Text

Attachment 2 - Heat Transfer Calculations Used to Develop Attachment 5 and Table A5-1 in the July 12, 2012, License Amendment Request
	ML12269A019
Person / Time
Site:	LaSalle
Issue date:	09/17/2012
From:	; Exelon Generation Co
To:	; Office of Nuclear Reactor Regulation
References
	RS-12-154
	Download: ML12269A019 (625)
	v • d • e

ATTACHMENT 2 Heat transfer calculations used to develop Attachment 5 and Table A5-1 in the July 12, 2012, License Amendment Request Component EPN Noun Name Design Analysis 1(2)E12-BO01A/B RHR Heat Exchanger 97-201, Rev. A02 ODG01A 0 DG Jacket Water Cooler 97-195, Rev. A01 1(2)DG01A A DG Jacket Water Cooler 97-195, Rev. A01 1 (2)E22-SO01 B DG Jacket Water Cooler 97-197, Rev. A04 1(2)VY01A NW ECCS (A RHR) Pump Cubicle Cooler 97-200, Rev. A05 1(2)VY02A SW ECCS (HPCS) Pump Cubicle Cooler 97-200, Rev. A05 1(2)VY03A SE ECCS (B/C RHR) Pump Cubicle Cooler 97-199, Rev. B03 1(2)VY04A NE ECCS (LPCS/RCIC)

Pump Cubicle Cooler 97-198, Rev. A03 CC-AA-309-1001 Revision 6 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page 1 Design Analysis (Minor Revision)

Last Page No. 1 Attachment B, B2 Analysis No.:'97-201 Revision:

2 A02 Title: 3 Thermal Model of ComEd/LSCS RHR Heat Exchangers 1(2)RH01A

& B EC/ECR No.: ' 388666 Revision:

000 Station(s):

LaSalle Unit No.: 8 01 &02 SafetylQA Class: 1 SR System Code(s): ,6 E12, RH Is this Design Analysis Safeguards Information?" Yes [] No 0 If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?

12 Yes F1 No 0 If yes, ATI/AR#: N/A This Design Analysis SUPERCEDES:

,3 N/A in its entirety.Description of Changes (list affected pages): 4 This revision evaluates a maximum cooling water inlet temperature of 107 OF for the RHR heat exchangers.

The previous temperature that was evaluated was 104 OF. Affected pages are Pages 1-3, Attachment A, Pages A1-A2, and Attachment B, Pages B1-B2.Disposition of Changes: ,5 See attached pages. The changes made are acceptable.

Preparer:

16 Sean Tanton L 4 J L Print Name Sign Name ate Method of Review: '7 Detailed Review Z Alternate Calculations fl Testing [I Reviewer:

8 Steve Chon (3,. cl>.... 6///Z..Print Name Sign Name Date Review Independent review 0 Peer review [I Notes: " (For External Anaiyses Only)External Approver:

20 N/A Print Name Sign Name Date Exelon Reviewer 21 N/A Print Name Sign Name Date Exelon Approver: " SW4V CJM/7- ___V__ 6/_,A-_h Print Name V Sign Name Date 97-201 Rev. A02 Page 2 of 3 Purpose: The purpose of this revision is to determine the amount of heat that can be removed via the 1 (2)E1 2-BO01 A/B heat exchangers for the containment cooling mode (CCM) and to verify that the heat exchangers can remove the design heat load of 41.6 MBTU/hr for the shutdown cooling (SDC) mode with a revised maximum cooling water temperature of 107 OF. The revised design heat load to be used for GL 89-13 surveillance testing will also be determined with this revision.Assumptions:

There are no assumptions for this revision.Inputs:* Cooling water temperature

= 107 OF (Reference 2)* Cooling water flow rate = 7400 gpm (Reference 1)* RHR System water temperature during CCM = 212 OF (Reference 1)* RHR System water temperature during SDC = 120 OF (Reference 1)* RHR System flow rate through 1(2)E1 2-B001 A/B = 7200 gpm (Reference 1)* Fouling factor for 1(2)E12-B001A/B

= 0.00185 hr-ft 2.°F/BTU (Reference 1)* 53 tubes plugged (5% tube plugging) (Reference 1)* RHR Heat Exchanger K factor = 438 (Reference 2)

References:

1. Design analysis97-201, Rev. A, up to and including Rev A01 2. EC 388666, Rev. 000 3. L-00071 1, Rev. 004D (See EC 388666)4. EC 382267, Rev. 000 5. L-002857, Rev. 001 (See EC 388666)6. L-003352, Rev. OOOA (See EC 388666)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 EX00001 03.Method of Analysis I Numeric Analysis: As stated in Reference 2, to maintain peak suppression pool temperatures at or below their current analyzed values, the RHR heat exchanger K factor is required to be raised from 417 to 438. This number is used as an input for various analyses.

The RHR Heat Exchanger K factor [Btu/sec, 0 F] is determined as follows: K= Q (Tsp -Tsw ) x 3600 Where: Q = heat load (Btu/hr)Tsp = Suppression Pool Temperature (OF)Tsw= Cooling Water Temperature (OF)3600 = Conversion from hours to seconds Using this equation, the credited K factor can be used to determine the design heat load to be removed. Using a K factor of 438, a bounding suppression pool temperature of 212 OF, and a cooling water temperature of 107 °F, the design heat load becomes 165,564,000 Btu/hr. Note that Reference 5 performs a sensitivity study of the K factor based on various suppression pool temperatures.

It demonstrates that 438 is the appropriate K factor even with varying suppression pool temperatures.

Reference 6 shows a peak suppression pool temperature of 197 OF, which would equate to a design heat load lower than that which was calculated with 212 OF. Because 165,564,000 Btu/hr is bounding, it will be used as the acceptance criteria.To determine the amount of heat that could be transferred with a cooling water temperature of 107 OF, the existing heat exchanger model will be revised by changing the input of the 'Tube Inlet Temp" from 104 OF to 107 OF for containment cooling mode.97-201 Rev. A02 Page 3 of 3 To achieve the required heat transfer rates a change in fouling factor from 0.00185 hr.ft 2.-F/BTU to 0.00147 hr.-f.OF/BTU was necessary.

A review of trend data from previous RHR heat exchanger thermal performance evaluations was performed.

The most recent thermal performance test data shows a worst case fouling factor of 0.000410 hr-ft 2.F/BTU (Ref. 4), which is well below the new fouling factor of 0.00147 hr-ft 2.°F/BTU. The thermal performance testing prior to that shows small changes between each test. The heat exchangers are also cleaned regularly to maintain a very low actual fouling factor. The new fouling factor of 0.00147 hr-fte-°F/BTU has been accepted by the GL 89-13 program manager.Results I

Conclusions:

The RHR Heat Exchangers can remove the revised design heat load of 165,564,000 Btu/hr with the following CCM conditions:

107 OF cooling water temperature

7400 gpm cooling water flow* fouling factor of 0.00147 hrft 2 e-F/BTU* 53 tubes plugged* RHR process temperature of 212 OF (CCM)* RHR process flow of 7200 gpm The total heat removed at these conditions is 166,468,480 BTU/hr, which provides 0.5% thermal margin over the design heat load. The model benchmark was shown to conservatively underestimate the heat transfer of the cooler by 1.31% for CCM. Therefore, any positive margin shown in the model would be an underestimate of actual thermal performance, which would show more margin than what is calculated.

The previous maximum fouling factor of 0.00185 hr.ft 2.OF/BTU has been revised to 0.00147 hr.ft 2.°F/BTU. This case is shown in Attachment A.The RHA Heat Exchangers can remove the design heat load of 41.6 MBTU/hr with the following SDC conditions:

107 OF cooling water temperature

7400 gpm cooling water flow* fouling factor of 0.00147 hr.ft 2.OF/BTU* 53 tubes plugged* RHR process temperature of 121 OF (SD0) (see below)* RHR process flow of 7200 gpm The total heat removed at the above listed conditions is 21,770,576 BTU/hr per heat exchanger, which equates to a total of 43,541,152 BTU/hr for two heat exchangers.

The operation of 2 heat exchangers for SDC mode is acceptable as it is a non-safety related function of RHR. Operation of two heat exchangers provides 4.7%thermal margin over the design heat load. The model benchmark was shown to conservatively underestimate the heat transfer of the cooler by 0.31% for the SDC mode. Therefore, any positive margin shown in the model would be an underestimate of actual thermal performance, which would show more margin than what is calculated.

Note that the previous process temperature used for the SDC case was 120 OF. Because SDC mode is non-safety related, the basis for the number is outage productivity.

This temperature is used to maintain comfortable conditions during refueling outages. Additionally, the change to 121 OF is a change of 0.83% and is considered to be essentially the same. The RHR pumps and seals are rated for a much higher temperature than this (250 OF, Refs. 2 & 3). Because this is considered to be essentially the same, 120 'F should be used for future evaluations of the RHR heat exchangers for the SDC mode. Just as was done for the CCM mode, the previous maximum fouling factor of 0.00185 hrft 2.F/BTU has been revised to 0.00147 hrft.OF/BTU.

This case is shown in Attachment B The acceptance criteria to be used in GL 89-13 thermal performance testing is a fouling factor of 0.00147 hrft 2.F/BTU and a total heat removal of 165,564,000 BTU/hr for CCM. The heat removal of 41.6 MBTU/hr for 4ft SDC remains the same.Attachments:

A. CCM Data Report for 1(2)E12-B001A/B (2 pgs)B. SDC Data Report for 1(2)E12-B001A/B (2 pgs) uj-IJ-ZU12 I/: PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-1002)

Commonwealth Edison Data Report for E12-BOO1 -LSCS -RHR Hx.CCM -tube side = 107 OF, 7400 gpm, shell side = 212 OF, 7200 gpm, 53 tubes plugged, FF = 0.00147 Shell and Tube Heat Exchanger Input Parameters II Shell-Side Tube-Side Fluid Quantity, Total gpm 7,446.28 7,396.31 Mass Fluid Quantity, Total Ibm/hr 0.00 0.00 Inlet Temperature OF 120.00 90.00 Outlet Temperature OF 108.80 101.25 Fouling Factor hr.fl 2-°F/BTU 0.00250 0.00000 Shell Fluid Name Tube Fluid Name Design Q (BTU/hr)Design U (BTU/hr'ft 2-"F)Outside h Factor (Hoff)Fixed U (BTU/hr'ft 2-°F)Fixed Area (Wt 2)Performance Factor (% Reduction)

Heat Exchanger Type Total Effective Area per Unit (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 (It)Tube Inside Diameter (in)Tube Outside Diameter (in)Tube Wall K (BTU/hr-ftP'F)

Lbc, Central Baffle Spacing (in)Lbi, Inlet Baffle Spacing (in)Lbo, Outlet Baffle Spacing (in)Doti, Tube Circle Diameter Bh, Baffle Cut Height (in)Ds, Shell Inside Diamter (in)Lsb, Diametral difference between Baffle and Shell (in)Ltb, Diametral difference between Tube and Baffle (in)Nss, Number Sealing Strips Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0 0.00 0.00 TEMA -E 11,500.00 0.996344561 0.00000 1 4.880000000 3.400 1.0000 Triangular 2 Yes 1,063 1,010 55.30 0.652 0.750 9.40 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 97-201 Revision A02 Attachment A Page Al of A2 05-15-2012 17:18:26 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-1002)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -tube side = 107 IF, 7400 gpm, shell side = 212 IF, 7200 gpm, 53 tubes plugged, FF = 0.00147 Page 1 Calculation Soecifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User 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 (oF)Shell Inlet Temp (IF)Input Fouling Factor 7,344.00 6,905.00 107.00 212.00 0.001470 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr.It 2-.F)Tube Mass Flow (lbm/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 0.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 (oF)Prandtl Number Tav Shell (IF)Bulk Vise (lbm/ft-hr)

Shell Skin Temp (IF)Skin Visc (lbm/flthr)

Tube Temp In (IF)Density (lbm/ft')

Tube Temp Out (IF)Cp (BTU/Ibm.°F)

Tav Tube (IF)K (BTU/hr.ft.°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 (fW 2)Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Vise (lbm/fihr)

Skin Vise (lbm/ft-hr)

Density (Ibm/ft)Cp (BTU/Ibm.0 F)K (BTU/hr-ft 0.F)Shell-Side 3.26 55,935 2.0490 0.7909 0.8775 60.3957 1.0032 0.3872 3,454,223.04 3,673,832.59 166,468,480.24 58.3 10,926.6 Tube-Side 7.08 69,169 3.2991 1.2323 1.1347 61.5557 0.9990 0.3732 Overall Fouling (hr~ft 2.°F/BTU)Shell-Side ho (BTU/hr.ft 2 0.F)Tube-Side hi (BTU/hr-ft 2-°F)I/Wall Resis (BTU/hr.ft 2-.F)LMTD Correction Factor U Overall (BTU/hr.ft 2-.F)Shell Temp In ('F)Shell Temp Out (IF)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (°F)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)0.001470 1,128.7 2,079.4 2,148.1 0.8820 296.3 212.0 164.0 188.0 172.7 107.0 152.4 129.7 139.2** Reynolds Number Outside Range of Equation Applicability

!! With Zero Fouling The Test Heat Load Could Not Be Achieved 97-201 Revision A02 Attachment A Page A2 of A2 05-18-201 2 07:17:52 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-1002)

Commonwealth Edison Data Report for E12-BOOI -LSCS -RHR Hx.SDC -tube side = 107 OF, 7400 gpm, shell side = 121 OF, 7200 gpm, 53 tubes plugged, FF = 0.00 147 Shell and Tube Heat Exchanger Input Parameters Shell-Side Tube-Side Fluid Quantity, Total gpm 7,446.28 7,396.31 Mass Fluid Quantity, Total Ibm/hr 0.00 0.00 Inlet Temperature OF 120.00 90.00 Outlet Temperature OF 108.80 101.25 Fouling Factor hr.ft 2.°F/BTU 0.00250 0.00000 Shell Fluid Name Tube Fluid Name Design Q (BTU/hr)Design U (BTU/hr'ft 2 -F)Outside h Factor (Hoff)Fixed U (BTU/hr'ft 2'-F)Fixed Area (ft 2)Performance Factor (% Reduction)

Heat Exchanger Type Total Effective Area per Unit (ft 2)Area Factor Area Ratio Number of Shells Per Unit Shell Minimum Area Shell Velocity (tf/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 K (BTU/hr'ft.°F)

Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0 0.00 0.00 TEMA -E 11,500.00 0.996344561 0.00000 1 4.880000000 3.400 1.0000 Triangular 2 Yes 1,063 1,010 55.30 0.652 0.750 9.40 Lbc, Central Baffle Spacing (in)Lbi, Inlet Baffle Spacing (in)Lbo, Outlet Baffle Spacing (in)Doti, Tube Circle Diameter Bh, Baffle Cut Height (in)Ds, Shell Inside Diamter (in)Lsb, Diametral difference between Baffle and Shell (in)Ltb, Diametral difference between Tube and Baffle (in)Nss, Number Sealing Strips 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 97-201 Revision A02 Attachment B Page B1 of B2 05-18-2012 07:17:52 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-1002)

Commonwealth Edison Calculation Report for E 12-BOOI -LSCS -RHR Hx.Page 1 SDC -tube side = 107 IF, 7400 gpm, shell side = 121 IF, 7200 gpm, 53 tubes plugged, FF = 0.00147 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,344.00 Shell Flow (gpm) Shell Flow (gpm) 7,122.00 Shell Temp In (IF) Tube Inlet Temp (IF) 107.00 Shell Temp Out (IF) Shell Inlet Temp (IF) 121.00 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF) Input Fouling Factor 0.001470 Foulin Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr.ft2.°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 z.F)LMTD LMTD Correction Factor Effective Area (f1 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 (IF)Prandtl Number Tav Shell (OF)Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (OF)Skin Visc (Ibm/ft hr) Tube Temp In (IF)Density (Ibm/if')

Tube Temp Out ('F)Cp (BTU/Ibm.°F)

Tav Tube (IF)K (BTU/hr'ft' 0 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 (fW 2)Property Shell-Side Velocity (ft/s) 3.28 Reynold's Number 33,234 Prandtl Number 3.7131 Bulk Visc (Ibm/ft-hr) 1.3730 Skin Visc (Ibm/ft hr) 1.4037 Density (Ibm/ft-)

61.7433 Cp (BTU/Ibm.°F) 0.9988 K (BTU/hr'-.t°F) 0.3693 3,562,777.19 3,673,832.59 21,770,576.54 8.0 10,926.6 Tube-Side 7.04 57,419 4.0454 1.4845 1.4643 61.8605 0.9988 0.3665 Overall Fouling (hr-ft 2-°F/BTU)Shell-Side ho (BTU/hr-ft 2.F)Tube-Side hi (BTU/hr-ft 2 0'F)1/Wall Resis (BTU/hr-fi 2.°F)LMTD Correction Factor U Overall (BTU/hr-ft2.

F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)0.001470 965.4 1,865.5 2,148.1 0.8965 278.7 121.0 114.9 117.9 115.6 107.0 112.9 110.0 111.3** Reynolds Number Outside Range of Equation Applicability With Zero Fouling The Test Heat Load Could Not Be Achieved 97-201 Revision A02 Attachment B Page B2 of B2 CC-AA-309-1001 Revision 1 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page I of I Last Page No. 1 Analysis No.97-201 Revision AO1 ECIECR No. EC 352363 Revision 0 Title: Thermal Model of ComEd/LSCS RHR Heat Exchangers 1(2)RHROIA

& B Station(s)

LaSalle Is this Design Analysis Safeguards?

Yes Q] No 0 Unit No.: Units 1 and 2 Does this Design Analysis Contain Unverified Assumptions?

Yes C0 No 0 Safety Class Safety Related System Code E12, RH ATI/AR#Description of Change This revision clarifies that the required heat removal capability of an RHR HX for the Containment Cooling Mode is now 1631 MBtulhr with an RHR service water inlet temperature of 104 deg. F, a maximum fouling factor of 0.00185 hr-ftA2-deg F/Btu, and a 5% tube plugging allowance (ref. Case 3 on page 7 of rev. AO0 of this calculation).

This heat removal value is to be used as the acceptance criteria in RHR HX thermal performance evaluations.

Based on Calculation L-002826 rev. 0, SIL 636 Disposition for LaSalle County Station and New Decay Heat Table, and General Electric Power Uprate Project Task Report 310: Residual Heat Removal System, GE-NE-A1300384-12-01 rev. 0, no change to the Shutdown Cooling Condition (SDC) design heat load acceptance criteria of 41.6 Mbtu/hr is required.Disposition of Changes (include additional pages as required)EC 334017 (dated 5-16-02) evaluated the increased cooling water temperature to a new maximum temperature of 104 deg-F. The Design Considerations Summary states in part for the Post LOCA Suppression Pool Temperature Analysis: "Design Analysis No. L-002857, Rev. 0 has been completed to determine the RHR heat exchanger efficiency (expressed as a "K" factor in LaSalle's existing Containment Analysis...)

with an increased inlet service water temperature of 104°F at various suppression pool temperatures.

