proto-power Ca/c: 97-198 

==Attachment:==

J Rev: A Page 20 of 55 VY4FRCJNr.XT.SXP Page 7 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 1)I Analytical Uncertainty in Hleat Transfer Surface Area Ao Do Ud L UL tfin Utfin hin Uhfin UAolAo UAo 717.51253 0.05208 0.00417 8.75000 0.02100 0.00100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivatives: 
-5904.62 82.00 7938.80 14942.99 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty In Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' hoa Uho* hi* Uhi* Rw* URw* Rf URf UR*/R* UR*0.14826 16.10851 2.41628 274.07820 41.11173 0.00025 0.00000 0.03172 OOC"C 0. 12641 0.01874 6 Analytical Uincertaintv in Extrapolated Heat Transfer q" R* UR* Ao UAo LMTD* Uq'lq&deg; Uq" 121420.9121 0.14826 0.01874 717.51253 34.99475 25.08881 0.13549 16451.57176 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 21 of 55 VY4FRONT.XLS Page 8 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 2)I. PROTO-HX Output -Fouling Calculat di (ft) =Al (ftA2)Ao (ftA2)Ao/Ai do (ft)Udotdo (M)Udo (ft)Nt NI=Lambda (finsift) 
=L (ft) =UL/L (1/)=1I. PROTO-HX Output -Extrapolation Calculation di (n) =Ai (ft-2) =24 144448541 AO (ftA2) [ 7525349 Ao/Ai 329.71749526 do (ft) 0.052083333-Udodo (=81 Udo (ift) = 0.00416067 Nt = 20 NI = I2 Lambda (fins/ft) 
=L (ft) .UL)L ()0.24 UL(ft) = 0.021, UL(ft) =tfin (ft) =Utfinltfln 
(%) =hfin (f) =Uhfihlobin 
(%)Mdotc (Ibm/hr)Q (Ft^3Ihr) 
=DT (DegF)rho (IbmIftA3) 
=Urho/rho (%)Cp (Btu/lbm/DegF) a UCp/Cp (%) =Uffin (ft) =lt.Thfi (11t)=: Urho z UCp =tfin (ft) =Utfinitfin 
(%)hMe (ft)=Itligmn/hr,.u NO)Mdotc' (Ibmlhr)0* (FtA'31hr)=
DT* (Deg F)rho* (Ibm/ft43)=
Urhol/rho* 
(%)Cp* (Btu/lbftVDegF)
UCp*ICpI 4%) a q* (Btulhr) =LMTD ( DegF)Uo* =R*= (1/Uo)=RI [(hr.DegF-fttA2)IBtu]=
Etas =ho* [8tuJ(hr-OegF-ftA2)]
ho*(eII) [BtuI(hr-OegF-ft42)j Uho*lho* N% =hl* [Btui(hr-DegF-W'2)j Uhrl-hr (%) =Rw' [(hr-DegF-ftA2)IBtu]=
URw/Rw* (%)Uffin (ft) =1 Uiliin (fl) -0.006613 19492.05275 114354036I Urho' =1 .38S4 UCP* 0-019061 111304.1394 23.21284132 6.682723938 0.149639579

==0.0 31717495==
0.89059462 18.05221673
-16.0772071 15 Uho* 2.411580166
~F-774627131 Uhl' 40.174060 2 URw'- 4 4UE0 q (Btulhr) =LMTD (ODegF)Uo=R = (1/UO)RI [(hr-DoegF-ftA2)/Btuj 
=Etas =ho [BtuI(hr-DegF-ftA2)) 
=ho(off) [Btu/(hr-DegF-ftA2) 
=Uho/ho (%) =hi [Btu/(hr-DegF-ftA2)) 
=Uhilhi (%) =Rw [(hr-DegF-ftA2)/Btu] 
=URwIRw (%) =Uha =Uhi =URw=Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 22 of 55 VY4F'RONT.XL5 Page 9 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 2).1 Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAoIAo UAo 717.51253 0.05208 0.00417 8.75000 002100 0.00100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivatives: 
-5904.62 82.00 7938.80 14942.99 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 AnalytIcal Uncertainty In Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho* hi* Uhi* Rw* URw" Rf URf UR*[R" UR*0.14964 16.07721 2.41158 267.84627 40.17694 0.00025 0.00000 0.03172 0.00000 0.12750 0.01908 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R' UR" Ao UAo LMTD" Uq'/q" Uq" 111304.1394 0.14964 0.01908 717.51253 34.99475 23.21284 0.13651 15194.32143 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 23 of 55 Page 10 VY4FRONT.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 3)1. PROTO-HX Output -Fouling Calc di (ft) =Al (ftA2)Ao (ftA2)Ao/Ai do (ft) =Udo/doC()Udo (ft Nt =NI =Lambda (finsIft) 
=L (ft) =ULJL (%)UL(ft tfin (ft) =Utfin/tfin 
(%)Utfin (ft: hfin (ift) =Uh~finhflfln 
(%.) =11. PROTO-HX Output -Extrapolation Calculation di (ft) = 0.04391VC,67 Ai (ft^2) -24.14444854 Ao (ftA2) =717.512534 AoIAI =29.717495 do (ft) =0052083=UdCtdo (%) a8 1 Udo (ft) 0.004166667 1=Wina (It)=Mdotc (Ibrlnhr)=
O (FtA3Ihr) 
=OT (DegF)rho (IbmiftA3)
Urho/rho (%) =Cp (5tuIIbm/DegF)
UCp/Cp (%) =Urho'Nt=Ni =Lambda (finsift)L (ft)=ULIL ()t1mm (ft)UtflrVtfln(%
Wfin (if) -Ubtrin/lilla(%
Mdotc* (lbm/ihr)=
Q*(FtA3Ihr)
DT* (DegF)rho*(Ibm/ftA3)
Urhofrhoi 
(%)Cp* (9tuflbrnIDegF) q* (Btulhr) =LMTD, jDegF)Uo' =R'= (lJUo*)=Rf j(hr-DegF-ItA2)/Btuj Etas =ho* [BtuI(hr-OegF-ftA2)]
ho*(eff [Btu/(hr-DegF-ft'12)j Uholihol (%)=hI' [Btu/(hr-DegF-ft'12)j Uhl'tlh' (%)=Rw* I(hr-DegF-ft42)IBtuj URw*IRw* M) =UCp =Utfin (ft)=19492.0j76 527 314.9829052 239.60424096 61.3902710251 0r = .2353054205 U~* 0.03117145i 135899081241
-16.43971431 0.113S9 U h o* [ 2.406E5ED14665 ffi15J Uhl*- 1.=132 URW =q (Btulhr) -LMVTID(DegF)=
Uo=-R = 0IUo)Rf [(hr-DeqF-ft'12)/Btuj Etas 1 ho [BtuI(hr-DegF-ftA2))
ho(eff) EBtuI(hr-OegF-ftA2fl iUho/ho (%)hi [Btu/(hr-DegF.ftA2)j UhlIhi (%)=Rw [(hr-DegF-ftA12)IBtuj URwJRw (%) =Uho =Uhl =URw=Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 24 of 55 VY4FRCR14T.XLS P,,vge ! $
Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 3)I Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 717.51253 0.05208 0.00417 8.75000 0.02100 0.00100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivatives: 
-5904.62 82.00 7938.80 14942.99 2 Analhtical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty In Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho* hi* Uhi* Rw" URw" RI URf UR*R&deg; UR*0.15631 16.04394 2.40659 239.61020 35.94153 0.00025 0.00000 0.03172 0.00000 0.13321 0.02082 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R' UR* Ao UAo LMTD* Uq*/q* Uq.135899.0894 0.15631 0.02082 717.51253 34.99475 29.60480 0.14185 19277.78082 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 25 of 55 VY4FRONT.XLS Page 12 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 4)I. PROTO-HX Output -- Fouling Calcul di (ft) =Al (flA2) =Ao (ftA2) =AolAl =do (ft) =Udoldo (%) =Udo (ft)Nt =NI =Lambda (flnslft)L (f1) =ULIL (%)L II. PROTO-HX Output -Extrapolation Calculation di (ft)z 0,04391t667 Al (ftA2) = 24.14444854 Ao (ftA2) 717.5125349 Ao/Ai 2.7t1749526j do (ft) 0.0s2U83333 Udo/do (%) = (Udoa (ft) = 0.004166487 Nt = 20 MI "2 Lambda (finsift) 
= 120]L (ft) = 8.75 UL(/%) =0.24 UL(ft) o=o1.211 UL(ft) =tfin (ft) =Utfin/tfin 
(%) =hifin (ft) =Uhrain/bri 
%n Mdotc (lbm/hr) =Q (FtA3/hr) 
=DT (DegF)=rho (IbmiftA3)
Urho/rho (%)Cp (BtuiIbnVDegF)
UCp/Cp (%) =Utfin (ft) =Uhla (M) z Urho=UCp W tfln (11) =Utfln/tfin(%=
MfID (ft) =Mdote I bm/h r)DT* (OegF)rho* (lbM/ftA 3)=Urho/irho* 
(%)Cp* (8tu/IbmIfDegF)
UCp~icpf (%.)=q* (Btuthr) =LMTD0( OegF)=Uo*%R*= (1/Uo*)=Rf [(hr.OegF~ftA 2)Atuj Etas =ha' [Btu/(hr4DegF-ftA2fl ho*(eft) [BtuI(hr-O~gF~ftA 2)]UholIho* (%) =hi' [Btu/(hr43egF-ftA2)1 Uhr~lhr* (%) =Rw* [(hr-DegF-ftA 2)1ftul URwl/Rw* (%)=Utfin (ft)Lilifin (ft) -1 .061 Urho =1 128898 UCp* p ~ j 118479.0177 25.05167743 6.362774293 0.157164148

==0.0 31717496==
0.891036029 17.96751&M8
-16.00970446 is U11. 2.401455668 236.810238 1215 URw* 4943E.4)q (Btu/hr) =LUTE) ( OegF)=RlUo =Rt 1(hr-DegF~ftA2)IBtul Etas ho [BtWI(hr-OegF-ftA2)j ho(eff) [Btu/(hr-VegF-ftAI2)l Uhoiho (%)hl [BtuI(hr.DegF-ftA12)j UhI/hi fl%)=Rw [4hr-DegF-ftA2)/Btuj URw/Rw (%)=Uho =Uhl =URw =Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 26 of 55 VY4FRONT.XLS Page 13 
,Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 4)I Anal'tical lIUncertaintv in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 717.51253 0.05208 0.00417 8.75000 0.02100 0.00100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivativesi 
-5904.62 82.00 7938.80 14942.99 2 Analhtical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty In Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty In Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R" ho" Uho* hi* Uhl Rw&deg; URw* Rf URf UR*IR* UR*015716 16.00970 2.40146 236.84102 35.52615 0.00025 0.00000 0.03172 0.00000 0.13377 0.02102 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R' UR&deg; Ao UAo LMTD* Uqlq* Uq.118479.0177 0.15716 002102 717.51253 34.99475 25.95168 0.14239 16869.80234 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 27 of 55 Page 14 VY4FRONT.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate Extrapolated Heat Transfer (Btu/hr)Calculated Uncertainty (Btu/hr)(Uqiq)A2 Row1 121420.9121 16451.5718 0.001141 Row2 111304.1394 15194.3214 0.000973 Row3 135899.0894 19277.7808 0.001566 Row4 118479.0177 16869.8023 0.001199 487103.1586 34025.6474 0.069853 SRSS qtot SRSS Uqtot/qtot 
=6.99%66.5 gpm Case Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 28 of 55 Page 15 VY4FRONT.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate Extrapolated Heat Transfer (Btu/hr)Calculated Uncertainty (Btulhr)(Uq/q)A2 Row1 243763.8082 28029.4595 0.001159 Row2 207526.0668 23896.4774 0.000842 Row3 203960.0295 23572.9269 0.000820 Row4 168102.0354 19442.7635 0.000558 823351.9400 47858.0836 SRSS 0.058126 SRSS qtot Uqtot/qtot 
=5.81%(200 gpm Case)Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 29 of 55 Page 1 VY4FRONT.XLS 1AC( C. 0.L Definition of Analytical Uncertainty Analysis Terms Ao/Ai =di (in) =Ao (ft^2) =do (in) =Udo/do (0,), Udo =Nt =Nl=Lambda (fins/in) 
=L (Ft) =UL/L (%) =UL(ft) =tfin (in) =Utfin/tfin 
(%) =Utfin (in) =hfin (in) =Uhfinlhfin(%)=
Uhfin (in)--Mdotc (Ibm/hr) =Q (Ft^3Ihr)DT (DegF) =rho (lbm/ft^3) 
=Urho/rho (%) =Urho =Cp (Btu/Ibm/DegF) 
=1UCp/Cp (%) =UCp =qtest (Btu/hr) =LMTD (DegF) =Uo=R = (I/Uo)=Rf [(hr-DegF-ft^2)/BtuI 
=Etas =ho jBtu/(hr-DegF-ft^2)j 
=ho(eff) IBtu/(hr-DegF-ftA2)] 
=Uho/ho (%)Uho =hi [Btu/(hr-DegF-ft^
2)1 =Uhi/hi (%) =Uhi =Rw [(hr-DegF-ft^2)/Btuj 
=URw/Rw (%) =URw =Heat transfer area ratio Tube inside diameter Outside heat transfer area Tube outside diameter Uncertainty in tube outside diameter (as a percentage)
Uncertainty in tube outside diameter (absolute)
Number of tubes in given row Number of rows in heat exchanger Fin pitch Tube length Uncertainty in tube length (as a percentage)
Uncertainty in tube length (absolute)
Fin thickness Uncertainty in fin thickness (as a percentage)
Uncertainty in fin thickness (absolute)
Fin height Uncertainty in fin height (as a percentage)
Uncertainty in fin height (absolute)
Cooling water mass flow rate Cooling water volumetric flow rate Cooling water temperature difference (inlet to outlet)Cooling water density Uncertainty in cooling water density (as a percentage)
Uncertainty in cooling water density (absolute)
Cooling water specific heat Uncertainty in cooling water specific heat (as a percentage)
Uncertainty in cooling water specific heat (absolute)
Calculated test heat transfer for coil section Calculated log mean temperature difference Heat transfer coefficient Heat transfer resistance Fouling resistance Outside film coefficient Effective outside film coefficient Uncertainty in outside film coefficient (as a percentage)
Uncertainty in outside film coefficient (absolute)
Inside film coefficient Uncertainty in inside film coefficient (as a percentage)
Uncertainty in inside film coefficient (absolute)
Wall thermal resistance Uncertainty in wall resistance (as a percentage)
Uncertainty in wall resistance (absolute)
Proto-Power Caic: 97-198 

==Attachment:==

J Rev: A Page 30 of 55 VY4BACK.XLS Page 1 Analytical Uncertainty Analysis -- Uncertainty Inputs Parameter Udo/do ULc/Lc Utfin/tfin Uhfin/hfin Urho/rho UCp/Cp Uho/ho Uhi/hi URw/Rw Notes: Definition Uncertainty in tube outside diameter Uncertainty in coil (tube) length Uncertainty in fin thickness Uncertainty in circular fin height Uncertainty in cooling water density Uncertainty in cooling water specific heat Uncertainty in outside film coefficient Uncertainty in inside film coefficient Uncertainty in wall resistance Value (%)8.00 0.24 4.17 1.48 2.00 2.00 15.00 15.00 2.00 (1)(2)(3)(4)(5)(5)(6)(7)(5)(1)(2)(3)(4)(5)(6)(7)Measurement of 5/8" +1- 0.05" yields an uncertainty of 8.0%Measurement of 105" +/- 0.25" yields an uncertainty of 0.24%Specified as 0.012" with estimated tolerance of 0.0005" yields an uncertainty of 4.17%Measurement of 1.347" +/- 0.02" yields an uncertainty of 1.48%Uncertainty in property values is estimated as 2%Uncertainty in outside film coefficient is estimated as 15%Uncertainty in inside film coefficient is estimated as 15%Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 31 of 55 VY4BACK.XLS Page 2 PROTO-tIX Report -Model Inputs 16:07:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 07/10/98 CornEd -LaSalle Data Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Air Coil Heat Exchanger Input Parameters Fluid Quantity, Total Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Air-Side 32483 acfm'F'F'F'F Tube-Side 82 gpm 105 'F'F Fresh Water 0.002 0.002 14.315 1 0 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-i.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr.ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft-*F) 105 10 128 0.012 0.012 1.347 2 8 20 20 0.527 0.625 1.5 1.37 2 225 Proto-Power Caic: 97-198 

==Attachment:==

J Rev: A Page 32 of 55 VY4BACK.XLS Page 3 PROTO-HX Report -- Fouling Calculation Output Fouling Calculation Summary There is no fouling calculation for the rating analysis case.Uncertainty in use of design fouling in rating analysis is zero.Proto-Power Caic: 97-198 

==Attachment:==

J Rev: A Page 33 of 55 VY4BACK.XLS Page 4 PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Extrapolation Calculation Summary Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
("F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp ('F)Skin Temperature 
('F)Velocity **Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/f t)Cp (BTU/Ibm'*F)
K (BTU/hr-ft.&deg;F)
Tube-Side 110700.3 13574-82 Tube-Side hi (BTU/hr-ft.F) 130.41 100 j Factor 118.4512 124.4194 Air-Side ho (BTU/hr-ft2-'F)
Tube Wall Resistance (hr.ft'.F/BTU)
Overall Fouling (hr-ft'-&deg;F/BTU)
U Overall (BTUIhr-ft2-'F)
Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.000247 0.031717 5740.1 331168.4 331168.4 Extrapolation Calculation for Row 1(Dry)Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F) -Skin Temperature 
(&deg;F)Velocity **Reynold's Number Prandtl Number Bulk Visc (Ibmlft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/fP) " Cp (BTU/Ibm.&deg;F)
K (BTU/hr-ft.'F)
Tube-Side 110700.3 13574.82 Tube-Side hi (BTU/hr.ft'-&deg;F) 130.41 121.0124 j Factor 129.4309 125.012 Air-Side ho (BTU/hr-ft2-'F) 0.020272 Tube Wall Resistance (hr.ft3-*F/BTU) 0.020272 Overall Fouling (hr.ft=.*F/BTU) 129.9204 123.0119 127.6897 126.4444 U Overall (BTU/hr-ft2.&deg;F) 5764.992 0.504613 Effective Area (ftW)1603.412 3757.927 LMTD 0.726684 3.524269 Total Heat Transferred (BTU/hr)0.048111 1.309111 1.268623 Surface Effectiveness (Eta)0.06353 61.66439 Sensible Heat Transferred (BTU/hr)0.240245 0.998878 Latent Heat Transferred (BTU/hr)0.015906 0.371029 Heat to Condensate (BTU/hr)168.6431 0.011561 19.8098 0.000247 0.031717 5.639065 717.5125 6.701516 27115 0.881565 27115 Extrapolation Calculation for Row 2(Dry)Air-Side Mass Flow (Ibmlhr)Inlet Temperature 
(=F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp ('F)Skin Temperature 
('F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ft.hr)
Density (Ibm/fl')Cp (BTU/Ibm.'F)
K (BTU/hr.ft.'F) 110700.3 129.4309 128.4233 0.020272 0.020272 128.9271 126.6311 5764.992 1605.495 0.726762 0.048049 0.063639 0.240245 0.015883 Tube-Side 13574.82 Tube-Side hi (BTU/hr-ft'-"F) 11 119.7104 j Factor 0.123.8268 Air-Side ho (BTU/hr.ft3-&deg;F) 1'Tube Wall Resistance (hr-ft2.=F/BTU) 0.Overall Fouling (hr-ft2.=F/BTU) 0.121.7676 125.3501 U Overall (BTU/hr.ft2-OF) 5.0.504452 Effective Area (ft2) 7 3714.764 LMTD 6.3.56911 Total Heat Transferred (BTU/hr) 2 1.324322 1.281303 Surface Effectiveness (Eta) 0.61.68406 Sensible Heat Transferred (BTU/hr) 2 0.998827 Latent Heat Transferred (BTU/hr)0.370619 Heat to Condensate (BTU/hr)Proto-Power Calc: 97-198 66.2351 011556 9.79955 000247 031717 597947 17.5125 947216 7904.16 881617 7904.16 

==Attachment:==

J Rev: A Page 34 of 55 VY4BACK.XLS Page 5 PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Extrapolation Calculation for Row 3(Dry)Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(=F)Outlet Temperature 
(*F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity **Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ft hr)Density (Ibm/ft)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ftOF)
Tube-Side 110700.3 13574.82 Tube-Side hi (BTU/hr-ftl-&deg;F) 128.4233 115.6999 j Factor 127.1227 121.0124 Air-Side ho (BTU/hr.ft'&deg;F) 0.020272 Tube Wall Resistance (hr-ftl.&deg;F/BTU) 0.020272 Overall Fouling (hr-ft2.*F/BTU) 127.773 118.3564 124.8119 123.1606 U Overall (BTU/hr-ft2.OF) 5764.992 0.50402 Effective Area (ft')1607.926 3597.299 LMTD 0.72685 3.696975 Total Heat Transferred (BTU/hr)0.047976 1.367566 1.307313 Surface Effectiveness (Eta)0.06378 61.73696 Sensible Heat Transferred (BTU/hr)0.240245 0.998816 Latent Heat Transferred (BTU/hr)0.015857 0.369474 Heat to Condensate (BTU/hr)159.7789 0.01155 19.78764 0.000247 0.031717 5.486089 717.5125 9.149558 36015.75 0.881677 36015.75 Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (=F)Skin Temperature 
(&deg;F)Velocity **Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ffthr)
Density (Ibrn/f 3)Cp (BTUIbm 0'F)K (BTU/hr-ftf'F) 110700.3 127.1227 125.8348 0.020272 0.020272 126.4788 123.5458 5764.992 1610.664 0.726948 0.047894 0.063921 0.240245 0.015828 Extrapolation Calculation for Row 4(Dry)Tube-Side 13574.82 Tube-Side hi (BTU/hr-ft"-F) 114.4491 j Factor 119.7104 Air-Side ho (BTU/hr.ft 2-&deg;F)Tube Wall Resistance (hr-ftz.*F/BTU)
Overall Fouling (hr.ft 2 ,.F/BTU)117.0793 121.9112 U Overall (BTU/hr-ft 2.*F)0,503862 Effective Area (Wt)3553.652 LMTD 3.746789 Total Heat Transferred (BTU/hr)1.384363 1.322552 Surface Effectiveness (Eta)61.75638 Sensible Heat Transferred (BTU/hr)0.9988 Latent Heat Transferred (BTU/hr)0.369037 Heat to Condensate (BTU/hr)157.263 0.011543 19.77428 0.000247 0.031717 5.440658 717.5125 9.136426 35666.24 0.881745 35666.24 Extrapolation Calculation for Row 5(Dry)Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(=F)Outlet Temperature 
(=F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (=F)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (Ibm/ft hr)Density (Ibm/ft')Cp (BTU/Ibm&deg;F)
K (BTU/hr-ft&deg;F)
Tube-Side 110700.3 13574.82 Tube-Side hi (BTU/hr ft 2.*F)125.8348 108.7745 j Factor 124.1394 115.6999 Air-Side ho (BTU/hr.ftl.&deg;F) 0.020272 Tube Wall Resistance (hr.ft2,&deg;F/BTU) 0.020272 Overall Fouling (hr-ft 2.=F/BTU)124.9871 112.2375 121.1303 118.9822 U Overall (BTU/hr-ftl.&deg;F) 5764.992 0.503278 Effective Area (ftW)1613.838 3389.831 LMTD 0.727058 3.945992 Total Heat Transferred (BTU/hr)0.0478 1.451265 1.359459 Surface Effectiveness (Eta)0.064106 61.828 Sensible Heat Transferred (BTU/hr)0.240245 0.9988 Latent Heat Transferred (BTU/hr)0.015795 0.367343 Heat to Condensate (BTU/hr)Proto-Power Calc: 97-198 148.0407 0.011535 19.75889 0.000247 0.031717 5.270737 717.5125 12.41481 46950.58 0.881823 46950.58 