After the heat exchanger K factor had been determined, the impact on the LaSalle suppression pool temperature response following a LOCA was evaluated.

As detailed within this design analysis, the post LOCA peak suppression pool temperature (193 deg-F) has not increased even with a higher inlet service water temperature of 104°F. The peak suppression pool temperature demonstrated within this design analysis is still well below the suppression pool temperature NPSH limit for the ECCS pumps of 212°F." The increased efficiency implies a higher heat load capability.

Based on a review of L-002857: -the credited heat rejection capability is 163.1 MBtu/hr for the CCM case (Table 2 value for Q2). This is the value of Q used to get a 'K factor' of 417. Since we are crediting this heat load capability and this value is higher than 155 Mbtu/hr, this value should be used as the approved acceptance criteria.Preparer Dan Schmit 11/11/04 Print Name Sign Name Date Reviewer Terry Martin -, ý __ -6 (ýY(0 Print Name Sign Name Date Method of Review 0 Detailed Review El Alternate Calcu at~ons El Testing Review Notes: Approver 9- 'CK ____________

___Print Name Sign Name Date (For External Analyses Only)Exelon Reviewer NA Print Name Sign Name Date Approver NA Print Name Sign Name Date CC-AA-309

-ATTACHMENT I -Design Analysis Approval Page I of 2 DESIGN ANALYSIS NO.: Calc. # 97-201 PAGE NO. I Major REV Number:. A Minor Rev Number: 00[ BRAIDWOOD STATION BYRON STATION DESCRIPTION

..,,n(Co18)

Mil[ I CLINTON STATION[ J DRESDEN STATION IX] LASALLE CO. STATION DISCIPLINE CODE: (Coll) M[ I QUAD CITIES STATION Unit:[ 10 [XIl [X12 [ 13 SYSTEM CODE: (COI1) E12, RH TITLE: THERMAL MODEL OF COMEDILSCS RHR Heat Exchangers 1(2)RHROIA

& B.[X ] Safety Related ] Augmented Quality [ ] Non-Safety Related_________ATTRIBUTES (C016)TYPE VALUE TYPE VALUE Elevation 710'Software Proto-HX COMPONENT EPN: (COl4 Panel) DOCUMENT NUMBERS: (C012 Panel) (Design Analyses References)

EPN TYPE ypelSub Document Number Input (YIN)1E12-BOOIA H15 ____CP EC# 334017. Y 1E12-B001B H15 /2E12-B001A H15 /2E12-BOOIB H15 /RI REMARKS: NA E-Form CC-AA-309-1 v1.1 for use with CC-AA-309 Revision I and above.

CC-AA-309

-ATTACHMENT I -Design Analysis Approval Page 2 of 2 DESIGN ANALYSIS NO.97-201 REV: AO0 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 RHR Heat Exchanger thermal margins for different fouling factors and 5% tubes plugged at Containment Cooling and Shutdown Cooling conditions.

Electronic Calculation Data Flies: ProtoHX 3.02, e12-b001.phx, 160 KB, 04/19/2002.10:36am (Program Name, Version, File Name extensionisize/date/hour/min)

Design impact review completed? ( ]Yes I X I NA, Per EC#: 334017 (If yes. attach Impacl review sheet)Prepared by: Jeff W. VanStrien

.1 /Reviewed by: Buran L Davenwort 71 1 P*ý'T SirnOM MX I Detailed ( ]Altemate

[ ] Test This esaAnlsssiwew:.....initsen eXWml R#"n Anbaf Reviiew (Attachment 3 Attached)Review,,d by:/Pett SOgn Dote Approved by: ,*I .-pf" sign Date Do any ASSUMPMrONS

/ EMlOEERWM JUGEMENTS .qmMe1w

[ ]Y Y [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 Cor d Effective Date: 04/14/00 CALCULATION TABLE OF CONTENTS CALCULATION NO.97-201 REV. NO. AOO 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

5 6.0 CALCULATIONS 6 7.0

SUMMARY

AND CONCLUSIONS 8 8.0 ATTACHMENTS:

8 Attachment "A" -Proto-Hx Caic. Report for RHR Hx during CCM & SDC Al to A5 (CSCS=104 F @ Design FF, 5% plugged)Attachment "B" -Proto-Hx Calc. Report for RHR Hx during CCM & SDC B1 to B5 (CSCS=104 F @ 2X As-Tested FF)Attachment "C" -Proto-Hx Calc. Report for RHR Hx during CCM & SDC Cl to C5 (CSCS=104 F @ 2X As-Tested FF, 5% plugged)Attachment "D" -Proto-Hx CaIc. Report for RHR Hx during CCM & SDC D1 to D5 (CSCS=104 F @ Max. Allowable FF, w\ 5% plugged)i a I E-FORM I C =OSEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE I CALCULATION NO.97-201 REV. NO. AOO PAGE NO. 4 of 8 1.0 PURPOSE/OBJECTIVE The purpose of this minor revision is to revise the thermal model of this heat exchanger for a 1041F Service Water inlet temperature.

This assessment will evaluate the adequacy of the RHR Heat Exchangers at both Containment Cooling Mode (CCM) and Shutdown Cooling Conditions (SDC)during a maximum allowable inlet service water temperature of 104OF to ensure that adequate thermal margin still exists.2.0 METHODOLOGY AND ACCEPTANCE CRITERIA The existing heat exchanger model will be revised by changing the input of the "Tube Inlet Temp." to 104OF and simulated for the following conditions: (Case 1) design fouling factor with 5% of the tubes plugged, (Case 2) twice the 'as-tested' fouling factor and (Case 3) twice the 'as-tested' fouling factor with a 5% tube plugging allowance.

The acceptance criteria will be for the thermal margin at Case 3 stated conditions to exceed the LaSalle Design Heat Load of 155,000,000 BTU/hr for Containment Cooling Mode (CCM) and 41,600,000 BTU/hr in Shutdown Cooling Condition (SDC) (Ref. 1, Tables 3-1 & 3-2). If desired, both RHR heat exchangers may be placed in service to provide the maximum cool down rate specified above during the Shutdown Cooling Condition.

Additional conservatism was built into this acceptance criteria by assuming a 5% uncertainty in the Proto-HX heat transfer calculations.

The Reference 1 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 loads can be accommodated including heat transfer model uncertainty.

3.0 ASSUMPTIONS I ENGINEERING JUDGMENTS The assumptions indicated in section 5.0 of Reference 1 are still valid.Note: The shell side flow rate specified within reference 1 (8,400 gpm) has been changed to a more conservative number given within Tech. Spec. S.R. 3.5.1.5 as a minimum flow rate of 7,200 gpm. This flow rate was further reduced to account for volumetric flow rate correction required by Proto-Hx software limitations, refer to Table 1.4.0 DESIGN INPUTS The design inputs consist of References 1, 2 and 4 listed below.I E -FORM I Coirel NES-G-14.02 Effective Date: 04/14/00 I CALCULATION NO.97-201 CALCULATION PAGE REV. NO. AOO PAGE NO. 5 of 8

5.0 REFERENCES

1. Calculation No.97-201, Rev. A, "Thermal Model of COMED/LSCS RHR Heat Exchangers 1(2)RHR01A

& B" 2. NDIT LS-1 154, Upgrade 0, "lB RHR Heat Exchanger Test on 10-25-99 Evaluation" and Calculation L-002571, Rev. 0, "IA RHR Heat Exchanger Test performed on 01/10/02".

3. EC# 331912, "Assessment of High Lake Temperature Upon the Functionality of the Plant" 4. Crane Co. Technical Paper No. 410 "Flow of Fluids", Twenty-Fifth Printing -1991.5. "Standards of the Tubular Exchanger Manufacturers Association" (TEMA), Seventh Edition, 1988.II E-FORM Corn-d NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE I CALCULATION NO.97-201 REV. NO. AOO PAGE NO. 6 of 8 6.0 CALCULATIONS The current calculation model is based on a Service Water inlet temperature of 90OF (SDC) and 100 0 F (CCM). At these temperatures, a design fouling factor of 0.0025 hr*ft 2*OF/BTU and a 5%tube plugging allowance, the amount of heat transferred is 163,700,000 BTU/hr compared with a LaSalle Station Containment Cooling Design Heat Load of 155,000,000 BTU/hr for a 5.61%thermal margin. For Shutdown Cooling, the design case temperature, the same fouling factor and tube plugging results in a 41,310,000 BTU/hr heat transfer compared to a Shutdown Cooling Reference Load of 41,600,000 BTU/hr which appears to indicate no thermal margin available (Ref.1, Tables 6-3 & 6-4).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: ThermaiM arg in x 100% = %Thermal arg in Re quiredHeatLoad

[Equation 2]As detailed in reference 1 Proto-Hx inputs for fluid flow rates need to be adjusted using the ratio of the actual water density and the density of water at 60OF (assumed by Proto-Hx software).

The following formula is used for this adjustment and the calculation inputs are tabulated with Table 1.Qphx = Qtemp * ( Density @temp / Density @ 60 F )[Equation 31 Table 1: Reference Conditions, Proto-Hx Flow Rate Inputs Parameter Density (Ib/ft 3) Ref. 4 Actual Flow (gpm) Proto-Hx Input (gpm)Tube Side, 104 F 61.93 7,400 7,348 Shell-side, 120 F 61.71 7,200 7,124 Shell-side, 212 F 59.81 Proto-Hx, 60 F I 62.37 I E-FORM I NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO.97-201 REV. NO. AOO PAGE NO. 7 of 8 Case 1 When the service water inlet temperature is increased to 104OF for the same design fouling factor and 5% tube plugging allowance, the amount of heat transferred decreases to 150,800,000 BTU/hr, which appears to have no thermal margin at this elevated temperature and fouling condition for the Containment Cooling required heat load of 155,000,000 BTU/hr. With the RHR system operating in Shutdown Cooling conditions at 104OF service water inlet, design fouling factor, and 5% tube plugging allowance, 21,920,000 BTU/hr is transferred which is below the required heat removal of 41,600,000 BTU/hr and would necessitate the operation of the second RHR heat exchanger thereby providing an ample cooling capacity of 43,840,000 BTU/hr, resulting in a thermal margin of 5.4% (w\ 2 RHR Hx in service) [Attachment A].Case 2 Regular cleaning and testing of these heat exchangers limits the amount of fouling well below the values assumed above. The heat exchanger performance data taken under the G.L. 89-13 program here at LaSalle demonstrates a maximum measured fouling factor of 0.00065 hr*ft 2*OF/BTU (Ref. 2). For conservatism, this value was doubled to 0.0013 hr*ft 2*OF/BTU and simulated with 104OF service water inlet temperature.

The result was a heat transfer rate of 177,900,000 BTU/hr for a thermal margin of 14.8% [Attachment B]. Likewise for Shutdown Cooling condition at this fouling factor and service water condition the resulting heat transfer rate is 25,870,000 BTU/hr. This still necessitates the use of two heat exchangers to remove the design SDC heat load of 41,600,000 BTU/hr. However with two RHR heat exchangers in service the resulting thermal margin is 24.4% [Attachment B].Case 3 With additional conservatism included by adding a plugging allowance of 53 tubes, 5% of the total, in the heat exchanger and running the model again at the above fouling factor and inlet temperature for a 174,800,000 BTU/hr heat transfer rate, a 12.8% thermal margin above the 155,000,000 BTU/hr Design Containment Cooling Heat Load. As with the previous cases, Shutdown Cooling would require two RHR heat exchangers at 0.0013 hr*ft'*OF/BTU, 104OF inlet temperature and 5% tube plugging allowance.

However with 2 heat exchangers in service the resulting heat transfer rate is 50,780,000 BTU/hr (25,390,000 BTU/hr per Hx), resulting in a thermal margin of 22.1% [Attachment C].The maximum fouling factor was found to be 0.00185 hr*ft 2while maintaining the required heat transfer rate at 104OF inlet temperature and with a 5% plugging allowance

[Attachment D].The resulting heat transfer of 163,100,000 BTU/hr for CCM and 47,380,000 BTU/hr for SDC (w\2 RHR Hx in service) accommodates the design heat loads of 155,000,000 BTU/hr for CCM and 41,600,000 BTU/hr for SDC including analytical model uncertainty.

E-FORM I CornEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO.97-201 REV. NO. AOO PAGE NO. 8 of 8 This is judged to be a reasonably conservative fouling factor even though it is slightly lower than the typical fouling factor stated in Ref. 5, page 215. The LaSalle lake water quality exceeds the"River Water Fouling Factor" (at a velocity greater than 3 ft/sec) given in this reference.

The lake water passes through strainers and is chemically treated to control silt and scale prevention.

7.0

SUMMARY

AND CONCLUSIONS The RHR Heat Exchanger Model has been updated to reflect a maximum lake temperature of 104°F. The model found adequate thermal margin when operated for Containment Cooling Mode and would require two heat exchangers in operation to achieve the Design Heat Rate removal during Shutdown Cooling Mode. The maximum fouling factor was found to be 0.00185 hrkft 2*OF/BTU while maintaining the required heat transfer rate at 104 0 F inlet temperature and with a 5% plugging allowance.

This fouling factor has been determined to be an acceptable benchmark value that can be used in Generic Letter 89-13 testing evaluations of this model heat exchanger.

8.0 ATTACHMENTS

Attachment "A" -Proto-Hx Calc. Report for RHR Hx during CCM & SDC (CSCS=104 F @ Design FF, 5% plugged)Attachment "B" -Proto-Hx Calc. Report for RHR Hx during CCM & SDC (CSCS=1 04 F @ 2X As-Tested FF)Attachment "C" -Proto-Hx Calc. Report for RHR Hx during CCM & SDC (CSCS=104 F @ 2X As-Tested FF, 5% plugged)Attachment "D" -Proto-Hx Calc. Report for RHR Hx during CCM & SDC (CSCS=104 F @ Max. Allowable FF, w\ 5% plugged)Final Page (Last Page)II E-FORM I CeorEd CALCULATION NO.97-201 REVISION NO. AOO PAGE NO. Al of A5 Attachment "A" Proto-Hx Calc. Report for RHR Hx during CCM & SDC (CSCS=104 F @ Design FF, 5% plugged)I E-FORM I 16:54:44 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-B001 -LSCS -RHR Hx.CCM-5% PLUG. DESIGN FF a, 104 F 04/15/02 Shell and Tube Heat Exchanger Input Parameters Shell-Side Tube-Side Fluid Quantity, Total gpm 7,446.28 7,396.31 Inlet Temperature OF 120.00 90.00 Outlet Temperature OF 108.80 101.25 Fouling Factor 0.00250 0.00000 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)

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 Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 TEMA-E 11,500.00 0.996344561 1 4.880000000 3.400 1.0000 Triangular C('4j)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.°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 Yes 1,063 1,010 55.30 0.652 0.750 9.40 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Calculation No.97-201 Revision No. AOO Attachment A Page No. $: of A_£__

16:54:44 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM-5% PLUG. DESIGN FF (6. 104 F 04/15/02 Calculation Specifications II I1 Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used e~kfg ;Test Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (IF)Tube Temv Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)7,348.0 6,905.0 104.0 212.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2-IF)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.°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 (OF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF) Calculation No.97-201 Bulk Visc (lbm/ft-hr)

Shell Skin Temp (OF) Revision No. AOO Skin Visc (Ibm/ft-hr)

Tube Temp In (OF) Attachment A Density (lbm/ft 3) Tube Temp Out (IF) Page No.Cp (BTU/lbm.'F)

Tav Tube (IF) No. of__.K (BTU/hr-ft 0.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)Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr) z Skin Visc (lbm/fi-hr)

Density (Ibm/fl 3)Cp (BTU/lbm-°F)

K (BTU/hr-ft.°F)

Shell-Side 3.26 5.677E+04 2.02 0.78 0.85 60.34 1.00 0.39 3.454E+6 3.676E+6 1.508E+8 65.7 10,926.6 Tube-Side 7.07 6.607E+04 3.47 1.29 1.20 61.64 1.00 0.37 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr.ft2.OF)

Tube-Side hi (BTU/hr'ft 2.-F)I/Wall Resis (BTU/hrift2.°F)

LMTD Correction Factor U Overall (BTU/hr ft 2-OF)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (OF)0.002500 1,136.9 2,027.7 2,148.1 0.9268 226.6 212.0 168.5 190.2 177.1 104.0 145.1 124.5 133.0** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achiev 16:42:47 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E 12-B001 -LSCS -RHR Hx.SDC-5% PLUG, DESIGN FF (104 F)04/15/02 Shell and Tube Heat Exchanger Input Parameters Shell-Side Tube-Side Fluid Quantity, Total gpm 7,446.28 7,396.31 Inlet Temperature OF 120.00 90.00 CA&Outlet Temperature OF 108.80 101.25 Fouling Factor 0.00250 0.00000 Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/hr)Design Heat Trans Coeff (BTU/hrft 2.F)Emprical Factor for Outside h Performance Factor (% Reduction)

Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 TEMA-E 11,500.00 0.996344561 1 4.880000000 3.400 1.0000 Triangular 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-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 Yes 1,063 1,010 55.30 0.652 0.750 9.40 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Calculation No.97-201 Revision No. AOO Attachment k Page No. A4 of A4s 16:42:47 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-B001 -LSCS -RHR Hx.SDC-5% PLUG, DESIGN FF (104 F)04/15/02 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used JASI I Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,348.0 Shell Flow (gpm) Shell Flow (gpm) 7,124.0 Shell Temp In (IF) Tube Inlet Temp (IF) 104.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 120.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (0 F)Fouling Calculation Results Shell Mass Flow (ibm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr1ft 2 2"F)Tube-Side hi (BTU/hr'ft 2-IF)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"°F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (°F) Calculation No. 97-20 I Bulk Visc (lbm/ftrhr)

Shell Skin Temp (IF) Revision No. AOO Skin Vise (lbm/ft hr) Tube Temp In (IF) Attachment Density (Ibm/1f 3) Tube Temp Out (°F) AttameNt A-Cp (BTU/Ibm.°F)

Tav Tube (IF) Page No. Ar K (BTU/hr'ft 0'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)3.564E+6 3.676E+6 2.192E+7 9.9 10,926.6 Property Shell-Side Tube-Side Velocity (ft/s) 3.29 7.04 Reynold's Number 3.292E+04 5.574E+04 Prandtl Number 3.75 4.18 Bulk Visc (lbm/ft-hr) 1.39 1.53 Skin Visc (Ibm/ft-hr) 1.42 1.51 Density (Ibm/fl 3) 61.76 61.90 Cp (BTU/lbnm°F) 1.00 1.00 K (BTU/hr-ft 0'F) 0.37 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.°F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr1ft 2 2°F)I/Wall Resis (BTU/hr fi2.°F)LMTD Correction Factor U Overall (BTU/hr-ft2.°F)

Shell Tcmp In (IF)Shell Temp Out (IF)Tav Shell (°F)Shell Skin Temp (°F)Tube Temp In (IF)Tube Temp Out (°F)Tav Tube (fF)Tube Skin Temp (°F)215.9 120.0 113.8 116.9 114.7 104.0 110.0 107.0 108.3 0.002500 962.4 1,836.6 2,148.1 0.9348 Corn"I CALCULATION NO.97-201 REVISION NO. AOO PAGE NO. B1 of B5 Attachment "B" Proto-Hx Calc. Report for RHR Hx during CCM & SDC (CSCS=104 F @ 2X As-Tested FF)E-FORM 1 16:57:14 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E 12-BOOI -LSCS -RHR Hx.CCM-ALL TUBES 2X TEST FF (Q 104 F 04/15/02 Shell and Tube Heat Exchanger Input Parameters Shell-Side Tube-Side Fluid Quantity, Total gpm 7,446.28 7,396.31 Inlet Temperature OF 120.00 90.00 Outlet Temperature OF 108.80 101.25 Fouling Factor 0.002504' 0.00000 Ckc -.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)

Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 TEMA-E 11,500.00 0.996344561 Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Number of Shells per Unit Shell Minimum Area Shell Velocity (if'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-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 1 4.880000000 3.400 1.0000 Triangular 2 Yes 1,063 1,=63 55.30 0.652 0.750 9.40 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Calculation No.97-201 Revision No. AOO Attachment 8 Page No. B-. of 0&* Fouling Factor input on next page.