==Attachment:==

J Rev: A Page 35 of 55 Page 6 VY4BACK.XLS PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Extrapolation Calculation for Row 6(Dry)Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (=F)Skin Temperature 
("F)Velocity **Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/ft')Cp (BTU/Ibm.F)
K (BTU/hr-ft.&deg;F) 110700.3 124.1394 122.5339 0.020272 0.020272 123.3372 119.6846 5764.992 1617.371 0.727177 0.047696 0.064283 0.240245 0.015758 Tube-Side 13574.82 Tube-Side hi (BTU/hr-ft2.'F) 107.891 j Factor 114.4491 Air-Side ho (BTU/hr.ftl.=F)
Tube Wall Resistance (hr-ft'.&deg;F/BTU)
Overall Fouling (hr.ft 2.=F/BTU)111.1708 117.6518 U Overall (BTU/hr-ft2."F) 0.503153 Effective Area (ft2)3354.1 LMTD 3.9922 Total Heat Transferred (BTU/hr)1.466726 1.376791 Surface Effectiveness (Eta)61.84335 Sensible Heat Transferred (BTU/hr)0.998835 Latent Heat Transferred (BTU/hr)0.366962 Heat to Condensate (BTU/hr)145.8629 0.011526 19.74187 0.000247 0.031717 5.228233 717.5125 11.85177 44459.82 0.881909 44459.82 Air-Side Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature 
(*F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(=F)Velocity **" Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (Ibm/ft.hr)
Density (Ibm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F) 110700.3 122.5339 120.3887 0.020272 0.020272 121.4612 116.5875 5764.992 1621.416 0.727309 0.047577 0.064521 0.240245 0.015716 Extrapolation Calculation for Row 7(Dry)Tube-Side 13574.82 Tube-Side hi (BTU/hr.ft=-&deg;F) 100.0127 j Factor 108.7745 Air-Side ho (BTU/hr-ftl'.F)
Tube Wall Resistance (hr-ft 2."F/BTU)Overall Fouling (hr.ftt.*F/BTU) 104.3939 113.8776 U Overall (BTU/hr.ft 2.&deg;F)0.502391 Effective Area (ftW)3130.16 LMTD 4.307462 Total Heat Transferred (BTU/hr)1.5711659 1.428014 Surface Effectiveness (Eta)61.93712 Sensible Heat Transferred (BTU/hr)0.998845 Latent Heat Transferred (BTU/hr)0.364467 Heat to Condensate (BTU/hr)132.8281 0.011517 19.72252 0.000247 0.031717 4.967321 717.5125 16.66772 59405.67 0.882007 59405.67 Extrapolation Calculation for Row 8(Dry)Air-Side Mass Flow (Ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (&deg;F)Skin Temperature 
(&deg;F)Velocity *Reynold's Number Prandtl Number Bulk Visc (Ibmlft-hr)
Skin Visc (Ibm/ft-hr)
Density (Ibm/ft 3)110700.3 120.3887 118.4512 0.020272 0.020272 Tube-Side 13574.82 Tube-Side hi (BTU/hr.ff 2-OF)99.97818 j Factor 107.891 Air-Side ho (BTU l/hr ft 0."F)Tube Wall Resistance (hr.ft 2.=F/BTU)Overall Fouling (hr-ft2.&deg;F/BTU) 119.4199 103.9353 115.0151 112.5682 U Overall (BTU/hr-ft2.&deg;F) 5764.992 0.502342 Effective Area (ftW)1625.852 3115.201 LMTD 0.727448 4.330242 Total Heat Transferred (BTU/hr)0.047447 1.579206 1.446526 Surface Effectiveness (Eta)0.064737 61.94322 Sensible Heat Transferred (BTU/hr)131.7467 0.011506 19.70147 0.000247 0.031717 4.943438 717.5125 15.12588 53651.18 0.882114 53651.18 Proto-Power Caic: 97-198 

==Attachment:==

J Rev: A Page 36 of 55 VY4BACK.XLS Page 7 PROTO-HIX Report -- Extrapolation Calculation Output for Limiting Flow Case Cp (BTU/Ibmn F)K (BTU/hrft&deg;F) 0.240245 0.998908 Latent Heat Transferred (BTU/hr)0.01567 0.364294 Heat to Condensate (BTU/hr)Air Mass Velocity (Lbm/hr-ft2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 37 of 55 Page 8 VY4BACK.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 1)I. PROTO-HX Output -- Fouling Calculation di (ft) =Al (ft^2)Ao (11-2) =Ao/Ai do (ft)Udo/do (%)Udo (ft)Nt =NI=Lambda (fins/ft)L (ft) =UL/L (%) =It. PROTO-HX Output -Extrapolation Calculation di (ft) = 01 4391667 Al (ftA2) 24.14444854 Ao (1 0A 2) 717.5125349 Ao/A= 29.71749526 do (ft) 0.052083333 Udo/do (%) 8 Udo ift) 0.0(4166667 Nt :2 NI= !2 ,220 Lambda (fins/ift) 120 L (ft) = 8.75 ULIL(%) 0.24 UL(tt) 0.021 ULMf) =tfIn ("f) =Utfinltfin 
(%)hfin (11) =Uhfin/hfln 
(%)Mdotc (Ibm/hr)Q (FtA3/hr)DT (OegF)rho (lbm/ftA3) 
=Urho/rho (%) =Cp (Btu/ibm/DegF)
UCp/Cp (%) =Witin (It)Ulifla (ft)=Urho UCp =Mfin (Rf) =Uftf/irif(%)
hfin (if)uhflaui fn Mdotc* (ibmthr)=Q* (FtA 3/hr)Dr (DegF)rho* (fbm/iftA31 
=Urholfrho*
M% =Cp* (BWtuflbV~egF)=
UCp*/Cpl (%)q* (8W/lhf)=LMTD' (DegF)Uo, R* -(1/Uoi =RI [(hr-DegF-ftA2)1Btuj Etas =ho, [Btu/(hr-DeqF-ftA2)J=
ho*(eMf (Btu/(hr-DegF-Wt2)J Uho~fho* (%)=hl IBtu1(hr-DegFiftA2)1 1/hr/hi* (%) =Rw* [(hr-DegF-ttA2)/Btuj URw*/Rw* (%) =.000181 1357482245 3.9968762 Urho* =4 123327837 0.9878349 UCp, 0.0197758 27115.00023
: 6. 7015 1585 5.63906478 0.17733437

==0.0 31717495==
0.381584535 19.80979&83 17.4638157 15 Uho' 2 615423556 168.643109 URw*= -9,3 -o1 q (Btu/hr) =LMTD (Deg F)=UO =R = (/Uo)=RI [(hr-DegF-ftA'2)IBtuj Etas =ho [BtuJI(hr-DegF-ftA2)1 ho(emf IBtu/(hr-DegF-ftA12)J=
1.ho/ho (%)=hi (13tu/(hr-1DegF-ift4211 Uhifhil (%) =Rw [(hr-DogF-ftA 2)/Btu]URw/Rw (%) =Uho =Uhi:=URw =Proto-Power Calc: 97-198 

==Attachment:==

I Rev: A Page 38 of 55 VY4RACK X1.5 Page g Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 1)I Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 717.51253 0.05208 0.00417 8.75000 0.02100 000100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivatives: 
-5904.62 82.00 7938.80 14942.99 2 Analytical Uncertainty in Test Heat Transfer Rate 3 AnalytIcal Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R&deg; ho&deg; Uho* hi* Uhi* Rw URw Rf URf UR*IR* UR*0.17733 17.46362 2.61954 168.64311 25.29647 0.00025 0.00000 0.03172 00.64000 0.15673 0.02779 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R* UR* Ao UAo LMTD" Uq.lq" Uq.27115.0002 0.17733 0.02779 717.51253 34.99475 6.70152 0.16414 4450.63334 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 39 of 55 VY4BACK.XLS Page 10 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 2)I. PROTO-HX Output -- Fouling Calculation di (ft)=Ai (ftA2) =Ao (ftA2)AoIAi do (ft)Udoldo (%) =Udo (ft) m Nt =NI=Lambda (fins/ift 
=L (ft)ULIL (%)It. PROTO-HX Output.- Extrapolation Calculation di (ft) 04'.13ef7 At (ftA2) =24 4444854 Ao (ft^2) 717.5125349 AoIAi 2q 71749526 do (ft) =(052083333 Udo/do (%) a Udo (ft) 0.00416G8G7 Nt =2 NI = 2 Lambda (fins/ft) 
= ij oj L (ft) = 8.75 UL]L 0%o.)24 UL(ft)tfln (ft) =Utfin/tfin 
(%) =hfin (ft) =11hrin/hfin ( )=Mdotc (Ibmlhr) =Q (Ft^3/hr)DT (DegF) =rho (Ibm/ftA3) 
=Urho/rho (%) =Cp (BtufibmlDegF)
UCp/Cp (%) =Utfln (if)I tlfin (It)Urho UCp ttin (ft) =Utflnltfln(%
Wiln (11)Uflin/h rig %Mdotc* (Ibmlhr)Q' (FtA 3/hr)OT* (DegF)=rho' (lbm/ftA3) 
=UrholrhW (0h)=Cp*(BtulbnIDegF)=
UCP*ICp* (%) =q* (Stuffhr)=
LMTD* (DegF)Uo* =R s(W/oi =RI [(hr-OegF~ft A2)IBtuJ Etas =ho* [BtuI(hr-DegF-ftA2)J ho'(eff)l jBtuI(hr-DegF-ftA2)J Uho~fho*(%) 
=h1* [Btu/(hr-OegF-ftA2)]
Uhl-1hi- (%) =Rw* [(hr-DagF-ftA'2)IBtu1 URw*/Rwl (%) =Utfin (ft)= 0.00017 13574. 82245 t~~2~2 Urho* = 1.23368248 L~.2I UCp, 0.097536 27904.16465 6.947215729 5.597946,54.
0.1786369M3

==0.0 3t7l7495==
0.68816165D.3 19.79964517.
17.45563M61, Uho'! 2 6183Q0999 Uhl* -= 495M 0.000247317 2 URw* 4 -94534E08 q (Btulhr)=LMTD (OegF)U0 =R = (/Uo)=Rf [(hr-DegF-ftA2)IBtu]
Etas =ho [Btu/(hr.OegF-ftA2)J 
=ho~eff) [BtuI(hr-DegF-ftA2)1 Uho/ho (%) =hi (Btu/(hr-DegF-ft^2)J Uhi/hi (%) =Rw [(hr-DegF-ft112)IBtuJ=
U RwIRw (%) =Uho=Uhl =URw =Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 40 of 55 Pdc.1C I1 VY4L3A&#xfd;K XI.:S Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 2)I Analtical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAoIAo UAo 717.51253 0.05208 0.00417 8.75000 0.02100 0.00100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivativesi 
-5904.62 82.00 7938.80 14942.99 2 AnalytIcal Uncertainty In Test Heat Transfer Rate 3 Analytical Uncertainty In Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R* ho* Uho" hi Uhl* Rwy URw" Rf URf UR*R" UR*0.17864 17.45561 2.61834 166.23510 24.93526 0.00025 0.00000 0.03172 0.00000 0.15763 0.02816 6 Analytical Uncertainty in Extrapolated Heat Transfer q* R' UR" Ao UAo LMTD* Uq*lq* Uq*27904.1646 0.17864 0.02816 717.51253 34.99475 694722 0.16500 4604.25253 Proto-Power Caic: 97-198 

==Attachment:==

J Rev: A Page 41 of 55 VY4BACK.XLS Page 12 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 3)I. PROTO-HX Output -- Fouling Calcul;di (ft) =A! (ft2)Ao (ftA2) =Ao/Ai do (ft)Udoldo (%)Udo (ft)Nt =NI =Lambda (finslft) 
=L (ft)ULIL (%) =II. PROTO-HX Output -Extrapolation Calculation di (ft) = 0.043-,16667 Ai (ft^2) = 24.144448654 Ao (ftA2) = 717.5125349 Ao/Ai N.71749526 do (ft) 0.052083333 Udoldo (%) =Udo (ft) 0.004166667 Nt 20 NI 2 Lambda (finslft) 120 L (ft) a.75 UL/L (%) 0.241 UL(ft) =tfln (ft) =Utfinltftn 
(%) =hfill (ft) =IUhfln/hfln 
(%) =Mdotc (lbmnhr) =Q (FtA3/hr)OT (DegF)rho (lbMnftA3) 
=Urho/rho (%)Cp (Btu/IbmfDegF) 
=UCpICp (%) =Utfin (ft) =fin (It) =Urho UCp tfln (ft)-=Uhfl'Whrin 
(%I=Mdotc* (lbml~hr)Q' IFt'31hr)=
DTI (DagF)rho* (lbmIftA13)
Urholtrho* 
(%)Cp' (BtuJlbm/DegF)z UCp*ICP* (%) =q* (Btulhr)=LMTD' ( DegF)=Uo*R*=(lIUo*)=
Rf t(hr-DegF-ftA2)IBtuj=
Etas =ho* (BtuI(hr-DegF~ftA 2)I ho*(eff) [BtuI(hr4OegF~ftA 211 Uho'/ho' (%) =hl* [BtuI(hr-DegF-ftA2)1 Uhj*/hi* (%) =Rw* [(hr-DegF~ftA2)/Btu]
URw/lRw' %) =135748224.
219.881572 5.31449781 Urho w 1.3728 36015.74715 9.149558l111 5.45608659 0.182279229

==0.0 31717495==
0.881678887 19.78763579 17.44630111 is Uho=, 2.616945167 UhIIs 0.000n247317 URw -1 fE0 q (Btulhr)LMVTO ( DegF)=Uo =R = (1/Uo)=RI [(hr-DegFiftA21/Btul 
=Etas =ho [Btu/(hr-DegF-ftA2)j 
=ho(eff) [BtuIQhr43egF
_ftA 2)I Uho/ho (%)=hi [BtuI(hr-DLeaF~ftA 2)]UhlJhi (%) =Rw ((hr-DegF-ft^2)IBtul URwJRw (%) =Uho: Uhl =URw =Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 42 of 55 Page 13'10 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 3)I Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAoIAo UAo 717.51253 0.05208 0.00417 8.75000 0.02100 0.00100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivatives: 
-5904.62 82.00 7938.80 14942.99 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' ho' Uho*0.18228 17.44630 2.61695 hi* Uhl* Rw* URw* Rf URf UR*/R* UR*159.77891 23.96684 0.00025 0.00000 0.03172 0.00000 0.16016 0.02919 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R' UR* Ao UAo LMTD" Uq*/q* Uq" 36015.7472 0.18228 0.02919 717.51253 34.99475 9.14956 0.16742 6029.74516 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 43 of 55 VY4BACK XLS Page 14 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 4)I. PROTO-HX Output -Fouling Calcul dt (if) =Al (ft-2) =Ao (ifA2)Ao/Al =do (ft) =Udo/do (%)Nt =Ni=Lambda (fins/if) 
=L (if)ULJL (%)tfin (ft)Utfinltfin 
(%) =hJinnfrt) 
=Uitrin/hfi 
(%) =Mdotc (Ibmlhr) =O (FtA3/hr) 
=DT (DegF) =rho (lbm/ftiA3) 
=Urho/rho (%) =Cp (BtuiqbmIDegF) 
=UCplCp (%) =Udo (if) =UL(ft) =Utfin (ft) =(:bfln (it) =Urho=UCp =Il. PROTO-HX Output -Extrapolation Calculation di (ft) 7,.jag r Al (ft^2) 24.14444aS4 AO (ftA2) = 717.512.534 Ao!Ai 29,.717052 do (ft) = 0.05[p 3333J Udo/do (%)= 8 Udo (ft) = 0.004166667 Nt =NI =Lambda (finsIft) 
=L (if) =UUL (%) =UL(ft)tfin (ift) =Utfrrntffin(%
t'fln (if) =Mdotc* (lbni/hr)0* (Ft3/hr)Dr (DegF)rho* (lbm/ tA 3) =Urholrho* 
(%) m Cp* (Btu/lbm/vegF)
UCP*ICp*(%)=
q-(Btulhr)=
LMTD* ( DegF)Uo' =R* 2r(1/Uo*)=
Rf [(hr-OegF-ft42)/Btuj Etas =ho' (Btu/(hr-DegF-ftA2fl ho'(eff) [Btu/(hr-DegF-ftA 2)1 Uho*/ho* (%) =hi* [Btu/(hr-DegF-ftA2)J Uhl-/hl (%) =Rw* [(hr-OogF-ftA-2)IBtu]
URwI/Rw* (%) =4.17~21g.6124741 Urho* = .3178 UC p* .009799 356W3.2354 9.13642847 5.440657858 0.183801302

==0.0 31717495==
0.881744607 19.77428085 17.4&1,86549 15 Uho* 2615379823 157.2629764 Uhi* 2.59465 0.00247117 URw* 4 L7T3E~t q (Btulhr) =LMTD ( DegF)Uo =R = (IIUo)RI j(hr-0egF-ift'2)IBtuj 
=Etas=ho [BtuI(hr.DegF~ftA 2)1 =ho(eif) [Btul(hr-DegFiftA2)J Uholho (%) =hi [BtuI(hr-DegF-ifAf2)j Uhilhl (%)=Rw [(hr-OegF-ftA2)IBtuj URw/Rw (%) -Uho =Uhl =URw =Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 44 of 55 VYWIACK.XLS Page 15 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 4)1 Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tin Utfin hfin Uhfin UAoIAo UAo 717.51253 0.05208 0.00417 8.75000 0.02100 0.00100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivatives: 
-5904.62 8200 7938.80 14942.99 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho* hi* Uhl* Rw* URw" Rf UR URI*R UR*0.18380 17.43587 2.61538 157.26298 23.58945 0.00025 0.00000 0.03172 0.00000 0.16116 0.02962 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R' UR* Ao UAo LMTD* Uql/q. Uq&deg;35666.2354 0.18380 0.02962 717.51253 34.99475 9.13643 0.16838 6005.49693 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 45 of 55 VY4BACK.XLS Page 16 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 5)I. PROTO-HX Output -Fouling Calculation di (ft) =Ai (Wtt2)Ao (ftA2)=Ao/Ai=do (ft) =Udo/do (%)Udo (ft)Nt NI=Lambda (flnslft) 
=L (ft)=ULJL (%)II. PROTO-4X Output -Extrapolation Calculation dl (ft) = [ 4637 Al (ft"2) 24 14444854 Ao (ftA2) [ 71.5125349 Ao/Ai =29.71749526 do (ft) 0.052083333 Udoldo (%) 8 Udo(f)= 0.f041t)667 Nt = I 20 NJ= Lambda (finsift) 120 L (ft) =875 ULUL (%024 UL(ft) =0.021 UL(ft)=trin (1f) -Utfinftfln 
(%) =hfn (af) =Uhfinbltln 
(%I =Mdotc (lbm/hr)0 (Ft^3Ihr) 
=DT (DegF) =rho (lbmtft43) 
=Urho/rho (%) =Cp (BtuIbm/Degl'F)
UCpICp (%) =Utfln (ft), uhn (f)Urho: UCp, ttln (ft) =Utfinitfin (0/)lrif (ft) -Mdotc* (lbnifhr)=
Q* (Ft'131hr)
DT* (DegF)rho' (IbmnIftA3)=
Urho~'Irho' 
(%e)Cp* (lBtullbvIDegF)=
UCp*ICP* (%) =q* (Btuthr)=LMTD* (DegF)Uo*=* (lIUo*)Rf ((hr-DagF-ft 4 2)IBtuj =Etas=ho* [BtuI(hr.DegF-ttA 211 ho*(eff) [BtuI(hr-OegF-ft'I2)]
Uho*/ho* (%) =hi* [BtuI(h~r-DagF-ft^2)j Uhirlhr (%)=Rw* f(hr-OegF-ft^2)fBtuj URwI/Rw* (%) =4 17I Utfin (ft) = .0 U,,n. S 13574.82245I 21.5578482 12.41481174 5.270737233 0.189726779

==0.0 31717495==
o 8818Z2207 t 9.75889o t 17.4238372 15 Uho = 2.613575582 0.1489472677 Uho* 263=t582 URw* ___ &#xfd;a~r q (Btulhr)LMTD ( DegF)=Uo R = (/Uo)=RI [(hr-.OegF-ft112)/Btuj 
=Etas ho [BtuI(hr-DegF-ftA2)fl ho(eft) (Stu/(hr-0eqF-ft12)j Uho/io(%M 
=hi [BtuI(hr-OegF-ftA2)]=
MUMlh (%)Rw j~hr4)egF-ft112)I~tu]
URwIRw (%)=Uho =Uhi =URw =Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 46 of 55 VY4BA(CK:XLS PagA 17 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 5)I Analytical Uncertaint' in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAolAo UAo 717.51253 0.05208 0.00417 8.75000 0.02100 0.00100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivatives: 
-5904.62 82.00 7938.80 14942.99 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho* hi* Uhi* Rw* URw* Rf URf UR*/R* UR*0.18973 17.42384 2.61358 148.04072 22.20611 0.00025 0.00000 0.03172 0.00000 0.16507 0.03132 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R' UR&deg; Ao UAo LMTO* Uq'lq* Uq*46950.5838 0.18973 0.03132 717.51253 34.99475 12.41481 0.17212 8081.13244 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 47 of 55 VY4BACK.XLS Page 18 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 6)I. PROTO-HX Output -- Fouling Calculation di (ft) =Ai (ftA2)Ao (ftA2)Ao/Ai do (ft) =Udo/do (%) =Udo (ft) =Nt =NI =Lambda (finslft) 
=L (ft) =ULIL (%) =It. PROTO-HX Output -Extrapolation Calculation di (ft) = V43167J Al (ftA2) = 4.14444854 Ao (ftA2) 7 5 125349 AolAt 29 71749526[do (ft) 0052083333 Udo/do (%) 8 Udo (ft) 0.004168667 Nt= 1 20 Lambda (finslftl 
=M L (ft) = 8.751 UL/L %) = 0.24 UL(ft) = 0.021 UL(ft)tfln (ft) =Utfinltfin M%)hrin (11) =I[llfinluibfld Mdatc (lbm/hr)Q (Ft'31hr)DT (DegF)rho (lbml/ft&3)=
IUrho/rho 
(%)Cp (BtuAJbmIDeqF)w UCp/Cp (%) =Utfin ift)uIIrin (ft)Urho UCp*tfin (ft) =Utfinitfin 
(%)hfln (ft)=UIlln/brin 
%-Mdotc* (Ibm/dhr)Q*(Ft431hr)=
DT* (Deg F)=rho* (lbMftA 3)=Urho~!rho* 
(%)Cp (Btullbm/DegF)a UCp*ICp* %) =q' (Btuihr) =LMTD*( DogF)U0, =R'-(lIUo*)=
Rf I7(hr43egF-ftAZ2)IBtuj Etas -ho* [Btu/(hr-DegF-ftA2)j ho*(eff) [BtuI(hr-OegF~ftA 2)1 Uholho' (%) =hi* [BtuI(hr-DegF-ftA12)j Uhilfhi- (%) -Rw* [(hr-DogF~ftA 2)IBtuJ URwiRw* (0/) =0.001 1.i481 6.517613 Urho* 1.3=63 0.99835078 UCp* 0.0197602 44459.81549 11.85177138 5.212823257 0.191260227

==0.0 31717495==
0.88 1 0901 19. 74l187056 17 4 1053353 is Uho, 2.61158003 F 4586287331 Uhl*=0.,-00024731&#xfd;7 URW* 4.94634E-6 q (Btulhr) =LMTD ( DegF)Ug=R = (I/Uo)Rf t(hr-DegF-fta2)IBtu]
Etas =ho (BtuI(hr-DegF-ft^2)j=
ho(off) [Btu/(hr-OegF-ftAI2)j Uho/ho M%=hi [lBtuI4hr-DegF-ftt2)j Uhi/hl (%) =Rw [(hr-OegF-ftA2)/BtuJ URwIRw (%) =Uho =Uhi =URw Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 48 of 55 VY4 BAC'K XLS Pjqe 19 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 6)1 Analytical Uncertainto in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAolAo UAo 717.51253 0.05208 0.00417 8.75000 0.02100 0.00100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivatives: 
-5904,62 82.00 7938.80 14942.99 2 Analytical Uncertainty in Test Heat Transfer Rate 3 AnalytIcal Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty In Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R" ho* Uho* hi* Uhi" Rw* URw" Rf URf UR*/R* UR&deg;0.19127 17.41053 2.61158 145.86287 21.87943 0.00025 0.00000 0.03172 0.00000 0.16600 0.03175 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R'. UR* Ao UAo LMTDO Uqlq. Uq*44459.8155 0.19127 0.03175 717.51253 34.99475 11.85177 0.17302 7692.48427 Proto-Power Caic: 97-198 

==Attachment:==

J Rev: A Page 49 of 55 VY4BACK.XLS Page 20 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 7)I. PROTO-HX Output-- Fouling Calculation di (ft)=Ai (ftA2) -Ao (ftA2) =Ao/Ai =do (ft)Udoldo (%)Udo (ft) =Nt =NI =Lambda (fins/ift)
L (ft)ULIL (%)II. PROTO-HX Output -- Extrapolation Calculation di (ft) = 0.391&i07 Ai (ftA2) = 24.1444485 Ao (ftA2) = 717.5125349 AoIAi 29.717491,2C do (ft) ().415208333 Udo/do (%) = a Udo (ft)=
Nt = 20 NI = 2 Lambda (fins/ift) 
=2 L (ft) =8,75 ULIL (%)=0.2 ULIft)= 0.o21I UL(ft) =tfin (ft) =Utfinitfin 
(%) =bfini (ft) =Uhrin/hfln 
(%) =Mdotc (Ibm/hr)Q (Ft^31hr) 
=OT (DegF)rho (Ibm/ft^3) 
=Urho/rho (%) =Cp (Btu/lbm/DegF)
UCpICp (%) =Utfin (ft)(I hfin (If)Urho =UCp =tfin (ft) =Utfirdtfin 
(%) =hfln (ft) -IJbnithla 
(%h 3/4Mdotc* (Ibm/hi) =Q* (Ft^3Ihr) 
=DTI (DegF) =rho* (Ibm/ftA3) 
=Urho*lrho* 
(%) =Cp&deg; (Btu/lbm/OegF) 
=UCp*/Cp* (%) =q* (Btulhr) =LMTD' ( DegF) =Uo* =R* = (I/Uo)=Rf [(hr-DegF-ftA2)/Btu]
Etas =ho&deg; fBtu/(hr-DegF-ftA2)J 
=ho*(eff) [Btu/(hr-DegF-ftA2)j Uho*lho' (%) =hl' [BtuI(hr-DegF-ftA2)]
Uhi-/hr- (%) =Rw* [(hr.DegF-ft^2)!BtuI 
=URw'/Rw* (%) =14417 1.1hrin (ftv=El 0.0016613 L21.710457 Urho* w t .23742317J 1 6.66771848 4.96732138 0.201316744 0.03MMS40 0.882D072 19.72252126
-17.39540576 15 Uhio* 2."09310664 F 3 210061 Uhi*=E ]0.000247317 URw 4903E0 q (Btuihr) =LMTD ( DegF)Uo=R = (0IUo)Rf [(hr-DegF-ftA2)/Btu) 
=Etas =ho [Btu/(hr-DegF-ftA2)j ho(eff) [Btu/(hr-OegF-ftA2)J 
=Uho/ho (%) =hi [Btu/(hr-OegF-ftA2)1 
=UhiNhi (%) =Rw [(hr-DegF-ftA2)/Btu] 
=URwIRw (%) =Uho =Uhi =URw.Proto-Power Calc: 97-198 