16:57:14 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM-ALL TUBES 2X TEST FF ( 104 F 04/15/02 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,348.0 Shell Flow (gpm) Shell Flow (gpm) 6,905.0 Shell Temp In (IF) Tube Inlet Temp (OF) 104.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 212.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF) Input Fouling Factor 0.001300 .[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.°F)Tube-Side hi (BTU/hr-ft2-°F)

Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr'ft 2.°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 (IF)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (IF) Calculation No.97-201 Bulk Visc (lbm/ft-hr)

Shell Skin Temp (0 F) Revision No. AOO Skin Visc (lbm/ft-hr)

Tube Temp In (°F) Attachment Density (Ibmn/ft')

Tube Temp Out (°F)Cp (BTU/Ibm.°F)

Tav Tube (°F) Page No. of pr K (BTU/hr-ft-0 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 2)3.454E+6 3.676E+6 1.779E+8 58.1 11,500.0 Property Velocity (fl/s)Reynold's Number Prandtl Number.Bulk Visc (lbm/ft-hr)

Skin Visc (Ibm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm'°F)

K (BTU/hr-ftý°F)

Shell-Side 3.25 5.533E+04 2.07 0.80 0.89 60.43 1.00 0.39 Tube-Side 6.73 6.491 E+04 3.35 1.25 1.14 61.58 1.00 0.37 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr ft 2.°F)I/Wall Resis (BTU/hr-ft 2.°F)LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (°F)Shell Skin Temp (IF)Tube Temp In (°F)Tube Temp Out (°F)Tav Tube (°F)Tube Skin Temp (IF)309.1 212.0 160.6 186.3 170.3 104.0 152.5 128.2 138.6 0.001300 1,123.8 1,985.4 2,148.1 0.8618** Reynolds Number Outside Range of Equation Applicability

!1 With Minimum Fouling 'he rest Heat Load Could Not Be 16:47:30 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E1I2-BOO I -LSCS -RHR Hx.SDC-ALL TUBES, 2X TEST FF(a)104 F 04/15/02 Shell and Tube Heat Exchanger Input ParametersI Fluid Quantity, Total 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 2.F)Emprical Factor for Outside h Performance Factor (% Reduction)

Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Shell-Side Tube-Side 7,446.28 7,396.31 120.00 90.00 108.80 101.25 0.002504 0.00000 Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 TEMA-E 11,500.00 0.996344561 Number of Shells per Unit Shell Minimum Area Shell Velocity (f'/s)Tube Pitch (in)Tube Pitch Type 1 4.880000000 3.400 1.0000 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.°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 Yes 1,063 1,063 55.30 0.652 0.750 9.40 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Calculation No. 97-20 1 Revision No. AOO Attachment R Page No. B4 of br* Fouling Factor input on next page.

16:47:30 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-BOO -LSCS -RHR Hx.SDC-ALL TUBES, 2X TEST FF(a,104 F 04/15/02 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions N Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,348.0 Shell Flow (gpm) Shell Flow (gpm) 7,124.0 Shell Temp In (IF) Tube Inlet Temp (IF) 104.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 120.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF) Input Fouling Factor 0.00 1300)'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.°F)Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hrft 2 0.°F)LMTD LMTD Correction Factor Effective Area (fi 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 (°F)Prandtl Number Tav Shell (IF)Bulk Vise (Ibm/ft-hr)

Shell Skin Temp (IF) Calculation No. 97-20 1 Skin Vise (lbm/ft-hr)

Tube Temp In (°F) Revision No. AOO Density (ibm/ft 3) Tube Temp Out (°F) Attachment

__-Cp (BTU/Ibm 0'F) Tav Tube (°F) Page No. _&j of _i 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 (lbm/ft-hr)

Density (Ibm/ft 3)Cp (BTU/Ibm-'F)

K (BTU/hr'ft-'F)

Shell-Side 3.28 3.274E+04 3.78 1.39 1.43 61.77 1.00 0.37 3.564E+6 3.676E+6 2.587E+7 8.8 11,500.0 Tube-Side 6.69 5.325E+04 4.16 1.52 1.50 61.90 1.00 0.37 Overall Fouling (hr-ft 2'0 F/BTU)Shell-Side ho (BTU/hr-ft 2-°F)Tube-Side hi (BTU/hr-ft 2-°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 (IF)Tav Shell (°F)Shell Skin Temp (IF)Tube Temp In (°F)Tube Temp Out (°F)Tar Tube (°F)Tube Skin Temp (OF)0.001300 960.0 1,768.9 2,148.1 0.8794 289.2 120.0 112.7 116.4 113.7 104.0 111,0 107.5 109.2** Reynolds Number Outside Range of Equation Applicability

!I With Minimum Fouling The Test Heat Load Could Not Be Achic'ý CornEd CALCULATION NO.97-201 REVISION NO. AOO PAGE NO. C1 of C5 Attachment "C" Proto-Hx Calc. Report for RHR Hx during CCM & SDC (CSCS= 104 F @ 2X As-Tested FF, 5% plugged)I E-FORM I 16:58:38 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-BOO1 -LSCS -RHR Hx.CCM-5% PLUG, 2X TEST FF @ 104 F 04/15/02 SShell and Tube Heat Exchanger Input Parameters 7 Fluid Quantity, Total 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 2.°F)Emprical Factor for Outside h Performance Factor (% Reduction)

Shell-Side 7,446.28 120.00 108.80 0.00250)Tube-Side 7,396.31 90.00 101.25 0.00000 Fresh Water Fresh Water 41,600,000 215.00 0.563555000 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 11,500.00 0.996344561 1 4.880000000 3.400 1.0000 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-°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 Yes 1,063 1,010 55.30 0.652 0.750 9.40 0.000 0.000.0.000 0.000 0.000 0.000 0.000 0.000 0.000* Fouling Factor input on next page.Calculation No.97-201 Revision No. AOO Attachment C Page No. LZ of C r 16:58:38 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E 12-BOO1 -LSCS -RHR Hx.CCM-5% PLUG, 2X TEST FF Ca 104 F 04/15/02 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions

.Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,348.0 Shell Flow (gpm) Shell Flow (gpm) 6,905.0 Shell Temp In (IF) Tube Inlet Temp (IF) 104.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 212.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (°F) Input Fouling Factor 0.001300,W 1L[_ Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hrTft 2-°F)Tube-Side hi (BTU/hr ft 2 -F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2-°F)LMTD LMTD Correction Factor Effective Area (fW.)Overall Fouling (hr-ft 2 0.F/BTU)Property Shell-Side Tube-Side Velocity (fr/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (°F) Calculation No.97-201 Skin Vise (lbm/ft-hr)

Tube Temp In (IF) Revision No. AOO Density (lbm/ft 3) Tube Temp Out (IF) Attachment e_Cp (BTU/Ibm°0 F) Tav Tube (IF) Page No. o,) of ce S K (BTU/hr'ft-°F)

Tube Skin Temp (°F)IF Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)3.454E+6 3.676E+6 1.748E+8 59.0 10.926.6 Property Velocity (if/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/ft'hr)

Skin Visc (lbm/ftlhr)

Density (lbm/ft 3)Cp (BTU/Ibm 0'F)K (BTU/hr'ft 0'F)Shell-Side 3.25 5.549E+04 2.07 0.80 0.89 60.42 1.00 0.39 Tube-Side 7.08 6.806E+04 3.36 1.25 1.15 61.59 1.00 0.37 Overall Fouling (hr-ft 2"°F/BTU)Shell-Side ho (BTU/hr-ft 2..F)Tube-Side hi (BTU/hr-ft 2.°F)1/Wall Resis (BTU/hr ft 2.°F)LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)Shell Temp In (°F)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (°F)Tube Temp In (°F)Tube Temp Out (°F)Tav Tube (°F)Tube Skin Temp (°F)311.3 212.0 161.5 186.8 170.4 104.0 151.6 127.8 138.0 0.001300 1,124.6 2,063.8 2,148.1 0.8717** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Hleat Load Could Not Be 16:49:37 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC-5% PLUG, 2X TEST FF@ 104 F 04/15/02 Shell and Tube Heat Exchanger Input Parameters I Fluid Quantity, Total 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 2"°F)Emprical Factor for Outside h Performance Factor (% Reduction)

Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Shell-Side Tube-Side 7,446.28 7,396.31 120.00 90.00 108.80 101.25 0.00250) 0.00000 Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 TEMA-E 11,500.00 0.996344561 Number of Shells per Unit Shell Minimum Area Shell Velocity (fl/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 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 1 4.880000000 3.400 1.0000 Triangular 2 Yes 1,063 1,010 55.30 0.652 0.750 9.40 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000* Fouling Factor input on next page.Calculation No.97-201 Revision No. AOO Attachment C_Page No. c4 of cf-16:49:37 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E 12-BOOI -LSCS -RHR Hx.SDC-5% PLUG, 2X TEST FF(a) 104 F 04/15/02 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,348.0 Shell Flow (gpm) Shell Flow (gpm) 7,124.0 Shell Temp In (°F) Tube Inlet Temp (0 F) 104.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 120.0 Tube Flow (gpm)Tube Temp In (0 F)Tube Temp Out (IF) Input Fouling Factor 0.001 300)Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2-°F)Tube Mass Flow (lbmihr) Shell-Side ho (BTU/hrft 2.°F)Tube-Side hi (BTU/hr-ft.°F)-Teat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft2"°F)

LMTD LMTD Correction Factor Effective Area (ftC)Overall Fouling (hrft 2'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 (°F) Calculation No.97-201 Bulk Vise (lbm/ft hr) Shell Skin Temp (IF) Revision No. A00 Skin Visc (lbm/ft-hr)

Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (IF) Attachment c Cp (BTU/Ibm-°F)

Tav Tube (°F) Page No. cs of CS K (BTU/hr-ft-.F)

Tube Skin Temp (IF)S Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)3.564E+6 3.676E+6 2.539E+7 9.0 10,926.6 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ftrhr)

Skin Visc (Ibm/ft-hr)

Density (Ibm/ftl)Cp (BTU/lbm 0'F)K (BTU/hr-ft'°F)

Shell-Side 3.28 3.277E+04 3.77 1.39 1.43 61.77 1.00 0.37 Tube-Side 7.04 5.601 E+04 4.16 1.52 1.50 61.90 1.00 0.37 Overall Fouling (hr-ft 2-0 F/BTU)Shell-Side ho (BTU/hr-ft 2.0 F)Tube-Side hi (BTU/hr-ft 2-OF)1/Wall Resis (BTU/hr ft 2-OF)LMTD Correction Factor U Overall (BTU/hr.ft 2 .F)Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (°F)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp ('IF)291.4 120.0 112.9 116.4 113.7 104.0 110.9 107.5 109.1 0.001300 960.2 1,842.0 2,148.1 0.8882** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be CornEd CALCULATION NO.97-201 REVISION NO. AOO PAGE NO. D1 of D5 Attachment "D" Proto-Hx Calc. Report for RHR Hx during CCM & SDC (CSCS= 104 F @ Max. Allowable FF, w\ 5% plugged)I E-FORM I 17:06:36 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-B001 -LSCS -RHR Hx.CCM-MAX FF, w\5% PLUG, (w, 104 F 04/15/02 IShell and Tube Heat Exchanger Input Parameters I Fluid Quantity, Total 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 2-°F)Emprical Factor for Outside h Performance Factor (% Reduction)

Shell-Side 7,446.28 120.00 108.80 0.0025V Tube-Side 7,396.31 90.00 101.25 0.00000 Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 Heat Exchanger Type Effective Area (ftA2)Area Factor Area Ratio Number of Shells per Unit Shell Minimum Area Shell Velocity (ift/s)Tube Pitch (in)Tube Pitch Type TEMA-E 11,500.00 0.996344561 1 4.880000000 3.400 1.0000 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/hrl-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 Yes 1,063 1,010J 55.30 0.652 0.750 9.40 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000* Fouling Factor input on next page.Calculation No.97-201 Revision No. AOO Attachment 0 Page No. > of D5 17:06:36 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-B001 -LSCS -RHR Hx.CCM-MAX FF, w\5% PLUG, (A 104 F 04/15/02 E Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions x Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,348.0 Shell Flow (gpm) Shell Flow (gpm) 6,905.0 Shell Temp In (IF) Tube Inlet Temp (°F) 104.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 212.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF) Input Fouling Factor 0.001850*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-°F)Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr'fV2-°F)

LMTD LMTD Correction Factor Effective Area (11 2)Overall Fouling (hr-ft 2-°F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (°F) Calculation No.97-201 Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (IF) Revision No. 9 -0 Skin Visc (bm/ft-hr)

Tube Temp In (IF) Revision No. A00 Density (Ibm/ft ) Tube Temp Out (OF) Attachment .l_Cp (BTU/lbm'°F)

Tav Tube (IF) Page No. _J _ _ of p_" K (BTU/hr-ft'°F)

Tube Skin Temp (°F)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 (ibm/ft-hr)

Skin Visc (Ibm/fl-hr)

Density (Ibm/ftl 3)Cp (BTU/lbm-°F)

K (BTU/'hr'ft 0'F)Shell-Side 3.26 5.61 IE+04 2.04 0.79 0.87 60.39 1.00 0.39 3.454E+6 3.676E+6 1.63 1E+8 62.2 10,926.6 Tube-Side 7.08 6.709E+04 3.41 1.27 1.17 61.61 1.00 0.37 Overall Fouling (hrft 2-°'F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2.°F)I/Wall Resis (BTU/hr-ft2.°F)

LMTD Correction Factor U Overall (BTU/hr.ft2-'F)

Shell Temp In (°F)Shell Temp Out (°F)Tav Shell (IF)Shell Skin Temp ("F)Tube Temp In (°F)Tube Temp Out (°F)Tav Tube (OF)Tube Skin Temp (fF)0.001850 1,130.7 2,046.1 2,148.1 0.9024 265.8 212.0 164.9 188.5 173.8 104.0 148.4 126.2 135.5** Reynolds Number Outside Range of Equation Applicability

!! With Minimum Fouling The Test Heat Load Could Not Be AchieV 17:08:18 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-BOOl -LSCS -RHR Hx.SDC-MAX FF,w\5% PLUG (t 104 F 04/15/02 Shell and Tube Heat Exchanger Input Parameters I Fluid Quantity, Total 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 2 0-F)Emprical Factor for Outside h Performance Factor (% Reduction)

Heat Exchanger Type Effective Area (ftA2)Area Factor Area Ratio Shell-Side 7,446.28 120.00 108.80 0.0025W0, Tube-Side 7,396.31 90.00 101.25 0.00000 Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 TEMA-E 11,500.00 0.996344561 1 4.880000000 3.400 1.0000 Triangular 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-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* Fouling Factor input on next page.2 Yes 1,0633 1,010.3 55.30 0.652 0.750 9.40 gE1 r'coz 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Calculation No. 97-20 1 Revision No. AOO Attachment

.Page No. _D4 of 5-17:08:18 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC-MAX FF,w\5% PLUG (a-, 104 F 04/15/02 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions

-0 Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,348.0 Shell Flow (gpm) Shell Flow (gpm) 7,124.0 Shell Temp In (OF) Tube Inlet Temp (IF) 104.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 120.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (,F) Input Fouling Factor 0.001850 4 Fouling Calculation Results Shell Mass Flow (Ibmlhr) U Overall (BTU/hr.ft 2.F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr'ft 2"°F)Tube-Side hi (BTU,'hr-ft'.°F)

Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft2-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 (IF)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (IF) Calculation No.97-201 Skin Visc (lbm/ft-hr)

Tube Temp In (IF) Revision No. AOO Density (lbm/ft')

Tube Temp Out (IF) Attachment 1)Cp (BTU/Ibm 0'F) Tav Tube (IF) Page No. __ 5 of DS K (BTU/hr'ft-'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')3.564E+6 3.676E+6 2.369E+7 9.4 10,926.6 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft'hr)

Skin Visc (lbm/ft-hr)

D.Density (Ibmlft')Cp (BTU/lbm.'F)

K (BTU/hr-ft'°F)

Shell-Side 3.28 3.284E+04 3.76 1.39 1.42 61.76 1.00 0.37 Tube-Side 7.04 5.588E+04 4.17 1.53 1.50 61.90 1.00 0.37 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2-.F)Tube-Side hi (BTU/hr ft 2.°F)I/Wall Resis (BTU/hr ft 2-IF)LMTD Correction Factor U Overall (BTU/hr ft 2 -F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (°F)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)251.2 120.0 113.3 116.7 114.2 104.0 110.5 107.2 108.7 0.001850 961.3 1,839.3 2,148.1 0.9140** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achiec PROTO-POWER CORPORATION CALCULATION TITLE SHEET Commonwealth Edison / LaSalle County Station CLIENT: PROJECT: COMED / LSCS GL 89-13 Program CALCULATION TITLE: CALCULATION NO.: FILE NO.: Thermal Model of COMED / LSCS RHR Heat Exchangers 1(2)RHRO1A

& B.97-201 31-003 COMPUTER CODE & VERSION (if applicable):

PROTO-HXTM Version 3.02 REV TOTAL NO. OF ORIGINATOR/DATE VERIFIER/DATE APPROVAL/DATE PAGES DA.5 Phyfe S. Ings/,8 pot Page i of v Form No.: P1050101 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION c- No. 9-i- REV A PAGE ii v GROTON, CONNECTICUT ORIGINATOR D. Phyfe "lATE 7/16/98 .VERIFIED BY S. Ingalls JOB NO.31-003 CLIENT COMED / LaSalle County Station PROJECT COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers I(2)RHRO1A

& B.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 No.97-201 P.Ev A PAGE iii oV GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 7/16/98 ,.T.RIFIED BY S. Ingalls JOB NO.31-003 CLIENT COMED / LaSalle County Station PPOJECT COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers I(2)RHROIA

& B.CALCULATION VERIFICATION FORM REVIEW METHOD: Approach Checked: Logic Checked: Arithmetic Checked: Alternate Method (Attach Brief Summary)Computer Program Used (Attach Listing)Other*Errors Detected N/A L_N/A [N/A E-N/A N/A N/A EXTENT OF VERIFICATION:

Complete Calculation:

Revised areas only: f]LI Other (describe below): El*Error Resolution

Other Comments-A, m -" elJI(aJ r "~ fl~M 4 rrnCJ C/i{. c~roU*Extra References Used*(Attch extra sheets if needed)CALCULATION FOUND TO BE VALID AND CONCLUSIONS TO BE CORRECT AND REASONABLE:

IDV Signature: / .JJL Initials: 21L Printed Name: Date: 741 Form No.: P1050103 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION N O- 97-201 REV A PAGE iv oP V GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 7/16/98 VERIFIED BY S.. Ingalls JOB NO.31-003 CLIENT COMED / LaSalle County Station PROJECT COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers 1(2)RHROIA

& B.TABLE OF CONTENTS C A L C T IT L E SH E E T .........................................................................................................

i R E V ISIO N H IST O R Y .........................................................................................................

i CALC VERIFICATIO N SH EET ......................................................................................

iii TA BL E O F C O N T E N T S ....................................................................................................