==Attachment:==

J VY48ACK.YLS Rev: A Page 50 of 55 Page 21I 6Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 7)I Analytical Uncertaintv in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 717.51253 0.05208 0.00417 8.75000 0.02100 0.00100 0.00004 0.11225 0.00166 0,04877 34.99475 Derivatives: 
-5904.62 82.00 7938.80 14942.99 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty In Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R' ho* Uho*0.20132 17.39541 2.60931 hi* Uhl* Rw* URw* Rf URf UR*IR* UR*132.82810 19.92422 0.00025 0.00000 0.03172 0.00000 0,17212 0.03465 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R' UR* Ao UAo LMTD* Uq'iq" Uq*59405.6714 0.20132 0.03465 717.51253 34.99475 1666772 0.17889 10627.19473 Proto-Power Calc: 97-198 

==Attachment:==

J VY4BACK.xLS Rev: A Page 51 of 55 Page 22 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 8)I. PROTO-HX Output -Fouling Calcul di (ft) =Ai (ftA2)Ao (ftA2)AOiAi =do (if)Udoido (%)Udo (ft)Nt NI=Lambda (fins/ift) 
=L (it) =ULIL (%)II. PROTO-HX Output -Extrapolation Calculation di (ft) = F 0.04391W,6?
Ai (ftA2) 24.14444554 Ao (flA2) 717.5125349 AojAi 2q 71749526 do (ft) = 0 052083333 Udoldo(%)Udo (ft) =1 0.004166067 Nt = Zn NI= 2 Lambda (finsiif) 
-120 L (if) = 9.7z ULL(%)= 0.24 UL(ft) 0.021 UL(f =ttin (ft) =Utfln/tfin 
(%) =lifla (rt) =Uhlfin/hrin 
(%) =Mdotc (Ibm/hr) =Q (Ft731hr)DT 4DegF)=rho (Ibrmlft A3)Urho/rho (%) =Cp (Btu/ibmnDegF) a UCpICp (%) =Utfin (ift =Uhfin (ft)=Urho=UCp =tfin (ft) =Utfinitfin 
(%) =hfin (It)I 1hfln/hfin 
*%)Mdotc* (Ibm/hr) =Q0 (FtA3/hr) 
=DT* (DegF) =rho* (IbmriftA3) 
=Urhol/rho* 
(%) =Cp* (BtuIlbm/DegF)=
UCP*/Cp" (%) =q* (Btulhr) =LMTD ( DegF)Uo+ =R, = (lIUo*) =Rf [(hr.DogF-ftA2)IBtuJ Etas=ho* [BtuW(hr-DegF-f2)] 
=ho*(eff) [Btuf(hr-DegF-ffA2)]
UhoIho* (V) =hi* [Btu/(hr-DogF-ft"2)J 
=Uhl*ihi (%) =Rw" [(hr.DegF-ftA2)/BtuJ URwlIRw* (%) =.0001 Utfin (ft) 0.oo00417 0.&deg;"12 Llifn (It) o.0016613 13574.82245 Urhol 1.238864454 0.998908141 UCgr= 0 .01j9781e3 5,3651.18089 15.12588275 4 943437676 0.20228838

==0.0 31717495==
0.882114054 19.70147117 17.3789446 15 Uho* 2.606841689 Uhl=L23282
: 77. -00247;317 I ffiC2I URw*= I4.94E34 E-S6 q (Btulbr) =LMTD (DegF)U0 c R = 1/UM)Rf [(hr-DegF-ftA2)J8tuJ 
=Etas =ho [BtuI(hr-DegF-ftA2)] 
=ho(eff) [Btu/(hr-DegF.ftA2)] 
=Uho/ho (%) =hi [BtuI(hr-DegF-ft42)J 
=UhI/hN (%) =Rw [(hr-DegF-ftA2)/BtuJ 
=URw/Rw (%) =Uho =Uhi =URw=Proto-Power Cale: 97-198 

==Attachment:==

J Rev: A Page 52 of 55 VN'4BACK.XLS P.age 23 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 8)I Analytical Uncertainty in Heat Transfer Surface Area Ao Do Ud L UL tin Utfin hfin Uhfin UAolAo UAo 717.51253 0.05208 0.00417 8.75000 0.02100 0.00100 0.00004 0.11225 0.00166 0.04877 34.99475 Derivatives: 
-5904.62 82.00 7938.80 14942.99 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty in Observed Heat Transfer Resistance (R): 4 Analytical Uncertainty in Observed Rf 5 Analytical Uncertainty in Overall Extrapolation Heat Transfer Resistance:
R* ho" Uho hi* Uhi* Rw* URw* Rf URf UR*IR&deg; UR*0.20229 17.37894 2.60684 131.74672 19.76201 0.00025 0.00000 0.03172 0.00000 0,17262 0.03492 6 Analytical Uncertainty in Extrapolated Heat Transfer qR UR* Ao UAo LMTD&deg; Uq*lq. Uq&deg;53651.1809 0.20229 0.03492 717.51253 34.99475 15 12588 0.17937 9623.65803 Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 53 of 55 VY4BACK.XLS Page 24 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate Extrapolated Heat Transfer (Btu/hr)Calculated Uncertainty (Btulhr)(Uq/q)A2 Row1 27115.0002 4450.6333 0.000181 Row2 27904.1646 4604.2525 0.000193 Row3 36015.7472 6029.7452 0.000332 Row4 35666.2354 6005.4969 0.000329 Row5 46950.5838 8081.1324 0.000595 Row6 44459.8155 7692.4843 0.000540 Row7 59405.6714 10627.1947 0.001030 Row8 53651.1809 9623.6580 0.000844 331168.3989 qtot 21058.5416 SRSS 0.063589 SRSS Uqtot/qtot 
=6.36%(66.5 gpm Case)Proto-Power Calc: 97-198 

==Attachment:==

J Rev: A Page 54 of 55 VY4BACK.XLS Page 25 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate Extrapolated Heat Transfer (Btu/hr)Calculated Uncertainty (Btu/hr)(Uq/q)A2 Row1 70294.7986 8445.3499 0.000381 Row2 63265.8492 7611.4575 0.000309 Row3 61001.3988 7353.9743 0.000289 Row4 53941.6362 6510.6279 0.000226 Row5 53234.1862 6439.2884 0.000221 Row6 45755.0059 5539.4034 0.000164 Row7 46831.9924 5683.3513 0.000172 Row8 38456.5123 4668.8780 0.000116 432781.3794 18761 .0171 SRSS 0.043350 SRSS qtot Uqtot/qtot 
=4.33%(200 gpm Case)Proto-Power Caic: 97-198 

==Attachment:==

J VY4BACK.XLS Rev: A Page 55 of 55 Page 1 Attachment K to Proto-Power Calculation 97-198 Revision A Proto-Power Caic: 97-198 

==Attachment:==

K Rev: A Page 1 of 4 COMPARING SPIRAL AND CIRCULAR FINS Area Calculation A view of the spiral fin layout as compared to the circular fin layout is provided below.Let angle cc represent the angle between the plane of the circular fin and the plane of the spiral fin.A differential area in the circular fin is given as: dA = rdrdO The expression for circular fin surface area (times 2 for both sides and disregarding the edge area) taken over a complete traverse of the tube is given as: ACf =2 ,rdrd0 = 2 r(ro -r 2)Where: r. = the fin outside radius which is one half the fin height ri = the inside fin radius which is the tube outside radius Proto-Power Calc: 97-198 

==Attachment:==

K Rev: A Page 2 of 4 The spiral fin surface area (times 2 for both sides and disregarding the edge area) can be approximated by the expression:
A , 2,7a .i'Af ~cosa)2ra-r.The ratio of the two areas becomes: A,: = (cosaJ Acf Angle a is approximated by the expression:
-(fin separation) 1 tan a = 4 ro 4r 0 2 a = tan- -where: X = fin pitch Substituting fin height into the expression yields the following:
a = 2f ntan-' 1 As the angle cc goes to zero, the spiral fin area approaches that of the circular fin. It can be seen that for very small fin separations (i.e., high fin pitch) the smaller the resulting angle oa.For the case of the VY cooler fin geometry: a = = tan-'= tan-'(0.033625) 
= 1.93-2H (2(l.487)(10))
Proto-Power Calc: 97-198 

==Attachment:==

K Rev: A Page 3 of 4 The resulting area ratio is then: A,. cos(1.93) 1.00057 This difference is negligible and is bounded by the uncertainty in the analysis presented in Attachment J.Heat Transfer Coefficient The fin geometry affects the calculation of the outside heat transfer film coefficient (h,,)for condensing modes of operation.
Vertical (circular) fins provide for better condensation heat transfer since the condensate falls away from the fins at a faster rate than if the fin were inclined (i.e., spiral geometry).
As shown in the area discussion above, the angular difference between the circular fin geometry and the spriral fin geometry for the VY coils with a fin pitch of 10 fins per inch is very small (i.e., <20).The angle of incline, therefore, is deemed to be sufficiently small as to make the difference between circular and spiral fin geometries negligible even for condensing modes of operation.
In other words, as far as condensation removal from the fin surfaces is concerned, the 10 fin per inch fin pitch of the VY coils results in a fin orientation that is sufficiently close to vertical as to make differences in condensation heat transfer predictions negligible.
Proto-Power Calc: 97-198 

==Attachment:==

K Rev: A Page 4 of 4 Attachment L to Proto-Power Calculation 97-198 Revision A Proto-Power Calc: 97-198 

==Attachment:==

L Rev: A Page 1 of 5 COMED NUCLEAR DESIGN INFORMATION TRANSMITTAL
[ SAFETY-RELATED Originating Organization NDIT No.: LS-0847 " E] NON-SAFETY-RELATED Section: SE Upgrade: 0 fl REGULATORY RELATED Company: CornEd Page 1 of 2 Station: LaSalle County Units: 1.2 System: To: P hilpot, Lloyd. Proto-Power Design Change Authority No NIA VY 

==Subject:==
Dimensional Verification for Tubing and Fins for Coolers 1(2)VYO3A and 1(2)VY04A.
Miller, William J. System Engineer E n, '14el&#xfd; &#xfd; r, _v 716/98 Preparer Position:
Dt Friedrich, Rich Engineer 7//9 Revewer Position:
Date hall, Rich DE- Mech. Supv. 716/98 Approver.
Position:
* Date Status of Information: 
[ Approved for Use [C Unverified Verification Method N/A[] Engineering Judgement Schedule: Purpose of Issuance Transmittal of Dimensions to Proto-Power for Heat Exchanger analysis.Source of Information Walkdown performed on the 2VYO3A and 2VYO4A coolers performed by W. Miller (System Engineering) and R. Frieddrick (Design Engineering) on 7/3198.Description of Information The following measurements were obtained for the 2VY03A and 2VY04A room coolers at the request of Proto-Power Corporation.
These conditions were obtained at ambient conditions with the systems shutdown.
Attached is a copy of a sketch for each cooler that provides dimensions obtained in the field.The following information was obtained for the 2VY03A cooler Tube outside diameter:
0.672 inches Fin Height: 1.452 inches Transverse Tube Pitch: 1.410 Inches Effective Finned Tube Length: 108 inches (dimension is based on 111 inches from the inside of the furthest separated tube support"end" plates, which includes three -1 inch tube support plates between the end plates).The following information was obtained for the 2VY04A cooler Distribution:
SEAG Szumski, Daniel R. -CornEd. SES-BOP Wilhelmsen, George R. -CornEd, SES-BOP Proto-Power Calc: 97-198 