Iv LIST O F A TTA C H M EN TS ................................................................................................

v Total number of pages in Preface of Calc 5 1.0 PURPOSE ...........................................................................................................

1 2.0 BACKGROUND

....................................................................................................

1 3.0 DESIGN INPUTS ....................................................................................................

1 3.1. LASALLE STATION REFERENCE CONDITION

........................................................

2 3.2. CONSTRUCTION D ETAILS ......................................................................................

2 3.3. PERFORM ANCE D ETAILS ......................................................................................

3 3.4. VENDOR DESIGN FOULING FACTOR ......................................................................

5 4.0 APPROACH .......................................................................................................

6 4.1. PROTO-HXTh PARAMETER CALCULATION

..............................

6 4.2. PROTO-HXTM EXTRAPOLATION METHOD ..........................................................

7 4.3. PROTO-HX FLOW RATE INPUTS ...........................................................................

7 5.0 ASSUMPTIONS

..................................................................................................

8 6.0 ANALYSIS .........................................................................................................

9 6.1. PROTO-HX rm M ODEL ........................................................................................

9 6.2. FOULING SENSITIVITY

...........................................................................................

9 6.3. THERMAL PERFORMANCE MARGIN ....................................................................

10

7.0 CONCLUSION

.........................................................................................................

11 7.1. PROTO-HX Tm M ODEL ........................................................................................

11 7.2. FOULING SENSITIVITY

.........................................................................................

12 7.3. THERMAL PERFORMANCE MARGIN ....................................................................

12

8.0 REFERENCES

.........................................................................................................

12 Total number of pages in Body of Calc 12 Form No.: P1050107 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO.97-201 1RL A PAGE V OF v GROTON, CONNECTICUT ORIGITOR D. Phyfe DATE 7/16/98 VERIFIED B" S. Ingalls -oB r1o.31-003 CLIENT COMED / LaSalle County Station PROJECT COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers 1(2)RHRO1A

& B.LIST OF ATTACHMENTS Attachment Subject Matter Total Pages A Proto-Power Calc.97-201, Rev. A; 5 Vendor Data Sheet & Drawings B Proto-Power Calc.97-201, Rev. A; 3 RHR Process Flow Diagram, 731E966AA Sheets 1 & 3 C Proto-Power Caic.97-201, Rev. A; 9 PROTO-HXTm Calculation Reports and Model Data Sheets D Proto-Power Calc.97-201, Rev. A; 11 PROTO-HX Calculation Reports for the Fouling Sensitivity E Proto-Power Calc.97-201, Rev. A; 10 PROTO-HX Calculation Reports for the Margin Analysis F Proto-Power Calc.97-201, Rev. A; 2 PROTO-HX Model of the LaSalle Station RHR Hx.Number of Attachment Pages: Total number of pages: 40 57 Form No.: P1050107 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CA.C No 97-201 REV A PAGE 1 or 12 GROTON, CONNECTICUT D. Phyfe "Ar' 7/16/98_VERIFIEDBY S. Ingalls JOB o.31-003 c COMED / LaSalle County Station PROJECT COMED / LSCS GL 89-13 ProgramThermal Model of COMED / LaSalle Station RHR Heat Exchangers I(2)RHRO1A

& B.1.0 PURPOSE The purpose of this calculation is to develop a thermal performance analysis model for the Commonwealth Edison (ComEd) LaSalle Station, Residual Heat Removal Heat Exchanger.

This model is to be used for the analysis of heat exchanger thermal performance test data as part of the LaSalle Station heat exchanger testing program.Once developed, the model is used to evaluate the thermal margin of the heat exchanger at the LaSalle Station Reference Conditions as currently defined in the LaSalle design and licensing basis.The thermal performance model documented in this calculation has been created and used with PROTO-HX, Version 3.02. The model can be used with previous versions of PROTO-HX and produce identical results as long as the following restrictions are upheld:* Versions prior to version 3.02 will not calculate a negative fouling factor when calculating the fouling factor based on test data.* Shell and tube heat exchangers analyzed in Version 3.0 or earlier must have a tube-side Reynolds Number greater than 10,000 (i.e., fully developed turbulent flow).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:* Water (fresh and salt): 32-500"F 2.0 BACKGROUND LaSalle County Station is in the process of implementing a heat exchanger thermal performance monitoring program in response to the requirements of NRC Generic Letter 89-13 (Reference 8.2). Development of an analytical model in PROTO-HXTM, Version 3.02, will allow -timely analysis of data resulting from the test program.3.0 DESIGN INPUTS The PROTO-HXTM program was developed and validated in accordance with Proto-Power's Nuclear Software Quality Assurance Program (SQAP). This program meets the requirements of 1OCFR50 Appendix B, 1OCFR21, 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-HXTM Version 3.02 was verified and approved for use as documented in Reference 8.11.The design inputs for this calculation consist of the heat exchanger LaSalle Station Reference Condition (Section 3.1), Construction Details (Section 3.2), Performance Details (Section 3.3)provided by the Hx vendor data sheets or design documents as referenced.

Construction details give the necessary information for model construction while performance specifications provided Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION

=c ".97-201 REV A PAGE 2 OF 12 GROTON, CONNECTICUT D. Phyfe /DATE 7/16/98 VERIFIED BY S. Ingalls JOB NO.31-003 COMED/ LaSalle County Station PRoJrcr COMED / LSCS GL 89-13 Program TI TLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers I(2)RHROIA

& B.by the vendor are used to benchmark the models. Section 3.4 discusses the design overall fouling factor used on the vendor data sheets.3.1. LASALLE STATION REFERENCE CONDITION Table 3-1 describes the performance requirement of the RHR heat exchanger during Containment Cooling mode of operation.

Table 3-1 Reference Condition

-Containment Cooling Mode Parameter Value Reference Heat Rate (BTU/hr) 155,000,000 8.1 Shell-Side Flow Rate (gpm) 8400 8.1 Shell-Side Inlet Temperature

('F) 212 8.1 Tube-Side Flow Rate (gpm) 7400 8.1 Tube-Side Inlet Temperature

(*F) 100 8.1 Table 3-2 describes the performance requirement of the RHR heat exchanger during Shutdown Cooling mode of operation.

Table 3-2 Reference Condition

-Shutdown Cooling Mode Parameter Value Reference Heat Rate (BTU/hr) 41,600,000 8.1 Shell-Side Flow Rate (gpm) 7450 8.1 Shell-Side Inlet Temperature

('F) 120 8.1 Tube-Side Flow Rate (gpm) 7400 8.1 Tube-Side Inlet Temperature

('F) 90 8.1 3.2. CONSTRUCTION DETAILS The majority of the construction details stay consistent between both the shutdown cooling and containment cooling modes of operation.

The values that are specific to a mode of operation or number of available tubes in Table 3-3 are based on the shutdown cooling mode with all tubes available.

Table 3-3 Construction Detail Parameter Value Reference Heat Exchanger Type TEMA E / Vertical -AEU 8.6 Total Effective Area per unit (ft 2) 11,500 8.6 Number of Shells per unit 1 8.6 Tube Passes per shell 2 8.6 Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION

--o.97-201 REVA PAGE 3 OF 12 GROTON, CONNECTICUT ORICIPUIATO D. Phyfe /OATE 7/16/98.VERIFIEt BY S. Ingalls JOB ".31-003 CLW COMED / LaSalle County Station prooer COMED / LSCS GL 89-13 Program TITLE 'Thermal Model of COMED / LaSalle Station RHR Heat Exchangers 1(2)RHRO1A

& B.Table 3-3 Construction Detail Parameter Value Reference U-Tubes (yes or no) Yes 8.6 Total Number of Tubes 1063 8.6 Tube Length (ft) 55.3 8.6, See below Tube Inside Diameter (in) 0.652 (18 BWG) 8.6 Tube Outside Diameter (in) 3/4 8.6 Tube Wall Conductivity (BTU/hr-ft-*F) 9.40 (A-249 TP 304L SS) 8.9 (8.6)Tube Pitch (in) I 8.6 Pitch Type Triangle 8.6 Tube Circle Diameter (in) 51.25 8.3 The length of a U-Tube in PROTO-HX T M is twice the straight length of tube plus 30% of the shell diameter (Equation 1). This value is then entered into the PROTO-HXTm data sheet. Based on Reference 8.6 the RHR U-Tube length: U -Tube=2 .L ube+30%'IDshell LTube =50%'26.5ft+25%'27ft+25%'28ft=27ft U -Tube= 2.27ft+0.30-51.25 in it -=55.3 ft 12in Equation 1 3.3. PERFORMANCE DETAILS Table 3-4 shows the performance parameters for the RHR heat exchanger in Containment Cooling mode; whereas, Table 3-5 shows the performance parameters for the RHR heat exchanger in Shutdown Cooling mode. The Shutdown Cooling mode (5% plugged, 53 tubes plugged) performance data was used to create the PROTO-HXTM model.Table 3-4 Containment Cooling Performance Detail Parameter Value Reference Shell Side Fluid Type Demineralized Water (Fresh) 8.6 Shell Side Fouling Factor (Design) 0.0005 8.6 Shell Side Fluid Flow Rate (gpm) 8,400 (4,200,000 lb/hr) 8.6 Shell Side Inlet Temperature

('F) 212.0 8.6 Shell Side Outlet Temperature

('F) All Tubes: 171.6 8.6 5% Plugged: 172 Tube Side Fluid Type Service Water (Fresh) 8.6 Tube Side Fouling Factor (Design) 0.002 8.6 Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CA NO.97-201 REV A PAGE 4 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe /DAT 7/16/98 -VERIFIED BY S. Ingalls JOB No.31-003 ENT COMED / LaSalle County Station pRoJECt COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers I(2)RHROIA

& B.Table 3-4 Containment Cooling Performance Detail Parameter Value Reference Tube Side Fluid Flow Rate (gpm) 7,400 (3.700,000 Ib/hr) 8.6 Tube Side Inlet Temperature

(*F) 100 8.6 Tube Side Outlet Temperature (0 F) All Tubes: 145.9 8.6 5% Plugged: 145.3 Design Q -Service (BTU/hr) All Tubes: 170,000,000 8.6 5% Plugged: 168,000,000 Design U -Clean (BTU/hr-ft 2-°F) All Tubes: 563 8.6 5% Plugged: 568 Design U -Service (BTU/hr-ft 2-°F) All Tubes: 231 8.6 5% Plugged: 235 Shell Velocity (ft/sec) 3.82 8.6 Number of Plugged Tubes All Tubes: 0 8.6 5% Plugged: 53 Table 3-5 Shutdown Cooling Performance Detail Parameter Value Reference Shell Side Fluid Type Reactor Water (Fresh) 8.6 Shell Side Fouling Factor (Design) 0.0005 8.6 Shell Side Fluid Flow Rate (gpm) 7,450 (3,725,000 lb/hr) 8.6 Shell Side Inlet Temperature (0 F) 120.0 8.6 Shell Side Outlet Temperature

(°F) All Tubes: 108.6 8.6 5% Plugged: 108.8 Tube Side Fluid Type Service Water (Fresh) 8.6 Tube Side Fouling Factor (Design) 0.002 8.6 Tube Side Fluid Flow Rate (gpm) 7,400 (3700,000 lb/hr) 8.6 Tube Side Inlet Temperature (0 F) 90 8.6 Tube Side Outlet Temperature (0 F) All Tubes: 101.5 8.6 5% Plugged: 101.25 Design Q -Service (BTU/hr) All Tubes: 42,550,000 8.6 5% Plugged: 41,600,000 Design U -Clean (BTU/hr-ft 2-0F) All Tubes: 463 8.6 5% Plugged: 466 Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CA No.97-201 Rrv A PAGE 5 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe /DAT 7/16/98.

S. Ingalls ..o. ..31-003 cLENT COMED / LaSalle County Station PROECT COMED / LSCS GL 89-13 Program TIrL Thermal Model of COMED / LaSalle Station RHR Heat Exchangers 1(2)RHROIA

& B.Table 3-5 Shutdown Cooling Performance Detail Parameter Value Reference Design U -Service (BTU/hr-ft 2-°F) All Tubes: 213 8.6 5% Plugged: 215 Shell Velocity (ft/sec) 3.4 8.6 Number of Plugged Tubes All Tubes: 0 8.6 5% Plugged: 53 3.4. VENDOR DESIGN FOULING FACTOR The PROTO-HX convention for calculating overall fouling factors is to combine the shell-side and tube-side fouling factor using the outside heat transfer surface as the reference area. Equations 2 and 3 show the PROTO-HX method of combining the shell-side and tube-side fouling factors.AreaRatio

= TubeOD Tube ID Equation 2 Equation 3 fwota = fhcII + (Area Ratio). f,, Table 3-6 shows the results of combining the shell-side and tube-side fouling factors using the area ratio.Table 3-6 PROTO-HX Design Fouling Tube ID, in: 0.750 Tube 013, in: 0.652 Area Ratio (OD/ID) 1.150 Tube-side FF 0.002 Shell-side FF 0.0005 Overall FF (Area Ratio) 0.0028006d However, according to the vendor data sheets (Reference 8.6), the design overall fouling factor used by the vendor in the performance analysis presented on the data sheets appears to be approximately 0.0025 verse the 0.0028 calculated in Table 3-6. The fouling factor is calculated from the vendor data sheets by comparing the difference between the service and the clean overall heat transfer coefficients.

1 U=r(h )+ rtube-side FF + rw,,I, + rshe,,-side FF + r(rho) Equation 4 Reference 8.5 discusses that the fouling factor may be calculated directly from the difference between the service and clean overall heat transfer coefficients only when all other parameters remain constant (flow and temperature).

Likewise, the total fouling Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION

' No.97-201 REV A PAGE 6 OF 12 GROTON, CONNECTICUT oRIGZT D. Phyfe '/OA 7/16/98 -VERIFIRDBY

s. Ingalls JOB NO.31-003 COMED/ LaSalle County Station PROJECr COMED / LSCS GL 89-13 Program TIME Thernmal Model of COMED / LaSalle Station RHR Heat Exchangers l(2)RHRO1A

& B.factor may be calculated as the sum of the shell-side and tube-side fouling factors (Equation 5).ftotal -ftube-side

+ fshell-side Equation 5 Table 3-7 shows that the difference between the service and clean overall heat transfer coefficients is approximately 0.0025. The variations in the fouling factor can be attributed to the round-off error as reported on the vendor data sheets.Table 3-7 Vendor Data Sheet Fouling Factor Vendor Data Sheet U-Service U-Clean Fouling (U)All Tubes -SDC 213 463 0.0025350 5% PLG -SDC 215 466 0,0025052 All Tubes -CCM 231 563 0,0025528 5% PLG -CCM 235 568 0.0024948 Overall FF= 0.0025 Therefore, the PROTO-HX benchmarking of the RHR model will be performed with an overall fouling factor of 0.0025 versus the standard PROTO-HX method of referencing the fouling resistances to the outside heat transfer area. For PROTO-HX to use the 0.0025 value for fouling it will be entered into the heat exchanger data sheet as a shell-side fouling factor and zero will be entered as the tube-side fouling factor.The direct addition of the shell-side and tube-side fouling factors will yield a more conservative model then the standard PROTO-HX method of combining the fouling factors. This is because the Hoff calculated at data sheet conditions with a lower overall fouling factor is lower than that calculated with the higher value of overall fouling factor.4.0 APPROACH This calculation utilizes plant/vendor fabrication specifications provided in Attachment (A) to develop a thermal performance prediction model for the LSCS RHR Hx. The calculation then benchmarks the models by comparing the heat transfer rate calculated by PROTO-HXTM Version 3.02 with the vendor's specifications for thermal performance under different cooling modes.4.1. PROTO-HXTM PARAMETER CALCULATION Minimum Shell Area The minimum shell area is calculated using either the shell side velocity or shell geometry.

The preferred method of calculation is using the shell side velocity.

Reference 8.6 gives the shell side velocity to be 3.4 ft/sec at a flow rate of 7396.31 gpm (Section 4.3). Based on this velocity and flow rate the minimum shell side area is 4.880 ft 2.Outside H Factor (Hoff)Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION cm'o 97-20 1 R A PAGE 7 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe 0DAT 7/16/98 -VzRIPIED By S. Ingalls JOB No.31-003 c"NrT COMED / LaSalle County Station PRojEct COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers 1(2)RHROIA

& B.The Outside H Factor is a multiplier, with value less then 1.0, used to reduce the ideal shell side film heat transfer coefficient.

The Outside H Factor accounts for inefficiency in the heat exchanger.

Using the back calculation method, based on the design overall heat transfer coefficient (215 Btu/hr ft 2 OF), the Outside H Factor was calculated by PROTO-LiX T M to be 0.56355.4.2. PROTO-HXTm EXTRAPOLATION METHOD All calculations performed for this calculation are based on a constant cold inlet temperature (except where noted). This allows the comparison of the heat transfer, outlet temperatures, log mean temperature difference (LMTD), and heat transfer coefficient.

There is no comparison of the heat transfer coefficient in the design case since PROTO-HXTM used the data sheet value of the heat transfer coefficient to calculate the outside heat transfer coefficient.

4.3. PROTO-HX FLOW RATE INPUTS The vendor data sheets have the actual heat exchanger mass flow rates listed on them.The mass flow must be converted to a volumetric flow rate at 60'F for entry into PROTO-HX._ 7.48. rh 60. P60-F Table 4-1 Vendor Data Sheet: PROTO-HX Flow Rate Inputs Parameter Actual Flow (lb/hr) PROTO-HX Input (gpm)Tube-side, 90'F 3,700,000 7396.31 Tube-side, 100l F 3,700,000 7396.31 Shell-side, 120'F 3,725,000 7446.28 Shell-side, 212'F 4,200,000 8395.81 Density, 60'F 62.364 lb/ft 3 (8.12) ..-Equation 6 Volumetric flow rates are converted to mass flow rates based on a set temperature of 60'F in PROTO-HX.

Therefore, the actual PROTO-HX inputs have to be adjusted to give the correct mass flow rate. The PROTO-HX input is adjusted using the ratio of the actual water density and the density of water at 60'F.Qpx = Q temp P tenmp P60QF Equation 7 Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CA- O.97-201 REV A Pmr 8 oE 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe /ATE 7/16/98 -VERIFIEDBY S. Ingalls JOB NO. 31-003COMED / LaSalle County Station "' COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers l(2)RHR0IA

& B.Table 4-2 Reference Condition:

PROTO-HX Flow Rate Inputs Parameter Density (lb/ft 3) Actual Flow (gpm) PROTO-HX Input (gpm)Tube-side, 90'F 62.113 (8.12) 7400 7370.22 Tube-side, 100'F 61.994 (8.12) 7400 7356.08 Shell-side, 1207F 61.712 (8.12) 7450 7372.02 Shell-side, 2127F 59.823 (8.12) 8400 8057.65 PROTO-HX, 60F 62.364 (8.12) .- ---5.0 ASSUMPTIONS 5.1. For the containment cooling mode of operation with a 212'F shell side inlet temperature all fluid entering the shell is considered to be in the liquid phase. This is consistent with the vendor's analysis of the heat exchanger in Reference 8.6. Therefore, future validation of this assumption is not required.5.2. The vendor data sheet (Reference 8.6) is considered an accurate reflection of the vendor's expectation for the heat exchanger's outside film heat transfer coefficient.

Therefore, the benchmarking of the PROTO-HX model to the vendor data sheet will ensure that the PROTO-HX calculated outside film heat transfer coefficient is consistent with the vendor's expectation.

Future validation of this assumption is not required.Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&l 5-1 PROTO-POWER CORPORATION -c -O.97-201 RVA PAGE 9 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe /DAT 7/16/98 VERFIEO BY S. Ingalls JOB*-.31-003 COMED / LaSalle County Station PROJECT COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers 1(2)RHROIA

& B.6.0 ANALYSIS 6.1. PROTO-HXTNS MODEL Table 6-1 compares the PROTO-HXTIf (P-HX) values to the values shown on the Vendor Data Sheets (V -DS). PROTO-HX output reports can be found in Attachment C.Table 6-1 PROTO-HX Model Results CONTAINMENT COOLING MODE SHUTDOWN COOLING MODE ALL TUBES 5% PLUGGED ALL TUBES 5% PLUGGED Parameter P-HX V -DS P-HX V -DS P-HX V -DS P-HX V -DS Shell Side Outlet Temp, OF 171.7 171.6 172.7 172 108.6 108.6 108.9 108.8 Tube Side Outlet Temp, OF 146.0 145.9 144.9 145.3 101.5 101.5 101.2 101.25 Heat Transferred, BTU/hr 1.7 E8 1.70 E8 1.658E8 1.68 E8 4.251 E7 4.255E7 4.147E7 4.16E7 Heat Transfer Coef, BTU/hr ft 2 OF 230.7 231 231.9 235 213.7 213 215 215 Corrected LMTD 64.0 64.1 65.5 65 17.26 17.35 17.6 17.6 Table 6-2 shows the correlation between the manufacture data sheets and the PROTO-HXTM model. PROTO-HX output reports can be found in Attachment C.Table 6-2 PROTO-HX Model Correlation CONTAINMENT COOLING MODE SHUTDOWN COOLING MODE Parameter ALL TUBES (%) 53 PLUGS (%) ALL TUBES (%) 53 PLUGS (%)Shell Side Outlet Temp 0.06 0.41 0.00 0.09 Tube Side Outlet Temp 0.07 -0.27 0.00 -0.05 Heat Transferred 0.00 -1.31 -0.09 -0.31 Heat Transfer Coef -0.13 -1.32 0.33 N/A Corrected LMTD -0.16 0.77 -0.52 0.00 6.2. FOULING SENSITIVITY The fouling sensitivity of the jacket water cooler is shown in Figure 6-1. The fouling sensitivity was developed at both sets of Reference Conditions (Table 3-1 and Table 3-2).The tube-side fouling factor was varied from 0.0000 until the required heat load was met by increments of 0.0005 (hr ft 2 OF/Btu). The shell-side fouling factor is held constant at the design value of 0.0005 (hr ft 2 OF/Btu). The fouling factors overall fouling factors where entered in PROTO-HX based on the combining of the tube-side and shell-side fouling factors as described in the Heat Exchanger Design Handbook (Reference 8.5).The PROTO-HX Calculation Reports for the fouling sensitivity can be found in Attachment D.Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION

--o.97-201 REv A PAGE 10 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe /DATE 7/16/98.VERIFIED BY S. Ingalls JOB No-.31-003 CLI COMED / LaSalle County Station PROJECT COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers I(2)RHROIA

& B.Figure 6-1 Fouling Sensitivity 250,000.000 200,000,000" 150.000.000 0 d 100.000,000 50.000,000 Contasiment Cooung Mode)olIng 1equired A~eat -Coni ainment C 3hutdown Cooling ,____ ______'-~1equirediAleat

-Shut down Coo in g~*0 .1 0.0000 0.0002 0.0004 0.0006 0.0008 0.0010 0.0012 0.0014 0.0016 0.0018 0.0020 Tube-side Fouling (hr ft2 *FIBtu)6.3. THERMAL PERFORMANCE MARGIN The clean thermal margin is assessed by a comparison of the reference condition performance requirements to the heat exchanger performance capability with a zero (0)fouling factor. Using a zero (0) fouling factor shows the maximum available performance of the heat exchanger.

Likewise, the service thermal margin is assessed by comparing the reference condition performance requirements to the heat exchanger performance capability with the design fouling factor.The margin is calculated directly and as a percentage compared to the required heat rate to perform the component's safety function.

The PROTO-HX reports can be found in Attachment E.Margin=(Heat Rate)-(Heat Rate)equjird

% Margin= 100 "eMargin (Heat Rate)rquired Equation 8 Equation 9 Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION --97-201 --A PAGE 1 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe /lDATE 7/16/98 .VERIFIED BY S. Ingalls 10B NO.31-003 cI-1,Nr COMED / LaSalle County Station PRoJECT COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers 1(2)RHROIA

& B.Table 6-3 Thermal Margin -Containment Cooling Mode Service (Design Fouling) Clean (0 Fouling)Parameter All Tubes 53 Plugs All Tubes 53 Plugs Heat Transfer Rate 167,700,000 163,700,000 230,700,000 228,700,000 Required Heat Transfer Rate 155,000,000 155,000,000 155,000,000 155,000,000 Thermal Margin 12,700,000 8,700,000 75,700,000 73,700,000

% Thermal Margin 8.19% 5.61% 48.84% 47.55%Table 6-4 Thermal Margin -Shutdown Cooling Mode Service (Design Fouling) Clean (0 Fouling)Parameter All Tubes 53 Plugs All Tubes 53 Plugs Heat Transfer Rate 42,330,000 41,310,000 57,440,000 56,840,000 Required Heat Transfer Rate 41,600,000 41,600,000 41,600,000 41,600,000 Thermal Margin 730,000 -290,000 15,840,000 15,240,000

% Thermal Margin 1.75% -0.70% 38.08% 36.63%Table 6-5 Adjusted Tube Plugging for Shutdown Cooling Parameter Shutdown Cooling -38 Plugs Heat Transfer Rate 41,600,000 Required Heat Transfer Rate 41,600,000 Thermal Margin 0% Thermal Margin 0.00%

7.0 CONCLUSION

7.1. PROTO-HX T M MODEL The RHR Hx Model was developed using PROTO-HXTM, Version 3.02. The model was benchmarked and validated using the vendor supplied performance data sheets (Containment Cooling and Shutdown Cooling) for the heat exchangers.

Model correlation to the vendor's performance specification for Shutdown Cooling Mode with 53 Plugs was within one percent (-0.31 %). The model correlation with other modes of operation can be found in Table 6-2.This model should be considered suitable for use in the analysis of thermal performance test data.Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&l 5-1 PROTO-POWER CORPORATION CALC .97-201 R~vA PAGE 12 O" 12 GROTON, CONNECTICUT ORIGINATR D. Phyfe /DTEA 7/16/98 VERIFIED BY S. Ingalls JOB "0.31-003 COMED / LaSalle County Station PROJECT COMED / LSCS GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station RHR Heat Exchangers 1(2)RHR0IR1A

& B.7.2. FOULING SENSITIVITY Given a constant shell-side fouling at the model design value, the sensitivity of the RHR heat exchanger to tube-side fouling effects is shown on Figure 6-1.7.3. THERMAL PERFORMANCE MARGIN The available clean thermal margin of the RHR heat exchanger with no tubes plugged in Containment Cooling Mode of operation is 48.84% margin as compared to the Shutdown Cooling Mode of operation margin of 38.08%.Table 6-3 through Table 6-5 show the thermal margin for the RHR heat exchanger in both the Containment Cooling and Shutdown Cooling modes in service and clean conditions at various tube plugging levels.For the Shutdown Cooling mode with tubes plugged, the maximum allowable plugs allowed to still meet the required heat load with design fouling is 38 plugs.

8.0 REFERENCES

8.1. Process Flow Diagram, Residual Heat Removal System, 731E966AA Sheets I & 3 (Attachment B)8.2. NRC Generic Letter 89-13 8.3. Struthers Wells Drawing 1-71-04-30971 D2, Revision 1, "2-Pass Tube Layout for 52" I.D. Residual Heat Removal Hx. 52-27U12-6V" 8.5. Heat Exchanger Design Handbook, Volume 3, Thermal and Hydraulic Design of Heat Exchangers, Hemisphere Publishing Corp., Rev. 1989 8.6. Struther Wells Hx Data Sheet (Attachment A)8.7. LSCS Drawing, VPF 3161-4-6, J-2500 8.8. LSCS Drawing, VPF 3161-8-2, J-2500 8.9. PROTO-HXTM User Manual 8.10. LSCS Drawing, T-2792, J-2500 8.11. Heat Exchanger Thermal Performance Modeling Software Program PROTO-HX T M Version 3.02 Software Validation and Verification Report (SVVR) SQA No. SVVR-93948-02, Revision F, dated 2/17/98 8.12. Proto-Power Calculation 93-048, "Fluid Properties

-Fresh Water -Range 32 0 F to 5007F", Rev. A Form No.: P1050105 Rev.: 10 Date: 10/21t97 Ref.: P&I 5-1 Attachment A to Proto-Power Calculation 97-201 Revision A Proto-Power Calc: 97-201

Attachment:

A Rev: A Page 1 of 5 6IOIIA SECTION X STRUTHERS WELLS CORPORATION Heat Exchanger Specification Sheet Page 4 13 14 16 17 Is 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39 40 41 42'3 48'7 46 41 52 53 5'N T6)_ F WýLV -k %A U~h W tG pk ~jk_JOB NO.2 CUSTOMER GENERAL cOMPA f ' REFERENCENO.

5- PrQll"IC NO. S.t.,' --A PLAI LOCATION l.- "T_ DATE 5h9171 6 SERVCE OF UNIT R lg-iA\u4'o VA,ý ITEM NO. j _______6SIZE SZT.D. x2 31 TYPE )T~~~Nr.f I~,'*~V~7 UR .I NI G r,,,:S5) SURF./UNIT jC., O SHELLS/UNIT One SURF./SHELL

-1 (E~rP'j a -Four- A)\ llnls RenA PERFORPAONCE OF ONE UNI1T __________________

SHELL SIDE TUBE SIDE o FLUID CIRCULATED R--_0Cr r " ' y" TOTAL FLUID ENTERING #/HR 3 _ ( 74rzc ( _ c5,tn (74 3 o " 'VAPOR LIQUID 37- ;" ( .7 (STEAM NON-CONDENSA BL ES FLUID VAPORIZED OR CONDENSED STEAM CONDENSF-D SPECIFIC GRAVITY VISCOSITY MOLECULAR WEIGHT SPECIFIC HEAT BTU/LB OF THERMAL CONDUCTIVITY BTU/HR-FT-AF LATENT HEAT BTUILb TEMPERATURE IN OF -__ __ ___,_'TEMPERATURE OUT OF lp-'OPERATING PRESSURE PSIG NO. PASSES PER SHELL (M. -n,__ _ -_ _ __ _ _VELOCITY FT/SEC .VP,. L.rp (.t-7 PRESSURE DROP t .PSI R.l .9-FOULING RESISTANCE

.(MIN) .HEAT EXCHANGED.

BTU/HR 4-. ( MTD CORRECTED.

OF TRANSFER RATE -SERVICE 71 CLEAN _ _.(63 _ _ _ _CONSTRUCTION OF ONE SHELL -, S7'uL.ocs DESIGN PRESSURE PSIG I*TEST.PRESSURE PSlG DESIGN TEMPERATURE OF TUBES NO. O.D. BWG vG. LENGTH PITCH SHELL I.D. O.D. SHELL COVER (INTEG.)(REMOV.)

CHANNEL OR BONNET CHANNEL COVER TUBESHEET-STATIONARY TUBESHEET FLOATING BAFFLE-CROSS TYPE FLOATING HEAD COVER BAFFLES-LONG TYPE IMPINGEMENT PROTECTION TUBE SUPPORTS TUBE TO TUBE SHEET JOINT GASKETS CONNECTIONS-SHELL SIDE IN OUT RATING CHANNEL SIDE IN OUT RATING CORROSION ALLOWANCE-SHELL SIDE TUBE SIDE CODE REOUIREMENTS TEMA CLASS REMARKS Proto-Power Calc: 9I-ZUI

Attachment:

A Rev: A Page 2 of 5 1UI1A SECTION X STRUTHERS WELLS CORPORATION Heat Exchanger Specification Sheet 1PIVC~ ?SIC-C-rt

'TutV~Fs SlCA"Ft Trinwm~ CP VuM-i mr -d 2 3 4 S S 7 S IO 11 12 13 14 Is IS 17 IS 19 20 21 22 23 24 25 26 27 25 29 30 31 32 23 34 3S 36 27 38 39 40 41 42 43 44 45 4.47 48 49 so SI s2 S3 54 JOB NO.CUSTOMER r, r- N cr R N C-" A t , y ,,, insmPA"'i REFERENCE NO. , ADDRESS rn4 X,,."..9-E\4-NO. (7 n -C PLANT LOCATION TD --c -,ATE SERVICE OF UNIT p .A r i-er.* ITEM NO.-SIZE 7r. "T.. TYPE ("rj_ T.1 C7. _ ) , SURF.IUNIT

.'E '%"'*O SHELLS/UNIT SHELS/NIT Q SURF./SMELL

!C';`p 11.79 S -ItV" (PERFORMANCE OF ONE UNIT SHELL SIDE TUBE SIDE FLUID CIRCULATED

.Ai -r " J "rAwiv pyvui e-. ACICOLV" TOTAL FLUID ENTERING I/MR "4=Q-i , (

7ýc" " CT 40c' c--VAPOR LIQUID ,-77r.OC, C*STEAM NON-CONOENSABLES FLUID VAPORIZED OR CONDENSED STEAM CONDENSED SPECIFIC GRAV!TY VISCOSITY MOLECULAR WEIGHT SPECIFIC HEAT 8TU/LB oF THERMAL CONDUCTIVITY BTU/HR-FT-*F LATENT HEAT BTU/LB TEMPERATURE IN OF TEMPERATURE OUT OF ie1.R tl,k. _OPERATING PRESSURE PSIG NO. PASSES PER SHELL nT VELOCITY FT/SEC .4. I L,-i 7. 4-PRESSURE DROP tv PSI B-57. es e_%. _FOULING RESISTANCE (MIN) *

I -4q HEAT EXCHANGED.

BTU/HR -*4e.41 cne-%4' Ins MTO CORRECTED.

OF 4&e-T..C TRANSFER RATE -SERVICE CLEAN CONSTRUCTION OF ONE SHILL DESIGN PRESSURE .PSIG ____________________

__________

TEST.PRESSURE PSIG Per C-..A. -ClAp DESIGN TEMPERATURE OF A4g e- 4F,.c'1 I 32 "eo 4Vkn TUBES.4 A". .SO LENGTH 4k*; PITCH I" Tjivc 1 TUBES 304.L 3/4- BwG SHELL C. /2. u 4j3 L 0/S.CA. D. 52." 00( SHELL COVER C.& .ilA4LS _%aA¥INTEG')d297$M CHANNEL OR SONNET C. I.A.3/ C -q,.r 'nr.e CHANNEL COVER (.q,. t-,j(v--e%

wr-AiC Cant*TUBESHEETjSTATIONARY b 'A * , S/_e TUBESHEET FLOATING BAFFLE-CROSS 304% TYPE meA. __S r PICI,1 FLOATING HEAD COVER BAFFLES-LONG TYPE I IMPINGEMENT PROTECTION Ye-.TUBE SUPPORTS -14. 1-2/ -'!;'is_. TUBE TO TUBE SHEET JOINT WrIAP-A A GASKETS W pMnA _r "e. Am ksy%, CONNECTIONS-SHELL SIDE IN I P." OUT i9 RATING W. -.CHANNEL SIDE IN I s" " OUT I W," RATING W. F.CORROSION ALLOWANCE-SHELL SIDE ie'v, .Ceer.1_ tALVe..TUSE SlOE k"y_ 'SCvr. 71A CODE REOUIREMENTS Snhel, S;AOL- See .I-C -. ,-e SAc._.re.i-cTEMA CLASS C)REMARKS Peoyr~nyyn.yc9 re wAa I " are nv-c on F, utu-Puwei CaL. ;7-201

Attachment:

A Rev: A Pane 3 of 5 Page 5 SECTION X STRUTHERS WELLS CORPORATION Heat Exchanger Specification Sheet 1100tIA ALU.. TJXvS PLYRUAB\La

-CONTPAN~AMSAT C-(CM1UNG AMnny I JOB No.2 CUSTOMER c_..Pr' REFERENCE NO. Z -c;3 ADDRESS $Mp. -\ ,,c NO. (-.4a..> " .O L 4 PLAN47 LOCATION mr' 0\ 1- -z L _\\'-., DATE 't 5SERVICE OF UNIT \ ITEM NO. ~-io~6 SIZE 52.'.).X 2.7,'V.T.L.