==Attachment:==

L Rev: A Page 2 of 5 WIN No.:
COMED NUCLEAR DESIGN INFORMATION TRANSMITTAL
[ SAFETY-RELATED Originating Organization NDIT No.: LS-0847 "[] NON-SAFETY-RELATED Section: SE Upgrade: 0 E] REGULATORY RELATED Company: CornEd Page 2 of 2 Tube outside diameter:
0.675 inches Fin Height: 1.347 inches Transverse Tube Pitch: 1.370 inches Effective Finned Tube Length: 105 inches (dimension is based on 108 inches from the inside of the furthest separated tube support'end" plates, which include three -1 inch tube support plates between the end plates).The first three measurement for each cooler were taken with a calibrated set of calipers (MMD Id No 7140, calibration due 2199). The Effective Finned Tube Length was taken with a metal tape measure. The uncertainities for these measurements are based on engineering best estimates for the measurement techiniques used and are as stated in NDIT LS-0835 dated 6/19/98. Each cooler appeared to have staggered rows of tubes. The transverse tube pitch was variable for the various individual fins and the above dimension is considered typical.Attachment"1 contains two sheets with sketches of the identical dimensions provided above.NDIT LS-0847, Page 2 of 2 end. Attached -2 pages of sketch.Proto-Power Calc: 97-198 

==Attachment:==

L Rev: A Page 3 of 5 I CornEd -Nuclear Operations Disivion I 
&#xfd;N~T ..S-084i7 2VIYO3S~Acnim e )01 2-K- ..SI I!I (-S.T (H'IC I f H .q52'-1L/

==Attachment:==

L 4 of 5 S 14Z 4/- 1&#xfd; 1C)s if -I 1 11-11 1- -11 1141 '11 51 111 Jill J1Ij#:D 0, 672 1-4-I 
%)- L( 47 cci I 2_VV/o P i / I St I.4/...I'I 4/Proto-Power Calc: 97-.198 

==Attachment:==

L ,~:4Qb I Page 5 of 5 djO.75" Attachment M to Proto-Power Calculation 97-198 Revision A Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 1 of 27 18:40:27 PROTO-HX 3.01 by Proto-Power Corporation (SNPHIX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils-Fouling Sensitivity (Tube f = 0.0000)07/10/98 Air Coil Heat Exchanger Input Parameters Air-Side FMl-id-Q-l 33.4. 0-0-i-Inlet Dry Bulb Temp 150.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature OF Outlet Wet Bulb Temp OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Tube-Side 105.00 OF OF Fresh Water 0.002000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft.&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F) 105.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 20.00 0.5270 0.6250 2.000 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 2 of 27 18:40:27 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/10/98 ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0000)Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (OF)Air Dry Bulb Temp Out (OF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (OF)Wet Bulb Temp Out (OF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (&deg;F)Tube Temp Out (OF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm) 39.20 Air Flow (acfin) 30,048.00 Tube Inlet Temp (OF) 100.00 Air Inlet Temp (OF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (OF) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 3 of 27 18:40:27 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f= 0.0000)07/10/98 Extrapolation Calculation Summary II I. *1 Mass Flow (ibm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft.hr)
Density (Ibm/fl 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr'ftP"F)
Air-Side 111,037.50 148.00 128.40 Tube-Side 19,492.05 100.00 127.96 Tube-Side hi (BTU/hr fit 2.F)j Factor Air-Side ho (BTU/hr ft2.&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr ft 2 E-F/BTU) 0.00200000 U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)2,870.05 544,475 544,475 II Extrapolation calculation for Row Il(Dry)II Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftihr)
Skin Visc (lbm/ft-hr)
Density (lbrn/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft.&deg;F)
Air-Side 111,037.50 148.00 143.15 0.0203 0.0203 145.58 133.53 5,782.55 2,102 0.7253 0.0491 0.0621 0.2402 0.0163 Tube-Side 19,492.05 115.91 129.74 122.82 133.09 0.72 5,387 3.5310 1.3114 1.1959 61.6674 0.9990 0.3710 Tube-Side hi (BTU/hr.ft 2.&deg;F) 281.44 j Factor 0.0105 Air-Side ho (BTU/hr ft 2.&deg;F) 18.13 Tube Wall Resistance (hr-ft2. F/BTU 0.00024732 Overall Fouling (hr- ft2.'F/BTU) 

==0.0 0200000==
U Overall (BTU/hr ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)8.55 717.51 21.96 134,672 0.8902 134,672 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 4 of 27*** Air Mass Velocity (Lbrm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:40:27 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0000)07/10/98 ra Extrapolation Calculation for Row 2(Dry)II I. *1 Air-Side Mass Flow (lbm./hr) 111,037.50 Inlet Temperature (0 F) 143.15 Outlet Temperature (OF) 138.72 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 140.94 Skin Temperature (0 F) 129.91 Velocity *** 5,782.55 Reynold's Number 2,114 Prandtl Number 0.7258 Bulk Visc (lbm/ft-hr) 0.0488 Skin Visc (Ibm/ft.hr)
Density (Ibm/ift 3) 0.0625 Cp (BTU/Ibm'&deg;F) 0.2402 K (BTU/hr'tt.
0 F) 0.0162 Tube-Side 19,492.05 113.54 126.18 119.86 129.51 0.72 5,239 3.6397 1.3482 1.2342 61.7138 0.9988 0.3700 Tube-Side hi (BTU/hr. ft 2 0'F) 273.39 j Factor 0.0105 Air-Side ho (BTU/hr-ft 2-&deg;F) 18.08 Tube Wall Resistance (hr'ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr-ftl-&deg;F/BTU) 

==0.0 0200000==
U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)8.42 717.51 20.37 123,101 0.8904 123,101 Extrapolation Calculation for Row 3(Dry)II .3 Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr-fti.F)
Air-Side 111,037.50 138.72 133.14 0.0203 0.0203 135.93 122.07 5,782.55 2,128 0.7262 0.0485 0.0631 0.2402 0.0160 Tube-Side 19,492.05 99.99 115.91 107.95 121.57 0.72 4,662 4.1372 1.5151 1.3267 61.8887 0.9988 0.3658 Tube-Side hi (BTU/hr-ftf 2.F) 242.87 j Factor 0.0105 Air-Side ho (BTU/hr-itV.&deg;F) 18.04 Tube Wall Resistance (hr-ft 2 -F/BTU 0.00024732 Overall Fouling (hr.ft 2-&deg;F/BTU) 0.00200000 U Overall (BTU/hr. ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.96 717.51.27.13 154,912 0.8907 154,912 Proto-Power Calc" 97-198 

==Attachment:==

M pev: A Page 5 of 27*** Air Mass Velocity (Lbrn/hrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:40:27 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0000)07/10/98 Extrapolation Calculation for Row 4(Dry)II*1 Air-Side Mass Flow (lbm/hr) 111,037.50 Inlet Temperature (0 F) 133.14 Outlet Temperature (OF) 128.40 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 130.77 Skin Temperature (OF) 118.96 Velocity *** 5,782.55 Reynold's Number 2,142 Prandtl Number 0.7266 Bulk Visc (lbm/ft-hr) 0.0482 Skin Visc (Ibm/ft hr)Density (Ibm/ft3) 0.0636 Cp (BTU/Ibm-0 F) 0.2402 K (BTU/hrftf-PF) 0.0159 Tube-Side 19,492.05 100.00 113.54 106.77 118.53 0.72 4,606 4.1926 1.5335 1.3653 61.9050 0.9989 0.3654 Tube-Side hi (BTU/hr-ft 2 i.F) 239.09 j Factor 0.0105 Air-Side ho (BTU/hr'ftl 2-F) 17.99 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr- ft 2.F/BTU) 0.00200000 U Overall (BTU/hr ft 2.&deg;F)Effective Area (fV)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)7.89 717.51 23.29 131,790 0.8909 131,790 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 6 of 27*** Air Mass Velocity (Lbmr/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Moist Air Properties 
-- Given Dry Bulb and Specific Humidity Total Pressure:
P =Dry Bulb Temperature:
T =Specific Humidity:
W -Water Vapor Pressure:
Pv = (W*Rv*P)/(Ra+(W*Rv)) 
=Dry Air Pressure:
Pa =P -Pv =Dry Air Density: Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Water Vapor Density: Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Moist Air Density: Rho= Rho a + Rho v =Saturated Air Pressure:
Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*T5) =Moist Air Relative Humidity:
RH = Pv /Ps -Equation Coefficients:
a =b=CbCd=0e=-f 0".4 00-4 14.315 psia 128.4 OF 0.020273629 0.451874518 psia 13.86312548 psia 0.063627362 Ibm/ft 3 0.001289958 Ibm/ft 3 0.064917319 Ibm/ft 3 2.131789935 psia 2.1695334 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071 E-1 1 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]
18:48:38 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: t(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils-Fouling Sensitivity (Tube f = 0.0000)07/10/98 Air Coil Heat Exchanger Input Parameters AI F lUiiffQu-antii, Tta Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Air-Side 32-, GU-aoc-frii OF OF OF OF Tube-Side....82_00 gpm 105.00 OF Fresh Water 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-flt.F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-f.'
0 F)105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 20.00 0.5270 0.6250 1.500 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 8 of 27 18:48:38 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0000)7/10/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfirn)Air Dry Bulb Temp In (IF)Air Dry Bulb Temp Out (OF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (IF)Wet Bulb Temp Out (IF)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (IF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm)Air Flow (aefmn)Tube Inlet Temp (IF)Air Inlet Temp (IF)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (IF)Atmospheric Pressure 27.30 29,078.95 100.00 128.4 21.20 0.00 14.315 Idi 00 V; &-.. Ilea Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 9 of 27 18:48:38 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0000)07/10/98 Extrapolation Calculation Summary II Mass Flow (lbrn/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Vise (lbm/ft-hr)
Density (ibm/fl 3)Cp (BTU/Ibm."F)
K (BTU/hr-ft.&deg;F)
Air-Side 111,037.47 128.40 116.70 Tube-Side 13,574.82 100.00 124.00 Tube-Side hi (BTU/hr'ft 2"&deg;F)j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr-ft 2_-F/BTU 0.00024732 Overall Fouling (hr ft 2-0 F/BTU) 0.00200000 U Overall (BTU/hr ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5,740.10 324,952 324,952 w II Extrapolation Calculation for Row l(Dry)II-I Mass Flow (lbmlhr)Inlet Tepiperature 
(&deg;F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (Ibm/ft-hr)
Skin Visc (lbm/ft'hr)
Density (Ibm/fl 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr'ft.&deg;F)
Air-Side 111,037.47 128.40 127.53 0.0203 0.0203 127.97 125.96 5,782.55 1,612 0.7268 0.0480 0.0637 0.2402 0.0159 Tube-Side 13,574.82 121.01 124.56 122.79 125.88 0.50 3,750 3.5322 1.3118 1.2751 61.6679 0.9989 0.3710 Tube-Side hi (BTU/hr4ftV-&deg;F) 168.13 j Factor 0.0115 Air-Side ho (BTU/hr ft 2 -F) 19.83 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr ft 2 f-F/BTU) 0.00200000 U Overall (BTU/hr.ftl 2-F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.76 717.51 4.96 24,066 0.8815 24,066 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 10 of 27*** Air Mass Velocity (Lbrn/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:48:38 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0000)07/10/98 Extrapolation Calculation for Row 2(Dry)II i .Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)
Skin Vise (lbmr/lthr)
Density (lbm/ft 3)Cp (BTU/Ibm-'F)
K (BTU/hr-ft-&deg;F)
Air-Side 111,037.47 127.53 126.62 0.0203 0.0203 127.08 124.96 5,782.55 1,614 0.7269 0.0479 0.0638 0.2402 0.0158 Tube-Side 13,574.82 119.68 123.43 121.56 124.87 0.50 3,708 3.5768 1.3269 1.2869 61.6874 0.9988 0.3705 Tube-Side hi (BTU/hr'ft 2.&deg;F) 165.77 j Factor 0.0115 Air-Side ho (BTU/hr" ft 2-&deg;F) 19.82 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2 0 F/BTU) 0.00200000 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.71 717.51 5.29 25,442 0.8815 25,442 Extrapolation Calculation for Row 3(Dry)II*1 Mass Flow (lbm/hr)Inlet Temperature 
(&deg;F)Outlet 'temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (ibm/fl 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr.ftt.F)
Air-Side 111,037.47 126.62 125.40 0.0203 0.0203 126.01 123.19 5,782.55 1,617 0.7270 0.0479 0.0640 0.2402 0.0158 Tube-Side 13,574.82 116.02 121.01 118.51 123.08 0.50 3,603 3.6909 1.3655 1.3083 61.7345 0.9988 0.3695 Tube-Side hi (BTU/hr.ft 2-&deg;F) 160.04 j Factor 0.0115 Air-Side ho (BTU/hr.ft 2.&deg;F) 19.81 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr- ft 2.&deg;F/BTU) 0.00200000 U Overall (BTU/hr-ft2"&deg;F)
Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.56 717.51 7.19 33,875 0.8816 33,875 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 11 of 27*** Air Mass Velocity (Lbrn/hr-fti), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:48:38 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0000)07/10/98 Kk=====Extrapolation Calculation for Row 4(Dry)II t..Air-Side Mass Flow (lbm/hr) 111,037.47 Inlet Temperature 
(&deg;F) 125.40 Outlet Temperature (OF) 124.17 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 124.78 Skin Temperature (IF) 121.95 Velocity *** 5,782.55 Reynold's Number 1,619 Prandtl Number 0.7271 Bulk Vise (lbm/ft-hr) 0.0478 Skin Vise (lbmr/f-hr)
Density (Ibm/ft 3) 0.0641 Cp (BTU/1bm-'F) 0.2402 K (BTU/hr'ft-'F) 0.0158 Tube-Side 13,574.82 114.65 119.68 117.17 121.84 0.50 3,557 3.7434 1.3832 1.3235 61.7551 0.9988 0.3691 Tube-Side hi (BTU/hr'ft 2"&deg;F) 157.40 j Factor 0.0115 Air-Side ho (BTU/hr. ft 2.&deg;F) 19.80 Tube Wall Resistance (hr'ft-'&deg;F/BTU 