TYPE(TEMI\M "AU. 4vE. N c.A.- X SURF.JUIT ~II, SHELLS/UNIT y .SURF./SHELL t .-6 Fpux14. --.o. PERFORMANCE OF ONE UINIT 9 SHELL SIDE TUBE SIDE 10 FLUID CIRCULATED 11 TOTAL FLUID ENTERING #/HR 4, _c,. n P, (f't (c- z C'-.nPr 12 VAPOR 13 LIOUID ,4.? -y -.rs c"." 1-700. Goo 14 STEAM i5 NON-CONDENSABLES 16 FLUID VAPORIZED OR CONDENSED 17 STEAM CONDENSED 1I SPECIFIC GRAVITY 19 VISCOSITY 20 MOLECULAR WEIGHT 21 SPECIFIC HEAT BTU/LB OF 22 THERMAL CONDUCTIVITY BTU/HR-FT-OF 23 LATENT HEAT BTU/LB g4 TEMPERATURE IN OF .212.- n_ I _ _ n____ _ _25 TEMPERATURE OUT 'F'- l7 _ _ __r__ ___._-_ _26 OPERATING PRESSURE PSIG 27 NO. PASSES PER SHELL T 28 VELOCITY FT/SEC -_:k. p,. L__,,Cy , _,_ _ _ _ _ _ __ _ _ _ _ __t 29 PRESSURE DROP mr,-C. PSI V 30 FOULING RESISTANCE (MIN) ,_____

no.____ 7____31 HEAT EXCHANGED.

BTU/HR I 7 Q -00,I MTD CORRECTED.

F 664-1 32 TRANSFER RATE -SCRVICE ) CLEAN 33 .CONSTRUCTION OF ONE $HELL (SEQ k -,7* 4"Qyn 34 DESIGN PRESSURE PSIG 35. TEST.PRESSURE PSIG 35 DESIGN TEMPERATURE

F 37 TUBES NO. O.D. BWG AVG. WLO. LENGTH PITCH 38 SHELL. I. D. O.D. SHELL COVER (INTEG.)(REMOV.)

39 CHANNEL OR BONNET CHANNEL COVER 40 TUBESHEET-STATIONARY TUBESHEET FLOATING 41 BAFFLE-CROSS TYPE FLOATING HEAD COVER 42 BAFFLES-LONG TYPE IMPINGEMENT PROTECTION 43 TUBE SUPPORTS 44 TUBE TO TUBE SHEET JOINT 45 GASKETS 46 CONNECTIONS-SHELL SIDE IN OUT RATING 47 CHANNEL SIDE IN OUT RATING 48 CORROSION ALLOWANCE-SHELL SIDE TUBE SIDE 48 CODE REQUIREMENTS TEMA CLASS 50 REMARKS S5 52 53 Proto-Power Calc: 97-201 64 Attachment-A Rev: A Page 4 of 5

.rage L SE .CTION X.-raez STRUTHERS WELLS CORPORATION Heat Exchanger Specification Sheet 1 II 11 21 21 21 21 29 29 2S 31 32 33 35 26 27 S2 29 30 31 42 33 3S 46'7 48 41 42 43 45 FI'VE P £C¶__AAT "T P GGE-.. -C CcoOL~tt~. 1 .JOB NO.2 CUSTOMER C-r&N REFERENCE NO. 2O5 -3 ADDRESS , ._ NO. "--4 PLANT LOCATION l .-G. Sc\\e -t DATE .sli 17t 5 SERVICE OF UNTITEM NO. -6 SIZE ý 7 .A.TYE(,-&~P¶I (VfR1.rSURF./UNIT i SHELLS/UNIT "n- SURF,/SHEL L W r-' a SURFF.IUNPr.FRMARCE OF ONE UNIT ___r______.

_________g SHELL SIDE TUBE SIDE 0 FLUID CIRICULATCD X'-) P-v-in \4ývp-v- -se! 1Ce ,e3ey I TOTAL FLUID ENTERING I/Hf kA C%-0n" (R4csrt f ':ilM>

(_i4oc- GPM')2 VAPOR 3 LIQUID 4. ?,e-s C;gýc' 7l 4 STEAM S NON-CONDENSABLES 6 FLUID VAPORIZED OR CONDENSED 7 STEAM CONDENSED e SPECIFIC GRAVITY O VISCOSITY 0 MOLECULAR WEIGHT I SPECIFIC HEAT BTU/LB OF 2 THERMAL CONDUCTIVITY BTU/HR-FT-.F LATENT HEAT BTU/LB TEMPERATURE IN OF 712.c TEMPERATUREOUT OF l 12, OPERATING PRESSURE PSIG NO. PASSES PER SHELL ( _"1 VELOCITY FT/SEC 3-Q& _,________-t_________,____

PRESSURE DROP , PSI l __ _ _ _ _ _ _ _ _FOULING RESISTANCE (MIN) I (__ ___ _ .... .* __(___.HEAT EXCHANGED.

BTU/HR " e,ýo e MTO CORRECTED.

OF TRANSFER RATE -SERVICE CLEAN CONSTRUCTION OF ONE SHELL.DESIGN PRESSURE PSIG.TEST.PRESSURE PSIG DESIGN TEMPERATURE O F TUBES NO. O.D. BWG AVG .VO. LENGTH PITCH SHELL I. D. OD. SHELL COVER (INTEG.)(REMOV.)

-CHANNEL OR BONNET CHANNEL COVER TUBESHEET-STATIONARY TUBESHEET FLOATING BAFFLE-CROSS TYPE FLOATING HEAD COVER BAFFL ES-LONG TYPE IMPINGEMENT PROTECTION TUBE SUPPORTS TUBE TO TUBE SHEET JOINT GASKETS CONNECTIONS-SHELL SIDE IN OUT RATING CHANNEL SIDE IN OUT RATING CORROSION ALLOWANCE-SHELL SIDE TUBE SIDE CODE REQUIREMENTS TEMA CLASS REMARKS nLA iy, vv-7%,s j u pýP1UIU-pUWc, tcLk.97-201 Attactlment:

A Rev: A Page 5 of 5 Attachment B to Proto-Power Calculation 97-201 Revision A Proto-Power Calc: 97-201

Attachment:

B Rev: A Page 1 of 3

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-~'~C' -- ~"%7\"-. -.at.. .~4. ----n..asIa ~145 Ia~ -sonuiw a a Iq ...s.in C fla ISa-oQ)**00 Ga-4 o I 1'.)a Ga ---3 I N MM! /'- II ML ft -A OWC-Z *Owee 0'~r..w-.an i *m AfaDFC SuýsrgtgSS-ll PRINTll-aR tR.T-W 2-1/2met uramo~f it nwj wam ws*k- %n.W~ rn f I i I I Attachment C to Proto-Power Calculation 97-201 Revision A Proto-Power Calc: 97-201

Attachment:

C Rev: A Page 1 of 9 10:44:32 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-B001 -LSCS -RHR Hx.SDC -All Tubes, Vendor Fouling 07/13/98 40 I IF Shell and Tube Heat Exchanger Input Parameters II II II Shell-Side Flhiid-Quantity, Total gpm -7_,446-7.28--..

Inlet Temperature OF 120.00 Outlet Temperature OF 108.80 Fouling Factor 0.00250 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)

Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Tube-Side 90.00 101.25 0.00000 Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 TEMA-E 11,500.00 0.996344561 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.ft.'F) 1 4.880000000 3.400 1.0000 Triangular 2 Yes 1,063 ~1,0636-55.30 0.652 0.750 9.40 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 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-201

Attachment:

C Rev: A Page 2 of 9 10:44:32 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -All Tubes, Vendor Fouling 07/13/98 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) 7,396.3 Shell Flow (gpm) Shell Flow (gpm) 7,446.3 Shell Temp In (IF) Tube Inlet Temp (IF) 90.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 120.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF)1_ Fouling Calculation Results Shell Mass Flow (lbni/hr)

U Overall (BTU/hr-ft 2 -F)Tube Mass Flow (Ibnr/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..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 (°F)Prandtl Number Tav Shell (°F)Bulk Visc (Ibm/ft hr) Shell Skin Temp (°F)Skin Visc (lbm/ft-hr)

Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (°F)Cp'(BTU/lbm-°F)

Tar Tube (°F)K (BTU/hr'ft-0 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 (lbm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm.°F)

K (BTU/hr-ft-°F)

Shell-Side 3.43 3.354E+04 3.86 1.42 1.48 61.80 1.00 0.37 3.725E+6 3.7E+6 4.25 1E+7 18.5 11,500.0 Tube-Side 6.72 4.729E+04 4.77 1.73 1.67 62.05 1.00 0.36 Overall Fouling (hr.ftt 2.F/BTU)Shell-Side ho (BTU/hr-ft 2 0.F)Tube-Side hi (BTU/hr-ft'.°F) l/Wall Resis (BTU/hr-ft 2--F)LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)Shell Temp In (OF)Shell Temp Out (°F)Tav Shell (OF)Shell Skin Temp (°F)Tube Temp In (IF)Tube Temp Out (°F)Tav Tube (OF)Tube Skin Temp (°F)Proto-Power Calc: 97-201

Attachment:

C Rev: A Page 3 of 9 0.002500 977.6 1,666.6 2,148.1 0.9328 213.7 120.0 108.6 114.3 110.2 90.0 101.5 95,7 98.5** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:43:25 PROTO-HX 3.02 by Proto-Powver Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -53 Plugs, Vendor Fouling 07/13/98 a II Shell and Tube Heat Exchanger Input Parameters II Shell-Side Flii id-Qiiintif, Tota--, g m Inlet Temperature OF 120.00 Outlet Temperature OF 108.80 Fouling Factor 0.00250 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~7.39-6J.3--

90.00 101.25 0.00000 Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 TEMA-E 11,500.00 0.996344561 Heat Exchanger Type Effective Area (ftl2)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-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 1 4.880000000 3.400 1.0000 Triangular 2 Yes 1,063 1,010 55.30 0.652 0.750 9.40 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-201

Attachment:

C Rev: A Page 4 of 9 10:43:25 PROTO-HX 3.02 by Proto-Power Corporation (SN#PfIX-0000)

Commonwealth Edison Calculation Report for E12-B001 -LSCS -RHR Hx.SDC -53 Plugs, Vendor Fouling 07/13/98 Calculation Specitications

II i.I 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)7,396.3 7,446.3 90.0 120.0 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-ft 2.IF)Tube-Side hi (BTU/hr-ft 2.OF)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft2.°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 (OF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Vise (Ibm/ft-hr)

Shell Skin Temp (OF)Skin Vise (lbm/ftrhr)

Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (OF)Cp,(BTU/Ibm.°F)

Tav Tube (IF)K (BTU/hr-ft'°F)

Tube Skin Temp (OF)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) 3.43 Reynold's Number 3.359E+04 Prandtl Number 3.85 Bulk Visc (Ibm/ft-hr) 1.42 Skin Vise (lbm/ft-hr) 1.48 Density (Ibm/ft 3) 61.80 Cp (BTU/lbm 0'F) 1.00 K (BTU/hr-ft'°F) 0.37 3.725E+6 3.7E+6 4.147E+7 18.8 10,926.6 Tube-Side 7.07 4.970E+04 4.78 1.73 1.68 62.05 1.00 0.36 Overall Fouling (hrflt 2.°F/BTU)Shell-Side ho (BTU/hbafta'°F)

Tube-Side hi (BTU/hr-ft 2"°F)I/Wall Resis (BTU/h'ft 2"°F)LMTD Correction Factor U Overall (BTU/hr.ft 2 0.F)Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (IF)Proto-Power Calc: 97-201

Attachment:

C Rev: A Page 5 of 9 0.002500 978.0 1,734.7 2,148.1 0.9382 215.0 120.0 108.9 114.4 110.3 90.0 101.2 95.6 98.3** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:46:07 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -All Tubes, Vendor Fouling 07/13/98 Shell and Tube Heat Exchanger Input Parameters Shell-Side, Toa-i- gpm_44_6.28 Inlet Temperature OF 120.00 Outlet Temperature OF 108.80 Fouling Factor 0.00250 Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/hr)Design Heat Trans Coeff (BTU/hrvft 2.°F)Emprical Factor for Outside h Performance Factor (% Reduction)

Tube-Side 7,396.31 -90.00 101.25 0.00000 Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 TEMA-E 11,500.00 0.996344561 1 4.880000000 3.400 1.0000 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 (fit)Tube Inside Diameter (in)Tube Outside Diameter (in)Tube Wall Conductivity (BTU/hr-ftl.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 Yes 1,063 1,063 55.30 0.652 0.750 9.40 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-201

Attachment:

C Rev: A Page 6 of 9 10:46:07 IF PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -All Tubes, Vendor Fouling 07/13/98 CJalculation Specitications II 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 (OF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out (OF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (fF)Shell Inlet Temp (OF)7,396.3 8,395.8 100.0 212.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (lbm/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-°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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (°F)Bulk Visc (lbm/ft hr) Shell Skin Temp (OF)Skin Visc (lbm/ft-hr)

Tube Temp In (OF)Density (Ibm/fP) Tube Temp Out (°F)Cpi(ITJilbm 0'F) Tav Tube (°F)K (BTU/hr'ft 0'F) Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTUfhr)LMTD Effective Area (ft2)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 0'F)K (BTU -hrft.F)Shell-Side 3.96 6.973E+04 2.00 0.77 0.84 60.31 1.00 0.39 4.2E+6 3.7E+6 1.7E+8 68.8 11,500.0 Tube-Side 6.76 6.230E+04 3.53 1.31 1.20 61.67 1.00 0.37 Overall Fouling (hr' ft 2-F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr ft 2.°F)1/Wall Resis (BTU/hr-ft'°F)

LMTD Correction Factor U Overall (BTU/hr ft2.°F)Shell Temp In (°F)Shell Temp Out (°F)Tav Shell (OF)Shell Skin Temp (fF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (OF)Tube Skin Temp f°F)Proto-Power Calc: 97-201

Attachment:

C Rev: A Page 7 of 9 0.002500 1,286.8 1,944.4 2,148.1 0.9309 230.7 212.0 171.7 191.8 179.5 100.0 146.0 123.0 132.4** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:47:05 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -53 Plugs, Vendor Fouling 07/13/98 II Shell and Tube Heat Exchanger Input Parameters

'I Shell-Side Fluid _Q-iantinfi, T6-t-l gpm 7n,-446.28 Inlet Temperature OF 120.00 Outlet Temperature OF 108.80 Fouling Factor 0.00250 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......T,367.3T -90.00 101.25 0.00000 Fresh Water Fresh Water 41,600,000 215.00 0.563555000 0.00 TEMA-E 11,500.00 0.996344561 1 4.880000000 3.400 1.0000 Triangular Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Number of Shells per Unit Shell Minimum Area Shell Velocity (f'/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 Wall 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 Yes 1,063 1,010 55.30 0.652 0.750 9.40 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-201

Attachment:

C Rev: A Page 8 of 9 10:47:05 01I PROTO-HX 3.02 by Proto-Power Corporation (SN#fPHX-0000)

Commonwealth Edison Calculation Report for E12-B001 -LSCS -RHR Hx.CCM -53 Plugs, Vendor Fouling 07/13/98.1 Calculation Specitications 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)7,396.3 8,395.8 100.0 212.0 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-ft2-OF)

Tube-Side hi (BTU/hr-ft 2.OF)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2.0 F)LMTD LMTD Correction Factor Effective Area (ft)Overall Fouling (hrift 2.°FIBTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ftrhr)

Shell Skin Temp (OF)Skin Visc (lbm/ft-hr)

Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (OF)Cp (BTU/Ibm 0'F) Tav Tube (°F)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)4.2E+6 3.7E+6 1.658E+8 69.9 10,926.6 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.°F)

K (BTU/hr-ft.°F)

Shell-Side 3.97 6.995E+04 1.99 0.77 0.84 60.30 1.00 0.39 Tube-Side 7.12 6.523E+04 3.55 1.32 1.21 61.67 1.00 0.37 Overall Fouling (hr-ft 2 0.F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2.°F)I/Wall Resis (BTU/hr.ft 2-°F)LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)Shell Temp In (IF)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (°F)Tube Temp In (°F)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (fF)Proto-Power Calc: 97-201

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C Rev: A Page 9 of 9 231.9 212.0 172.7 192.3 179.7 100.0 144.9 122.4 131.7 0.002500 1,287.9 2,019.7 2,148.1 0.9365** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Attachment D to Proto-Power Calculation 97-201 Revision A Proto-Power Calc: 97-201

Attachment:

D Rev: A Page 1 of 11 11:48:39 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -Tube-side FF = 0.0000 07/15/98.1 II Calculation Specifications 11 Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (IF)Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)Input Fouling Factor 7,370.2 7,372.0 90.0 120.0 0.000500 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-°F)Tube-Side hi (BTU/hr-ft 2-°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hrfit 2 0-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 (°F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (OF)Bulk Vise (Ibm/ft-hr)

Shell Skin Temp (OF)Skin Vise (lbm/ft-hr)

Tube Temp In (OF)Density (lbm/ft')

Tube Temp Out (OF)CV(BTU/lbm-°F)

Tav Tube (OF)K (BTU/hr'ft'°F)

Tube Skin Temp (°F)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)3.688E+6 3.687E+6 5.4E+7 15.3 11,500.0 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (Ibm/ft-hr)

Density (Ibm/ft 3)Cp (BTU/Ibm-'F)

K (BTU/hr'ft 0'F)Shell-Side 3.40 3.268E+04 3.93 1.45 1.53 61.82 1.00 0.37 Tube-Side 6.70 4.796E+04 4.68 1.70 1.63 62.03 1.00 0.36 Overall Fouling (hr'ft 2-°F/BTU)Shell-Side ho (BTU/hr-ft2-°F)

Tube-Side hi (BTU/hr'ftz-°F)

I/Wall Resis (BTU/hr'ft2-°F)

LMTD Correction Factor U Overall (BTU/hr.ft 2.°F)Shell Temp In (°F)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (°F)Tube Skin Temp (OF)Proto-Power Calc: 97-201

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D Rev: A Page 2 of 11 372.1 120.0 105.3 112.7 106.7 90.0 104.7 97.3 101.2 0.000500 963.7 1,680.3 2,148.1 0.8229** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 11:50:14 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -Tube-side FF = 0.0005 07/15/98 Calculation Specifications I1 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 (OF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (°F)Input Fouling Factor 7,370.2 7,372.0 90.0 120.0 0.001075 Fouling Calculation Results Shell Mass Flow (lbm/br) U Overall (BTU/hr-ft2t.F)

Tube Mass Flow (ibm/hr) Shell-Side ho (BTU/hr ft 2.°F)Tube-Side hi (BTU/hr-ft2-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.°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 (IF)Skin Visc (lbm/ft-hr)

Tube Temp In (IF)Density (lbm/f') Tube Temp Out (IF)Cpf(BTU/Ibm.'F)

Tav Tube (IF)K (BTU/hr-ft-°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 (Ibm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (Ibm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr-ft.°F)

Shell-Side 3.40 3.285E+04 3.91 1.44 1.51 61.81 1.00 0.37 3.688E+6 3.687E+6 5.024E+7 16.4 11,500.0 Tube-Side 6.70 4.769E+04 4.71 1.70 1.64 62.03 1.00 0.36 Overall Fouling (hr.ft 2.0 F/BTU)Shell-Side ho (BTU/hr'ft2-°F)

Tube-Side hi (BTU/hr.ft2.OF) 1/Wall Resis (BTU/hr.ft 2-°F)LMTD Correction Factor U Overall (BTU/hr.ft 2-°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (°F)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (CF)Proto-Power Calc: 97-201