==0.0 0024732==
Overall Fouling (hr' ft 2.&deg;F/BTU) 0.00200000 U Overall (BTU/hr-ft 2.0 F)Effective Area (ft')LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.50 717.51 7.32 34,118 0.8816 34,118 Extrapolation Calculation for Row 5(Dry)11 I.Air-Side Mass Flow (lbm/hr) 111,037.47 Inlet Temperature (IF) 124.17 Outlet (IF) 122.49 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 123.33 Skin Temperature (IF) 119.47 Velocity *** 5,782.55 Reynold's Number 1,622 Prandtl Number 0.7272 Bulk Vise (lbm/ft-hr) 0.0477 Skin Vise (Ibm/fl hr)Density (Ibm/fl 3) 0.0643 Cp (BTU/lbm'&deg;F) 0.2402 K (BTU/hr'f-'
0 F) 0.0158 Tube-Side 13,574.82 109.14 116.02 112.58 119.31 0.50 3,401 3.9314 1.4464 1.3552 61.8230 0.9988 0.3675 Tube-Side hi (BTU/hr- ft 2-&deg;F) 148.72 j Factor 0.0115 Air-Side ho (BTU/hr-ft1.&deg;F) 19.78 Tube Wall Resistance (hr-fl 2 -F/BTU 0.00024732 Overall Fouling (hr- ft 2.&deg;F/BTU) 0.00200000 U Overall (BTU/hr.ft 2.0 F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.27 717.51.10.36 46,594 0.8817 46,594 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 12 of 27*** Air Mass Velocity (Lbrn/hrft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 18:48:38 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0000) " 07/10/98 29===Extrapolation Calculation for Row 6(Dry)II I.Air-Side Mass Flow (lbm/hr) 111,037.47 Inlet Temperature (0 F) 122.49 Outlet Temperature (OF) 120.90 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 121.70 Skin Temperature (OF) 118.03 Velocity *** 5,782.55 Reynold's Number 1,626 Prandtl Number 0.7273 Bulk Visc (lbm/ft-hr) 0.0476 Skin Visc (lbm/ftrhr)
Density (Ibm/ft 3) 0.0645 Cp (BTU/lbm'0 F) 0.2402 K (BTU/hr-ft 0.F) 0.0157 Tube-Side 13,574.82 108.12 114.65 111.38 117.88 0.50 3,361 3.9829 1.4636 1.3738 61.8403 0.9988 0.3670 Tube-Side hi (BTU/hr-ft 2.F) 146.29 j Factor 0.0115 Air-Side ho (BTU/hr ft2-&deg;F) 19.76 Tube Wall Resistance (hr ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2.&deg;F/BTU) 0.00200000 U Overall (BTU/hr ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.20 717.51 9.94 44,247 0.8818 44,247 II Extrapolation Calculation for Row 7(Dry)II Air-Side Mass Flow (ibm/hr) 111,037.47 Inlet Temperature (OF) 120.90 Outlet Temperature (OF) 118.68 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (&deg;F) 119.79 Skin Temperature (OF) 114.69 Velocity *** 5,782.55 Reynold's Number 1,630 Prandtl Number 0.7274 Bulk Visc (Ibm/ft-hr) 0.0475 Skin Visc (lbm/ftihr)
Density (lbm/ft 3) 0.0647 Cp (BTU/Ibm-&deg;F) 0.2402 K (BTU/hr'ft-&deg;F) 0.0157 Tube-Side 13,574.82 100.05 109.14 104.60 114.49 0.50 3,137 4.2974 1.5683 1.4195 61.9344 0.9988 0.3645 Tube-Side hi (BTU/hr fi2-'F) 133.31 j Factor 0.0115 Air-Side ho (BTU/hr.ft 2-F) 19.74 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr-fl2.&deg;F/BTU) 

==0.0 0200000==
U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ftf)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.84 717.51 14.71 61,662 0.8819 61,662 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 13 of 27 Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 18:48:38 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0000)07/10/98 Extrapolation Calculation for Row 8(Dry)II II I Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr-ft 0'F)Air-Side 111,037.47 118.68 116.70 0.0203 0.0203 117.69 113.14 5,782.55 1,635 0.7276 0.0473 0.0649 0.2402 0.0156 Tube-Side 13,574.82 100.02 108.12 104.07 112.97 0.50 3,120 4.3236 1.5770 1.4408 61.9414 0.9989 0.3643 Tube-Side hi (BTU/hr ft 2-&deg;F) 132.06 j Factor 0.0115 Air-Side ho (BTU/hr ft 2-&deg;F) 19.72 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr ft 2-&deg;F/BTU) 0.00200000 U Overall (BTU/hr. ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.81 717.51 13.19 54,947 0.8820 54,947 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 14 of 27*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 19:01:31 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0040)07/10/98 Air Coil Heat Exchanger Input Parameters I F I ihii k-Q-iti if iT6vt a-Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperatu Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side..33,5-46_0-0 ac--fim 150.00 OF 92.00 OF ire OF OF Tube-Side.-1-l870-0 gpm 105.00 OF OF Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)
Heat Exchanger Type Fin Type Fin Configuration Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-VF)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr-ft.&deg;F)
Fresh Water 0.004000 0.002000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Cooler 04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]105.000 10.000 128.000 0.0120 0.0120 1.347 2 4 20.00 20.00 0.5270 0.6250 2.000 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 15 of 27 19:01:31 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 7/10/98 CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils kv Fouling Sensitivity (Tube f = 0.0040)Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfrn)Air Dry Bulb Temp In ('F)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In ('F)Wet Bulb Temp Out (&deg;F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (fF)Tube Temp Out (&deg;F)Condensate Temperature (fF)Extrapolation Data Tube Flow (gpm) 39.20 Air Flow (acfm) 29,874.00 Tube Inlet Temp ('F) 100.00 Air Inlet Temp (0 F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (0 F) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 16 of 27 19:01:31 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0040)07/10/98 V --Extrapolation Calculation Summary II Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Vise (lbm/ftihr)
Density (Ibm/fr')Cp (BTU/Ibm'&deg;F)
K (BTU/hr'ft'&deg;F)
Air-Side 110,394.51 148.00 132.06 Tube-Side 19,492.05 100.00 122.59 Tube-Side hi (BTU/hr-ft 2.&deg;F)j Factor Air-Side ho (BTU/hr-ft 2.&deg;F)Tube Wall Resistance (hr-ft 2.&deg;F/BTU Overall Fouling (hr. ft 2-&deg;F/BTU)U Overall (BTU/hr.ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00024732

==0.0 6143499==
2,870.05 440,315 440,315 II Extrapolation Calculation for Row l(Dry)11*1 Air-Side Mass Flow (Ibm/hr) 110,394.51 Inlet Temperature (IF) 148.00 Outlet Temperature (OF) 144.01 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 146.01 Skin Temperature (OF) 136.31 Velocity *** 5,749.07 Reynold's Number 2,089 Prandtl Number 0.7253 Bulk Visc (Ibm/fti.hr) 0.0491 Skin Visc (Ibm/fIthr)
Density (lbm/ft 3) 0.0620 Cp (BTU/Ibm'&deg;F) 0.2402 K (BTU/hr-ft-&deg;F) 0.0163 Tube-Side 19,492.05 112.40 123.72 118.06 126.70 0.72 5,151 3.7084 1.3714 1.2657 61.7415 0.9989 0.3694 Tube-Side hi (BTU/hrtft 2"&deg;F) 268.27 j Factor 0.0106 Air-Side ho (BTU/hr-ft 2.&deg;F) 18.06 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr- ft 2.&deg;F/BTU) 0.06143499 U Overall (BTU/hr. ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.58 717.51 27.52 110,158 0.8906 110,158 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 17 of 27*** Air Mass Velocity (Lbm/hr-ft'), Tube Fluid Velocity (ft/sec):
Air Density at Inlet T, Other Properties at Average T 19:01:31 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f= 0.0040)07/10/98 Extrapolation Calculation for Row 2(Dry)_11 Mass Flow (lbmlhr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (ibm/ft-hr)
Skin Visc (Ibm/ft-hr)
Density (lbM/ft 3)Cp (BTU/Ibm'&deg;F)
K (BTU/hr-ftf.F)
Air-Side 110,394.51 144.01 140.33 0.0203 0.0203 142.17 133.22 5,749.07 2,099 0.7257 0.0489 0.0624 0.2402 0.0162 Tube-Side 19,492.05 111.04 121.47 116.25 124.36 0.72 5,062 3.7797 1.3954 1.2930 61.7689 0.9988 0.3688 Tube-Side hi (BTU/hr ft 2.'F) 263.29 j Factor 0.0105 Air-Side ho (BTU/hr ft 2.F) 18.02 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr- ft 2.&deg;F/BTU) 0.06143499 U Overall (BTU/hr. ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.54 717.51 25.53 101,543 0.8907 101,543 Extrapolation Calculation for Row 3(Dry)II Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (lbm/rft)Cp (BTU/lbm-&deg;F)
K (BTU/hr-ftV'F)
Air-Side 110,394.51 140.33 135.95 0.0203 0.0203 138.14 127.46 5,749.07 2,109 0.7260 0.0486 0.0628 0.2402 0.0161 Tube-Side 19,492.05 99.97 112.40 106.18 116.91 0.72 4,579 4.2204 1.5428 1.3867 61.9130 0.9988 0.3651 Tube-Side hi (BTU/hr ft2.&deg;F) 237.18 j Factor 0.0105 Air-Side ho (BTU/hr-ft2-&deg;F) 17.99 Tube Wall Resistance (hr-ft 2.0 F/BTU 0.00024732 Overall Fouling (hr-ft 2-F/BTU) 0.06143499 U Overall (BTU/hr-ft2-F)Effective Area (ft)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.36 717.51.31.51 121,070 0.8909 121,070 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 18 of 27**Air Mass Velocity (Lbmihr-ft2), 'rube Fluid Velocity (ft/sec), Air Density at Inlet T, Other Properties at Average T 19:01:31 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: l(2)VY04A-Front 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0040)07/10/98 U --- -~. ,.Extrapolation Calculation for Row 4(Dry)II II .5 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibml/fthr)
Skin Visc (lbm//.fhr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr.ft.&deg;F)
Air-Side 110,394.51 135.95 132.06 0.0203 0.0203 134.00 124.50 5,749.07 2,121 0.7264 0.0484 0.0632 0.2402 0.0160 Tube-Side 19,492.05 99.99 111.04 105.51 115.12 0.72 4,547 4.2527 1.5535 1.4108 61.9221 0.9989 0.3649 Tube-Side hi (BTU/hr ft 2.&deg;F) 235.01 j Factor 0.0105 Air-Side ho (BTU/hr-ft 2-IF) 17.95 Tube Wall Resistance (hr-ft 2"&deg;F/BTU 0.00024732 Overall Fouling (hr'ft-'&deg;F/BTU) 