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D Rev: A Page 3 of 11 0.001075 966.4 1,674.1 2,148.1 0.8710 306.5 120.0 106.4 113.2 108.0 90.0 103.6 96.8 100.3** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 11:50:54 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -Tube-side FF = 0.00 10 07/15/98 Calculation Specifications 11 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 (fF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (fF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)Input Fouling Factor 7,370.2 7,372.0 90.0 120.0 0.001650 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'.°F)

Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hrtft2-'F)

LMTD LMTD Correction Factor Effective Area (ft')Overall Fouling (hr'ft'°F/BTU)

Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell ("F)Bulk Visc (lbm/fti,hr)

Shell Skin Temp ("F)Skin Visc (lbm/ft-hr)

Tube Temp In ("F)Density (lbm/ft3)

Tube Temp Out ("F)Cp?(BTU/lbm.°F)

Tav Tube ("F)K (BTU/hr'ft "F) Tube Skin Temp ("F)Extrapolation Calculation Results Shell Mass Flow (lbm/ru)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')3.688E+6 3.687E+6 4.679E+7 17.3 11,500.0 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbm/fthr)

Density (lbm/ft')Cp (BTU/Ibm.°F)

K (BTU/hr-ft.°F)

Shell-Side 3.40 3.300E+04 3.89 1.43 1.50 61.81 1.00 0.37 Tube-Side 6.70 4.744E+04 4.74 1.71 1.66 62.04 1.00 0.36 Overall Fouling (hr.ft 2-°F/BTU)Shell-Side ho (BTU/hr-ft2-°F)

Tube-Side hi (BTU/hr-ft 2.°F)1/Wall Resis (BTU/hr-ft2-°F)

LMTD Correction Factor U Overall (BTU/hr.ft 2.°F)Shell Temp In ("F)Shell Temp Out (IF)Tav Shell ("F)Shell Skin Temp ("F)Tube Temp In ("F)Tube Temp Out ("F)Tav Tube ("F)Tube Skin Temp (OF)Proto-Power Calc: 97-201

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D Rev: A Page 4 of 11 260.6 120.0 107.3 113.6 109.0 90.0 102.7 96.4 99.5 0.001650 968.7 1,668.7 2,148.1 0.9026** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 11:56:51 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -Tube-side FF = 0.00 15 07/15/98 11 Calculation Specifications I I I, Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User 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 (°F)Shell Inlet Temp (IF)Input Fouling Factor 7,370.2 7,372.0 90.0 120.0 0.002225 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr ft 2-OF)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2-0 F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2.IF)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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ft hr) Shell Skin Temp (OF)Skin Visc (Ibm/ft-hr)

Tube Temp In (OF)Density (lbm/ft')

Tube Temp Out (OF)Cp'(BTU/Ibm 0-F) Tav Tube (OF)K (BTU/hrwft-°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)3.688E+6 3.687E+6 4.369E+7 18.1 11,500.0 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibmift-hr)

Skin Visc (lbm/ft-hr)

Density (lbrn/ft)Cp (BTU/Ibn-°F)

K (BTU/hr-ft-°F)

Shell-Side 3.40 3.314E+04 3.87 1.43 1.49 61.80 1.00 0.37 Tube-Side 6.70 4.722E+04 4.76 1.72 1.67 62.05 1.00 0.36 Overall Fouling (hrift 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2"°F)Tube-Side hi (BTU/hr'ft 2.°F)I/Wall Resis (BTU/hr-ft 2-°F)LMTD Correction Factor U Overall (BTU/hrft 2 0.°F)Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (IF)Proto-Power Calc: 97-201

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D Rev: A Page 5 of 11 226.7 120.0 108.1 114.1 109.8 90.0 101.9 95.9 98.8 0.002225 970.7 1,663.9 2,148.1 0.9242** Reynolds Number Outside Range of Equation Applicability

!! With Minimum Fouling The Test Heat Load Could Not Be Achie 11:52:45 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -Tube-side FF = 0.0020 07/15/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,370.2 Shell Flow (gpm) Shell Flow (gpm) 7,372.0 Shell Temp In (°F) Tube Inlet Temp (IF) 90.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 120.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF) Input Fouling Factor 0.002801 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-ft 2.0 F)Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2.°F)LMTD LMTD Correction Factor Effective Area (ft2)Overall Fouling (hr-ft 2.°F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft hr) Shell Skin Temp (IF)Skin Visc (lbm/ft hr) Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (°F)Cp'(BTU/Ibm.oF)

Tav Tube (IF)K (BTU/hr'ft-'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 2)Property Shell-Side Velocity (ft/s) 3.40 Reynold's Number 3.326E+04 Prandtl Number 3.85 Bulk Visc (lbm/ft-hr) 1.42 Skin Visc (lbm/ft.hr) 1.48 Density (Ibm/ft')

61.80 Cp (BTU/Ibm.°F) 1.00 K (BTU/hr ft.°F) 0.37 3.688E+6 3.687E+6 4.092E+7 18.9 11,500.0 Tube-Side 6.70 4.703E+04 4.78 1.73 1.68 62.05 1.00 0.36 Overall Fouling (hr-ft 2'.F/BTU)Shell-Side ho (BTU/hr'ft 2"°F)Tube-Side hi (BTU/hr.ft 2-OF)I/Wall Resis (BTU/hr.ft 2-0 F)LMTD Correction Factor U Overall (BTU/hr ft 2.°F)Shell Temp In (IF)Shell Temp, Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (°F)Proto-Power Calc: 97-201

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D Rev: A Page 6 of 11 0.00280r 972.4 1,659.7 2,148.1 0.9395 200.5 120.0 108.9 114.4 110.6 90.0 101.1 95.6 98.2** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 12:04:39 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIHX-0000)

Commonwealth Edison Calculation Report for El 2-BOO -LSCS -RHR Hx.CCM -Tube-side FF = 0.0000 07/14/98 i Calculation Specifications 1II 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 (IF)Shell Inlet Temp (IF)Input Fouling Factor 7,356.1 8,057.7 100.0 212.0 0.000500 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2-°F)Tube Mass Flow (Ibm/br) Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2 0.F)Heat Transferred (BTU/hr) I/Wall Resis (BTUI/hrft 2-F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft2.°F/BTU)

Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (7F)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (°F)Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (°F)Skin Visc (lbm/ft-hr)

Tube Temp In (°F)Density (Ibm/ftr)

Tube Temp Out (°F)Cp,(BTh/Ibm 0'F) Tav Tube (IF)K (BTU/hr-ft.°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)4.03 1E+6 3.68E+6 2.168E+8 55.7 11,500.0 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (Ibm/ft-hr)

Density (Ibm/ft')Cp (BTU/Ibm-°F)

K (BTU/hr-ft-°F)

Shell-Side 3.80 6.408E+04 2.09 0.81 0.92 60.46 1.00 0.39 Tube-Side 6.74 6.572E+04 3.31 1.23 1.10 61.56 1.00 0.37 Overall Fouling (hr.fi 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2..F)Tube-Side hi (BTU/hr.ft 2-°F)1/Wall Resis (BTU/hr-ft 2.F)LMTD Correction Factor U Overall (BTU/hr.ft 2-°F)Shell Temp In (°F)Shell Temp Out (°F)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (°F)Tube Temp Out (°F)Tav Tube (IF)Tube Skin Temp (OF)Proto-Power Calc: 97-201

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D Rev: A Page 7 of 11 424.9 212.0 158.4 185.2 165.9 100.0 159.0 129.5 143.1 0.000500 1,227.9 2,006.2 2,148.1 0.7971** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 12:06:16 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -Tube-side FF = 0.0005 07/14/98 Calculation Specitications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Shell Flow (gpm)Shell Temp In (°F)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (°F)Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (°F)Shell Inlet Temp (IF)Input Fouling Factor 7,356.1 8,057.7 100.0 212.0 0.001075 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr ft 2.°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.°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 (°F)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (°F)Bulk Visc (Ibm/ft hr) Shell Skin Temp (IF)Skin Visc (lbm/ffhr)

Tube Temp In (IF)Density (Ibm/ft')

Tube Temp Out (°F)Cp (BTU/lbm'°F)

Tav Tube (IF)K (BTU/hr-ft-°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) 3.80 Reynold's Number 6.491 E+04 Prandtl Number 2.06 Bulk Visc (Ibm/ft-hr) 0.80 Skin Visc (Ibm/ft-hr) 0.89 Density (lbm/ft 3) 60.42 Cp (BTU/Ibm 0'F) 1.00 K (BTU/hr-ft.°F) 0.39 4.031 E+6 3.68E+6 2.01E+8 59.8 11,500.0 Tube-Side 6.73 6.447E+04 3.38 1.26 1.14 61.59 1.00 0.37 Overall Fouling (hr-ft 2 -F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2-IF)1/Wall Resis (BTU/htft 2 0.°F)LMTD Correction Factor U Overall (BTU/hr-ft 2-°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (°F)Shell Skin Temp (OF)Tube Temp In (°F)Tube Temp Out (°F)Tav Tube (°F)Tube Skin Temp (OF)Proto-Power Calc: 97-201

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D Rev: A Page 8 of 11 0.001075-1,236.8 1,982.3 2,148.1 0.8568 341.4 212.0 162.3 187.1 170.6 100.0 154.7 127.3 139.2** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 12:07:05 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -Tube-side FF = 0.0010 07/14/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,356.1 Shell Flow (gpm) Shell Flow (gpm) 8,057.7 Shell Temp In (0 F) Tube Inlet Temp (OF) 100.0 Shell Temp Out (OF) Shell Inlet Temp (0 F) 212.0 Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF) Input Fouling Factor 0.001650 Fouling Calculation Results Shell Mass Flow (Ibn/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hrlft 2-°F)Tube-Side hi (BTU/hr ft 2-OF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hrift 2 7-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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (OF)Bulk Visc (ibm/ft hr) Shell Skin Temp (OF)Skin Visc (Ibm/ft-hr)

Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (OF)Cp1(BTU/Ibm.°F)

Tav Tube (OF)K (BTU/hr-ft-°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)4.03 1E+6 3.68E+6 1.865E+8 63.5 11,500.0 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (Ibm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm.°F)

K (BTU/hr'ft'-F)

Shell-Side 3.80 6.568E+04 2.04 0.79 0.87 60.37 1.00 0.39 Tube-Side 6.73 6.332E+04 3.44 1.28 1.17 61.63 1.00 0.37 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr.ft 2.°F)Tube-Side hi (BTU/hrift 2.°F)I/Wall Resis (BTU/hr-ft 2 -F)LMTD Correction Factor U Overall (BTU/hrift 2.°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (fF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (OF)Tube Skin Temp_°F)Proto-1ower Calc: 97-201

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D Rev: A Page 9 of 11 285.2 212.0 165.9 188.9 174.4 100.0 150.7 125.4 136.0 0.001650 1,244.2 1,961.1 2,148.1 0.8946** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 12:07:58 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -Tube-side FF = 0.0015 07/14/98 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 (OF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (fF)Tube Temp Out (OF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (OF)Shell Inlet Temp (OF)Input Fouling Factor 7,356.1 8,057.7 100.0 212.0 0.002225 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr.ft 2.°F)Tube-Side hi (BTU/hr.ft 2.°F)Heat Transferred (BTUJhr) I/Wall Resis (BTU/hr.ft 2-°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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (OF)Bulk Visc (lbm/ftrhr)

Shell Skin Temp (°F)Skin Vise (lbm/ft-hr)

Tube Temp In (°F)Density (Ibm/fl 3) Tube Temp Out (OF)Cp (BTU/Ibm 0'F) Tav Tube (OF)K (BTU/hr-ft.°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)4.03 1E+6 3.68E+6 1.734E+8 66.9 11,500.0 Property-Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft'hr)

Skin Vise (lbmrft-hr)

Density (Ibm/fr')Cp (BTU/lbm.°F)

K (BTU/hr-ft-°F)

Shell-Side 3.80 6.638E+04 2.01 0.78 0.85 60.34 1.00 0.39 Tube-Side 6.73 6.230E+04 3.50 1.30 1.19 61.66 1.00 0.37 Overall Fouling (hr-ft 2--F/BTU)Shell-Side ho (BTU/hr-ft2-°F)

Tube-Side hi (BTU/hr.ft 2-.F)1/Wall Resis (BTU/hr.ft 2.-F)LMTD Correction Factor U Overall (BTU/hr.ft 2.°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (OF)Tube Skin Temp (OF)Proto-Power Calc: 97-201

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D Rev: A Page 10 of 11 244.9 212.0 169.1 190.6 177.4 100.0 147.2 123.6 133.3 0.002225-1,250.4 1,942.3 2,148.1 0.9196** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 12:08:55 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOO -LSCS -RHR Hx.CCM -Tube-side FF = 0.0020 07/14/98 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 (°F)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (OF)Input Fouling Factor 7,356.1 8,057.7 100.0 212.0 0.002801 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2-.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) 1/Wall Resis (BTU/hr-ft 2.0 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 (°F)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (fF)Bulk Visc (lbm/ft hr) Shell Skin Temp (°F)Skin Visc (Ibm/ft-hr)

Tube Temp In (°F)Density (lbm/ft 3) Tube Temp Out (°F)Cp (BTU/Ibm-°F)

Tav Tube (°F)K (BTU/hr-ft 0.F) Tube Skin Temp (°F)Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)4.03 1E+6 3.68E+6 1.618E+8 70.0 11,500.0 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-°F)

K (BTU/hr-ft.°F)

Shell-Side 3.81 6.700E+04 1.99 0.77 0.83 60.30 1.00 0.39 Tube-Side 6.72 6.139E+04 3.56 1.32 1.22 61.68 1.00 0.37 Overall Fouling (hrift 2.°F/BTU)Shell-Side ho (BTU/hr'ft 2-OF)Tube-Side hi (BTU/hr.ft 2.°F)I/Wall Resis (BTU/hr.ft 2.°F)LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)Shell Temp In (°F)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (°F)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (°F)Tube Skin Terp (°F)Proto--'ower Calc: 97-201

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D Rev: A Page 11 of 11 214.6 212.0 172.0 192.0 180.0 100.0 144.0 122.0 131.0 0.002801-1,255.7 1,925.7 2,148.1 0.9369** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Attachment E to Proto-Power Calculation 97-201 Revision A Proto-Power Calc: 97-201

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E Rev: A Page 1 of 10 16:32:07 F+PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -Service Margin -All Tubes 07/14/98 Calculation Specifications I'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 (OF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (OF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)7,356.1 8,057.7 100.0 212.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft2.°F)

Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2.°F)LMTD LMTD Correction Factor Effective Area (ft2)Overall Fouling (hr'ft2-°F/BTU)

Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (OF)Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (IF)Skin Visc (lbm/ft-hr)

Tube Temp In (OF)Density (lbm/ft')

Tube Temp Out (IF)Cp (BTU/lbm-°F)

Tav Tube (IF)K (BTU/hr-ft.°F)

Tube Skin Temp (IF)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (lbrn/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)4.03 1E+6 3.68E+6 1.677E+8 68.4 11,500.0 Overall Fouling (hr'ft 2.F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr.ft 2-°F)1/Wall Resis (BTU/hr-ft 2-IF)LMTD Correction Factor 0.002500, 1,253.0 1,934.1 2,148.1 0.9286 Property Shell-Side Tube-Side Velocity (ft/s) 3.80 6.73 Reynold's Number 6.668E+04 6.185E+04 Prandtl Number 2.00 3.53 Bulk Visc (lbm/ft-hr) 0.77 1.31 Skin Visc (lbmlft-hr) 0.84 1.21 Density (lbm/ft 3) 60.32 61.67 Cp (BTU/Ibm-°F) 1.00 1.00 K (BTU/hr-ft.°F) 0.39 0.37** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie U Overall (BTU/hr-ft 2.F) 229.4 Shell Temp In (°F) 212.0 Shell Temp Out (°F) 170.5 Tav Shell (IF) 191.3 Shell Skin Temp (0 F) 178.7 Tube Temp In (IF) 100.0 Tube Temp Out (0 F) 145.6 Tav Tube (IF) 122.8 Tube Skin TePrt-Power Calc: 97-201 132.2

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E Rev: A Page 2 of 10 16:31:12 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -Service Margin -53 Plugs 07/14/98 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 (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 (IF)7,356.1 8,057.7 100.0 212.0 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/hrft 2 0-OF)Tube-Side hi (BTU/hr-ft 2-OF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr.ft 2.0 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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ft hr) Shell Skin Temp (IF)Skin Visc (ibm/ft-hr)

Tube Temp In (OF)Density (Ibm/ft 3) Tube Temp Out (IF)Cp,(BTU/lbm.°F)

Tav Tube (IF)K (BTU/hr-ft-°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')4.031E+6 3.68E+6 1.637E+8 69.5 10,926.6 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (Ibm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm 0'F)K (BTU/hr'ft.°F)

Shell-Side 3.80 6.690E+04 2.00 0.77 0.84 60.31 1.00 0.39 Tube-Side 7.08 6.477E+04 3.55 1.32 1.21 61.68 1.00 0.37 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2-°F)Tube-Side hi (BTU/hr-f-'°F)

I/Wall Resis (BTU/hr-ft 2.°F)LMTD Correction Factor U Overall (BTU/hr-ft-°F)

Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (°F)Tube Temp In (°F)Tube Temp Out (°F)Tav Tube (IF)Tube Skin Tempý°F)Tb kroto-)owLer Calc: 97-201

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E Rev: A Page 3 of 10 230.7 212.0 171.5 191.8 179.0 100.0 144.5 122.3 131.4 0.002500 1,254.1 2,009.1 2,148.1 0.9344** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 16:32:44 PROTO-IHX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -Clean Margin -All Tubes 07/14/98.3 Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User 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 Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)7,356.1 8,057.7 100.0 212.0 Tube Temp Out (IF) Input Fouling Factor 0.000000 IF --Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hrIft 2.°F)Tube-Side hi (BTU/hirft7.°F)

Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2-OF)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 (OF)Prandtl Number Tav Shell (OF)Bulk Visc (lbm/ftrhr)

Shell Skin Temp (IF)Skin Visc (Ibm/ftrhr)

Tube Temp In (OF)Density (Ibm/ft 3) Tube Temp Out (OF)Cp (BTU/Ibm 0'F) Tav Tube (IF)K (BTU/hr-ft'°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)4.031E+6 3.68E+6 2.307E+8 52.0 11,500.0 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'°F)

K (BTU/hr-ft.°F)

Shell-Side 3.79 6.335E+04 2.12 0.82 0.96 60.50 1.00 0.39 Tube-Side 6.74 6.683E+04 3.25 1.21 1.06 61.53 1.00 0.37 Overall Fouling (hr'ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft2.oF)

Tube-Side hi (BTU/hr-ft 2-OF)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 (IF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (OF)Tube SkinTern, (F Trotu- ow er Calc: 97-201