==0.0 6143499==
U Overall (BTU/hr'ft 2 -F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.34 717.51 28.09 107,544 0.8911 107,544 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 19 of 27*** Air Mass Velocity (Lbrnr/hr'ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Moist Air Properties 
--Total Pressure: Dry Bulb Temperature:
Specific Humidity: Water Vapor Pressure: Dry Air Pressure: Dry Air Density: Water Vapor Density: Moist Air Density: Saturated Air Pressure: Moist Air Relative Humidity: Equation -Coefficients:
Given Dry Bulb and Specific HumidityPv = (W*Rv*P)/(Ra+(W*Rv)) 
=Pa =P -Pv =Rho a = (144/53.352)*(Pa/(459.67+T)) 
=Rho v = (144/85.778)*(Pv/(459.67+T)) 
=Rho = Rho a + Rho v =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*TS) =RH = Pv/Ps a=b=C=d=e=f=14.315 psia 132.06 OF 0.020273629 0.451874518 psia 13.86312548 psia 0.063233811 Ibm/ft 3 0.001281979 Ibm/ft 3 0.064515789 Ibm/ft 3 2.350592396 psia 19.22385687%
2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 2.109071 E-1 1 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]>00 r 0-k) 0 0 00 004 19:06:23 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Data Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils-Fouling Sensitivity (Tube f = 0.0040)07/10/98 Air Coil Heat Exchanger Input Parameters FletidrQ-fi~t~ty, Bulboteamp Inlet Dry Bulb Temp Inlet Wet Bulb Temp, Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Tube Fluid Name Tube Fouling Factor Air-Side Fouling Air-Side...324830a-a-Dff OF OF OF OF Tube-Side--....-.----.
82T.0 gpm 105.00 OF OF Fresh Water 0.004000 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle Cooler 1(2)VY04A j = EXP[-1.9210 
+ -0.3441
* LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)
Fin Conductivity (BTU/hr-ft-&deg;F)
Fin Tip Thickness (inches)Fin Root Thickness (inches)Circular Fin Height (inches)Number of Coils Per Unit Number of Tube Rows Number of Tubes Per Row Active Tubes Per Row Tube Inside Diameter (in)Tube Outside Diameter (in)Longitudinal Tube Pitch (in)Transverse Tube Pitch (in)Number of Serpentines Tube Wall Conductivity (BTU/hr ft-&deg;F)105.000 10.000 128.000 0.0120 0.0120 1.347 2 8 20.00 20.00 0.5270 0.6250 1.500 1.370 2.000 225.00 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 21 of 27 19:06:23 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0040)7/10/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used Test Data Data Date Air Flow (acfm)Air Dry Bulb Temp In (fF)Air Dry Bulb Temp Out ('F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (fF)Wet Bulb Temp Out ('F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (fF)Tube Temp Out ('F)Condensate Temperature 
('F)Extrapolation Data Tube Flow (gpm)Air Flow (acfm)Tube Inlet Temp (fF)Air Inlet Temp ('F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (fF)Atmospheric Pressure 27.30 29,090.18 100.00 132.1 19.22 0.00 14.315 eKLA coi~ (ll fi V Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 22 of 27 19:06:23 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0040)07/10/98 Extrapolation Calculation Summary II I.Air-Side Mass Flow (lbm/hr) 110,394.53 Inlet Temperature (0 F) 132.06 Outlet Temperature (OF) 120.05 Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft-hr)
Density (IbM/fl 3)Cp (BTU/lbm-&deg;F)
K (BTU/hr4ft.&deg;F)
Tube-Side 13,574.82 100.00 124.49 Tube-Side hi (BTU/hr. ft2 .F)j Factor Air-Side ho (BTU/hr" ft 2.&deg;F)Tube Wall Resistance (hrtft2. F/BTU 0.00024732 Overall Fouling (hr- ft 2.F/BTU) 0.06143499 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (fi2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5,740.10 331,663 331,663 Extrapolation Calculation for Row l(Dry)II Mass Flow (lbm/hr)Inlet Temperature (7F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ftihr)
Density (lbm/ft)Cp (BTU/lbm'&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 110,394.53 132.06 131.00 0.0203 0.0203 131.53 129.15 5,749.07 1,596 0.7266 0.0482 0.0634 0.2402 0.0159 Tube-Side 13,574.82 120.78 125.08 122.93 126.59 0.50 3,755 3.5272 1.3101 1.2669 61.6657 0.9989 0.3710 Tube-Side hi (BTU/hruft2-&deg;F) 168.53 j Factor 0.0116 Air-Side ho (BTU/hr-ft 2 d-F) 19.79 Tube Wall Resistance (hr-ft 2 ,&deg;F/BTU 0.00024732 Overall Fouling (hr-ft 2-&deg;F/BTU) 0.06143499 U Overall (BTU/hr-ft2-&deg;F)
Effective Area (ft2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.83 717.51.8.41 29,136 0.8817 29,136 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 23 of 27*** Air Mass Velocity (Lbrn/hr'ft 2), 'rube Fluid Velocity (ftlsec);
Air Density at Inlet T, Other Properties at Average T 19:06:23 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: l(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f= 0.0040)07/10/98 Extrapolation Calculation for Row 2(Dry)I1 1.Air-Side Mass Flow (lbmr/hr) 110,394.53 Inlet Temperature (OF) 131.00 Outlet Temperature (OF) 129.94 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp ("F) 130.47 Skin Temperature (OF) 128.07 Velocity *** 5,749.07 Reynold's Number 1,598 Prandtl Number 0.7266 Bulk Visc (lbm/ft-hr) 0.0481 Skin Visc (lbm/ftrhr)
Density (lbrn/f 3) 0.0635 Cp (BTU/lbm-'F) 0.2402 K (BTU/hr-ft-'F) 0.0159 Tube-Side 13,574.82 119.55 123.90 121.72 125.48 0.50 3,713 3.5707 1.3249 1.2798 61.6847 0.9988 0.3706 Tube-Side hi (BTU/hr. ft 2-.F) 166.19 j Factor 0.0116 Air-Side ho (BTU/hr-ft 2."F) 19.78 Tube Wall Resistance (hr-ft 2"&deg;F/BTU 0.00024732 Overall Fouling (hr' ft 2.'F/BTU) 0.06143499 U Overall (BTU/hr-ftt 2.F)Effective Area (ftf)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.80 717.51 8.56 29,453 0.8817 29,453 II Extrapolation Calculation for Row 3(Dry)II 1 I. *1 Mass Flow (Ibm/hr)Inlet Tepnperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fthr)
Skin Visc (lbm/ft-hr)
Density (lbm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr.ft.&deg;F)
Air-Side 110,394.53 129.94 128.59 0.0203 0.0203 129.27 126.24 5,749.07 1,600 0.7267 0.0481 0.0636 0.2402 0.0159 Tube-Side 13,574.82 115.31 120.78 118.04 122.98 0.50 3,587 3.7091 1.3716 1.3095 61.7417 0.9988 0.3694 Tube-Side hi (BTU/hr.ft 2_-F) 159.19 j Factor 0.0116 Air-Side ho (BTU/hr-ft 2 i-F) 19.77 Tube Wall Resistance (hr-ft7-.F/BTU 

==0.0 0024732==
Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 6143499==
U Overall (BTU/hr.ft 2 -F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.71 717.51 10.99 37,111 0.8818 37,111 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 24 of 27*** Air Mass Velocity (Lbrnihr-ftl), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 19:06:23 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0040)07/10/98 kQ====== i Extrapolation Calculation for Row 4(Dry)II I *1 Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (Ibm/ft hr)Skin Vise (Ibm/ft-hr)
Density (lbm/ft 3)Cp (BTU/lbm-'F)
K (BTU/hr'ft'&deg;F)
Air-Side 110,394.53 128.59 127.28 0.0203 0.0203 127.94 124.97 5,749.07 1,603 0.7268 0.0480 0.0638 0.2402 0.0159 Tube-Side 13,574.82 114.19 119.55 116.87 121.77 0.50 3,547 3.7550 1.3871 1.3243 61.7595 0.9988 0.3690 Tube-Side hi (BTU/hr'ft 2.&deg;F) 156.87 j Factor 0.0116 Air-Side ho (BTU/hr ft 2.&deg;F) 19.75 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr ft2-&deg;F/BTU) 

==0.0 6143499==
U Overall (BTU/hr. ft 2.&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.68 717.51 10.84 36,360 0.8819 36,360 I Extrapolation Calculation for Row 5(Dry)11 II Mass Flow (ibm/hr)Inlet Temperature 
(&deg;F)Outlet Temperature 
(&deg;F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature 
(&deg;F)Velocity ***Reynold's Number Prandtl Number Bulk Vise (Ibm/fl-hr)
Skin Visc (Ibm/ft hr)Density (Ibm/ft 3)Cp (BTU/Ibm-&deg;F)
K (BTU/hr-ft-'F)
Air-Side 110,394.53 127.28 125.59 0.0203 0.0203 126.43 122.63 5,749.07 1,606 0.7270 0.0479 0.0639 0.2402 0.0158 Tube-Side 13,574.82 108.44 115.31 111.87 118.55 0.50 3,378 3.9617 1.4565 1.3650 61.8333 0.9988 0.3672 Tube-Side hi (BTU/hr ft 2 0-F) 147.30 j Factor 0.0116 Air-Side ho (BTU/hr- ft 2-&deg;F) 19.74 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr-ft2-&deg;F/BTU) 

==0.0 6143499==
U Overall (BTU/hr-ft 2.&deg;F)Effective Area (ft')LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.55 717.51 14.27 46,554 0.8819 46,554 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 25 of 27*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 19:06:23 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
ComEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0040)07/10/98 Extrapolation Calculation for Row 6(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)
Skin Visc (lbm/ft.hr)
Density (lbm/ft 3)Cp (BTU/lbm.&deg;F)
K (BTU/hrV-.&deg;F)
Air-Side 110,394.53 125.59 124.00 0.0203 0.0203 124.79 121.20 5,749.07 1,610 0.7271 0.0478 0.0641 0.2402 0.0158 Tube-Side 13,574.82 107.69 114.19 110.94 117.34 0.50 3,346 4.0022 1.4701 1.3809 61.8466 0.9988 0.3669 Tube-Side hi (BTU/hr ft 2"&deg;F) 145.39 j Factor 0.0115 Air-Side ho (BTU/hr ft 2-&deg;F) 19.72 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr- ft 2.F/BTU) 0.06143499 U Overall (BTU/hr-ft 2-&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.52 717.51 13.58 44,025 0.8820 44,025-1 Extrapolation Calculation for Row 7(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft hr)Skin Visc (lbm/ft-hr)
Density (Ibm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr-ft.&deg;F)
Air-Side 110,394.53 124.00 121.93 0.0203 0.0203 122.97 118.31 5,749.07 1,614 0.7272 0.0477 0.0644 0.2402 0.0157 Tube-Side 13,574.82 100.03 10844 Tube-Side hi (BTU/hr. ft 2.F) 132.43 j Factor 0.0115 Air-Side ho (BTU/hr ft 2.&deg;F) 19.70 Tube Wall Resistance (hr-ft 2.&deg;F/BTU 0.00024732 Overall Fouling (hr- ft 2.&deg;F/BTU) 0.06143499 104.23 113.32 0.50 3,125 4.3154 1.5743 1.4359 61.9393 0.9988 0.3644 U Overall (BTU/hr-ft 2..F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.32 717.51 18.40 57,038 0.8821 57,038 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 26 of 27*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T 19:06:23 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)
CornEd -- LaSalle Calculation Report for: 1(2)VY04A-Back 
-CSCS Equipment Area Cooling Coils Fouling Sensitivity (Tube f = 0.0040)07/10/98 Extrapolation Cialculation for Row z(Dry)II 1. 'I Air-Side Mass Flow (Ibmnhr) 110,394.53 Inlet Temperature (OF) 121.93 Outlet Temperature (OF) 120.05 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 120.99 Skin Temperature (OF) 116.74 Velocity *** 5,749.07 Reynold's Number 1,618 Prandtl Number 0.7273 Bulk Visc (Ibm/ft hr) 0.0475 Skin Vise (lbm/fi.hr)
Density (Ibm/fi3) 0.0646 Cp (BTU/Ibm'&deg;F) 0.2402 K (BTU/hr'ft'&deg;F) 0.0157 Tube-Side 13,574.82 100.03 107.69 103.86 112.19 0.50 3,113 4.3339 1.5804 1.4519 61.9442 0.9989 0.3643 Tube-Side hi (BTU/hr ft2.&deg;F) 131.54 j Factor 0.0115 Air-Side ho (BTU/hr'ft2-&deg;F) 19.68 Tube Wall Resistance (hr-ft 2-&deg;F/BTU 0.00024732 Overall Fouling (hr'ft 2"&deg;F/BTU) 0.06143499 U Overall (BTU/hr'ft 2"&deg;F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)4.31 717.51 16.83 51,985 0.8822 51,985 Proto-Power Calc: 97-198 

==Attachment:==

M Rev: A Page 27 of 27*** Air Mass Velocity (Lbrn/hr-ft 2), Tube Fluid Velocity (ft/sec);
Air Density at Inlet T, Other Properties at Average T Attachment N to Proto-Power Calculation 97-198 Revision A Proto-Power Calc: 97-198 

==Attachment:==

N Rev: A Page 1 of 2 Proto-HX Model Databas~e Two separate models are saved on the attached disks as follows: FRONT COIL- (2 Disksj Name: vy-04a-f.phx Size: 1,409,024 bytes Date: 7/10/98 Time: 4:09:12 pm BACK COIL Name: Size: Date: Time:-(2 Disks)vy-04a-b.phx 1,409,024 bytes 7/10/98 4:09:30 pm Proto-Power Calc: 97-198 

==Attachment:==

N Rev: A Page 2 of 2}}