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E Rev: A Page 4 of 10 539.6 212.0 154.9 183.5 160.4 100.0 162.8 131.4 147.3 0.000000&1,218.2 2,029.2 2,148.1 0.7148** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 16:33:25 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.CCM -Clean Margin -53 Plugs 07/14/98 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 (OF)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 7,356.1 8,057.7 100.0 212.0 0.000000 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.OF)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 2.0 F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr'ft2'OF/BTU)

Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Vise (Ibm/ft-hr)

Shell Skin Temp (OF)Skin Vise (Ibm/ft-hr)

Tube Temp In (OF)Density (lbm/ft')

Tube Temp Out (OF)Cpý (BTU/Ibm 0'F) Tav Tube (IF)K (BTU/hr-ft'°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)4.03 1E+6 3.68E+6 2.287E+8 52.5 10,926.6 Overall Fouling (hr-ft 2 0-F/BTU)Shell-Side ho (BTU/hr-ft 2 0.F)Tube-Side hi (BTU/hr.ft 2.OF)1/Wall Resis (BTU/hr-ft 2.0 F)LMTD Correction Factor 0.000000 1,218.3 2,110.6 2,148.1 0.7295 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Vise (Ibm/ft-hr)

Skin Vise (1bm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hr-ft-°F)

Shell-Side Tube-Side 3.79 7.09 6.345E+04 7.016E+04 2.11 3.25 0.81 1.22 0.96 1.07 60.49 61.53 1.00 1.00 0.39 0.37 U Overall (BTU/hr ft2-°F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin T 1 OOF0ower Calc: 97-201

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E Rev: A Page 5 of 10 546.0 212.0 155.4 183.7 160.1 100.0 162.2 131.1 146.8** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 16:26:29 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -Service Margin -All Tubes 07/14/98 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) 7,370.2 Shell Flow (gpm) Shell Flow (gpm) 7,372.0 Shell Temp In (0 F) Tube Inlet Temp (OF) 90.0 Shell Temp Out (OF) Shell Inlet Temp (OF) 120.0 Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)IF -Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 0-°F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr'ft 2.'F)Tube-Side hi (BTU/hr-ft 2-°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ftl.°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 (°F)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell ('F)Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (°F)Skin Visc (Ibm/ftlhr)

Tube Temp In (OF)Density (Ibm/ft')

Tube Temp Out (°F)Cpý (BTU/Ibm.°F)

Tav Tube (°F)K (BTU/hr'ft-0 F) Tube Skin Temp (°F)IF -Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)3.688E+6 3.687E+6 4.233E+7 18.5 11,500.0 Overall Fouling (hr.ft 2-°F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr'ft2.°F)

I/Wall Resis (BTU/hr ft 2.OF)LMTD Correction Factor 0.002500 971.5 1,661.9 2,148.1 0.9322 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbmift-hr)

Density (Ibm/ft 3)Cp (BTU/Ibm-'F)

K (BTU/hr'ft 0'F)Shell-Side Tube-Side 3.40 6.70 3.320E+04 4.713E+04 3.86 4.77 1.42 1.73 1.48 1.67 61.80 62.05 1.00 1.00 0.37 0.36 U Overall (BTU/hr ft 2.°F)Shell Temp In (fF)Shell Temp Out (OF)Tav Shell (°F)Shell Skin Temp (°F)Tube Temp In (fF)Tube Temp Out (°F)Tav Tube (fF)Tube Skin Tr/np ('F-roto-Power Calc: 97-201

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E Rev: A Page 6 of 10 213.4 120.0 108.5 114.3 110.2 90.0 101.5 95.7 98.5** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 16:29:58 49 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -Service Margin -53 Plugs 07/14/98.1 Calculation Specifications 11 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)7,370.2 7,372.0 90.0 120.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr.ft 2-0 F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr ft 2-OF)Tube-Side hi (BTU/hrift 2.°F)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 0.F/BTTJ)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 (OF)Skin Visc (Ibm/ft hr) Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (OF)CpI(BTU/Ibm-°F)

Tav Tube (IF)K (BTU/hr'ft' 0 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 2)3.688E+6 3.687E+6 4.13 1E+7 18.8 10,926.6 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.°F)

K (BTU/hr-ft.°F)

Shell-Side Tube-Side 3.40 7.05 3.324E+04 4.952E+04 3.86 4.78 1.42 1.73 1.48 1.68 61.80 62.05 1.00 1.00 0.37 0.36 Overall Fouling (hr.ft 2.°FIBTU)Shell-Side ho (BTU/hr-ft 2-0 F)Tube-Side hi (BTU/hr-ft 2-OF)1/Wall Resis (BTU/hr.ft 2.°F)LMTD Correction Factor U Overall (BTU/hr-ft 2'-F)Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Ta' Tube (IF)Tube Skin Temp (IF)Proto-Power Calc: 97-201

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E Rev: A Page 7 of 10 0.002500 971.9 1,729.7 2,148.1 0.9376 214.6 120.0 108.8 114.4 110.2 90.0 101.2 95.6 98.3** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 17:00:17 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -- Service Margin -38 Plugs 07/14/98 II 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 Shell Flow (gpm)Shell Temp In (OF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (°F)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (fF)Shell Inlet Temp (IF)7,370.2 7,372.0 90.0 120.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft'-°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.°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 (OF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibmý/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/Ibm'°F)

Tav Tube (IF)K (BTU/hr'ft 0'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)3.688E+6 3.687E+6 4.16E+7 18.7 11,088.9 Overall Fouling (hrift 2 0'F/BTU)Shell-Side ho (BTU/hr'ft 2 -F)Tube-Side hi (BTU/hr-ft 2.°F)I/Wall Resis (BTU/hr.ft 2 -F)LMTD Correction Factor 0.002500 971.8 1,709.9 2,148.1 0.9361 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbrnft')Cp (BTU/lbm'°F)

K (BTU/hr'ft 0'F)Shell-Side Tube-Side 3.40 6.95 3.323E+04 4.882E+04 3.86 4.78 1.42 1.73 1.48 1.68 61.80 62.05 1.00 1.00 0.37 0.36 U Overall (BTU/hr-ft 2.°F)Shell Temp In (IF)Shell Temp Out (°F)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (°F)Tav Tube (°F)Tube Skin Temp (IF)Proto-Power Calc: 97-201

Attachment:

E Rev: A Page 8 of 10 214.3 120.0 108.7 114.4 110.2 90.0 101.3 95.6 98.3** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 16:35:32 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -Clean Margin -All Tubes 07/14/98'I Calculation Specifications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User 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)Input Fouling Factor 7,370.2 7,372.0 90.0 120.0 0.000000 Fouling Calculation Results Shell Mass Flow (Ibm/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 0.F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2-OF)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 (IF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ft hr) Shell Skin Temp (IF)Skin Visc (Ibm/ft hr) Tube Temp In (OF)Density (lbm/ft) Tube Temp Out (IF)Cp (BTU/lbm'°F)

Tav Tube (IF)K (BTU/hr-ft 0'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 2)3.688E+6 3.687E+6 5.744E+7 14.4 11,500.0 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbmn/ft-hr)

Skin Visc (Ibm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr'ft-°F)

Shell-Side 3.40 3.253E+04 3.95 1.45 1.56 61.83 1.00 0.37 Tube-Side 6.70 4.820E+04 4.66 1.69 1.61 62.02 1.00 0.36 Overall Fouling (hr-ft 2'-F/BTU)Shell-Side ho (BTU/hr-ft 2 -F)Tube-Side hi (BTU/hr-ft 2-0 F)1/Wall Resis (BTU/hr-ft 2-°F)LMTD Correction Factor U Overall (BTU/hr ft 2.°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)Proto-Power Calc: 97-201

Attachment:

E Rev: A Page 9 of 10 457.0 120.0 104.4 112.2 105.4 90.0 105.6 97.8 102.3 0.000000 960.9 1,686.2 2,148.1 0.7586** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 16:34:35 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for E12-BOOI -LSCS -RHR Hx.SDC -Clean Margin -53 Plugs 07/14/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 7,370.2 Shell Flow (gpm) Shell Flow (gpm) 7,372.0 Shell Temp In (IF) Tube Inlet Temp (IF) 90.0 Shell Temp Out (IF) Shell Inlet Temp (OF) 120.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF) Input Fouling Factor 0.000000 IF- -Fouling Calculation Results Shell Mass Flow (lbrn/hr)

U Overall (BTU/hr-ft 2 0-F)Tube Mass Flow (Ibrn/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 0-°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 (°F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ft hr) Shell Skin Temp (IF)Skin Visc (lbm/ftlhr)

Tube Temp In (°F)Density (lbm/ft 3) Tube Temp Out (°F)Cp'(BTU/Ibm.°F)

Tav Tube (OF)K (BTU/hr'ft.°F)

Tube Skin Temp (°F)Extrapolation Calculation Results Shell Mass Flow (lbrn/hr)Tube Mass Flow (Ibrn/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/fr')Cp (BTU/Ibm 0'F)K (BTU/hr-ft 0'F)Shell-Side 3.40 3.256E+04 3.94 1.45 1.56 61.83 1.00 0.37 3.688E+6 3.687E+6 5.684E+7 14.6 10,926.6 Tube-Side 7.05 5.068E+04 4.66 1.69 1.61 62.02 1.00 0.36 Overall Fouling (hr-ft 2.°F/BTU) 0.Shell-Side ho (BTU/hr-ft 2"°F)Tube-Side hi (BTU/hrft 2 e-F)I/Wall Resis (BTU/hr'ft 2"-F)LMTD Correction Factor U Overall (BTU/hr.ft 2.°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (0 F_Proto-Power Calc: 97-201

Attachment:

E Rev: A Page 10 of 10 000009 960.9 1,755.7 2,148.1 0.7717 462.7 120.0 104.6 112.3 105.3 90.0 105.4 97.7 102.1** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Attachment F to Proto-Power Calculation 97-201 Revision A Proto-Power Caic: 97-201

Attachment:

F Rev: A Page 1 of 2 PROTO-HX T M Version 3.02 MODEL LASALLE STATION RESIDUAL HEAT REMOVAL HEAT EXCHANGER.

FILE NAME: E12-BOO1.PHX DATE LAST MODIFIED:

7/16/98 TIME LAST MODIFIED:

1:53:18 PM FILE SIZE: 960 KB Proto-Power Calc: 97-201

Attachment:

F 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. IAttachment A, A2 Analysis No.:'97-195 Revision:2 A01 Title: 3 Thermal Model of ComEd/LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers ECIECR No.: 4 388666 Revision:

000 Station(s):'

LaSalle Unit No.: 01 & 02 SafetylQA Class: SR System Code(s): DG Is this Design Analysis Safeguards Information?

Yes E] 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:

'1 NIA in its entirety.Description of Changes (list affected pages): " 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 A1-A2 Disposition of Changes: " See attached pages. The changes made are acceptable.

Preparer:'

$ -- e4 T-a'v%-oc(.

_______ a or_Print Name Sig Name Date Method of Review: " Detailed Review [ Alternate Calculations El Testing El Reviewer de- C-Ao O -- A t. /2/-Print Name Sign Name Da Review Independent review Peer review El Notes: 11 (For Extemar Analyses Only)External Approver:

-0 /1/IA Print Name Sign Name Date Exelon Reviewer'

/V/)Print Name Sign Name Date Exelon Approver:

_ __/__/__j_________

424___------__

"___ate /2--Pn-ntNahIre

-Sion Name rF 97-195 Rev. A01 Page 2 of 2 Purpose: The purpose of this revision is to verify that the 0(1)(2)DG01A coolers can remove the design heat load of 8,600,000 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)* Cooling water flow rate = 800 gpm (Reference 1)* Jacket water temperature for 0(1)(2)DG01A

= 190 OF (Reference 1)* Jacket water flow rate for 0(1)(2)DG01 A = 1100 gpm (Reference 1)* Fouling factor for 0(1)(2)DG01A

= 0.0022 hr.-f.°F/BTU (Reference 1)* 9 tubes plugged (5% tube plugging) (Reference 1)

References:

1. Design analysis97-195, Rev. A, up to and including Rev A00 2. EC 388666, Rev. 000 3. EC 384217, 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 I 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.Results I

Conclusions:

The 0(1)(2)DG01A coolers can remove the design heat load of 8,600,000 BTU/hr with the following conditions:

107 OF cooling water temperature

800 gpm cooling water flow 0 fouling factor of 0.0022 hr.ft 2 0 F/BTU* 9 tubes plugged* jacket water temperature of 190 OF* jacket water flow rate of 1100 gpm The total heat removed at these conditions is 8,727,760 BTU/hr, which provides 1.5% thermal margin over the design heat load. The benchmark of the model was shown to perform within 0.13% of the vendor data sheet, which is bounded by the 1.5% thermal margin. Note that the most recent thermal performance evaluation (Ref. 3)shows a maximum fouling factor of 0.000429 hr.ft.F/BTU, which shows that there is actually more margin than what is shown in this analysis.

The coolers are cleaned on a regular basis to maintain acceptable fouling factors.The previous maximum fouling factor of 0.0022 hr-ft 2-°F/BTU was used, which is the bounding fouling factor. This case is shown in Attachment A.Attachments:

A. Data Report for 0(1)(2)DG01A (2 pgs) 05-01-201 2 09:58:37 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-1002)

Commonwealth Edison Data Report for DGOIA -DG Jacket Water Cooler 0, IA, 2A DG -107 OF tube side, 800 gpm, 190 OF shell side, 1100 gpm, FF = 0.0022, 9 tubes plugged r_-Shell and Tube Heat Exchanger Input Parameters II Shell-Side Tube-Side Fluid Quantity, Total gpm 1,099.45 775.61 Mass Fluid Quantity, Total Ibm/hr 0.00 0.00 Inlet Temperature OF 190.00 100.00 Outlet Temperature OF 174.40 122.20 Fouling Factor hr.ft 2.°F/BTU 0.00278 0.00000 Shell Fluid Name Tube Fluid Name Design Q (BTU/hr)Design U (BTU/hr-ft 2.°F)Outside h Factor (Hoff)Fixed U (BTU/hr ft 2.°F)Fixed Area (Wt 2)Performance Factor (% Reduction)

Heat Exchanger Type Total Effective Area per Unit (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 K (BTU/hr-ft.OF)

Fresh Water Fresh Water 8,600,000 255.20 0.780339000 0 0.00 0.00 TEMA -E 471.23 0.981978184 0.00000 1 0.490000000 5.000 0.7500 Triangular 2 No 188 179 13.00 0.652 0.750 112.00 Lbc, Central Baffle Spacing (in)Lbi, Inlet Baffle Spacing (in)Lbo, Outlet Baffle Spacing (in)DotI, Tube Circle Diameter Bh, Baffle Cut Height (in)Ds, Shell Inside Diamter (in)Lsb, Diametral difference between Baffle and Shell (in)Ltb, Diametral difference between Tube and Baffle (in)Nss, Number Sealing Strips 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 0.000 97-195 Rev. A01 Attachment A Page Al of A2 05-01-2012 09:58:37 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-1002)

Page I Commonwealth Edison Calculation Report for DGO IA -DG Jacket Water Cooler 0, IA, 2A DG -107 OF tube side, 800 gpm, 190 IF shell side, I 100 gpm, FF = 0.0022, 9 tubes plugged 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 (IF)Shell Inlet Temp ('F)Input Fouling Factor 793.98 1,064.50 107.00 190.00 0.002200 11 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-ft2-°F)

Tube-Side hi (BTU/hr'ft 2"°F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hrft2"-OF)

LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-fl 2.°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 (lbnl/ft-hr)

Shell Skin Temp (OF)Skin Visc (lbm/ftfhr)

Tube Temp In (°F)Density (ibm/tI 3) Tube Temp Out (°F)Cp (BTU/Ibm.°F)

Tav Tube (IF)K (BTU/hr-fl.°F)

Tube Skin Temp (OF)I Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')Property Shell-Side Velocity (ft/s) 4.99 Reynold's Number 82,443 Prandtl Number 2.1391 Bulk Visc (lbm/ftfhr) 0.8239 Skin Visc (Ibm/ftfhr) 0.8810 Density (lbm/fP) 60.5342 Cp (BTU/Ibm.°F) 1.0024 K (BTU/hr-ftf.F) 0.3861 532,515.63 397,188.13 8,727,760.47 63.8 448.7 Tube-Side 8.61 75,787 3.7108 1.3722 1.2526 61.7424 0.9988 0.3694 Overall Fouling (hr-fl 2 2°F/BTU)Shell-Side ho (BTU/hr-ft'.°F)

Tube-Side hi (BTU/hr-ft 2.F)I/Wall Resis (BTU/hr ft2.°F)LMTD Correction Factor U Overall (BTU/hr-ft2.°F)

Shell Temp In (OF)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)0.002200 2,031.5 2,305.6 25,594.8 0.9851 309.6 190.0 173.7 181.8 172.1 107.0 129.0 118.0 127.9** Reynolds Number Outside Range of Equation Applicability With Zero Fouling The Test Heat Load Could Not Be Achieved 97-195 Rev, A01 Attachment A Page A2 of A2 CC-AA-309

-ATTACHMENT 1 -Design Analysis Approval Page I of 2 DESIGN ANALYSIS NO.: CaIc. # 97-195 PAGE NO. 1 Major REV Number: A Minor Rev Number: 00 S BRAIDWOOD STATION[ ] BYRON STATION DESCRIPTION CODE:(co0a)

CLINTON STATION DRESDEN STATION[X] LASALLE CO. STATION DISCIPLINE CODE: (COIl) M[ ] QUAD CITIES STATION Unit:[X]O

[X]I [X]2 [ ]3 SYSTEM CODE: (C011) DG TITLE: THERMAL MODEL OF COMED/LASALLE STATION UNIT 0, 1, AND 2 DIESEL GENERATOR JACKET WATER COOLERS[X I Safety Related [ Augmented Quality [ I Non-Safety Related ATTRIBUTES (C016)TYPE VALUE TYPE VALUE Elevation 710'Software PROTO-HX COMPONENT EPN: (C014 Panel) DOCUMENT NUMBERS: (C012 Panel) (Design Analyses References)

EPN TYPE Type/Sub Document Number Input (Y/N).ODGOIA H15 _/DCP EC# 334017 Y 1DG01A H15 I 2DGOIA H15 //REMARKS: NA E-Form CC-AA-309-1 v1.1 for use with CC-AA-309 Revision 1 and above.

CC-AA-309

-ATTACHMENT 1 -Design Analysis Approval Page 2 of 2 DESIGN ANALYSIS NO.97-195 REV: AO0 PAGE NO. 2 Revision Summary (including EC's incorporated):

Updated ProtoHX model for 104OF Service Water inlet temperature and calculated Unit 0, 1, and 2 DG Cooler thermal margins for different fouling factors and 5% tubes plugged.Electronic Calculation Data Files: ProtoHX 3.02. dg0la.phx.

704 KB. 04/14/2002.

4:01 pm (Program Name. Version, File Name extension/sizeldate/homrimin)

Design Impact review completed?

[ ] Yes [ X I N/A, Per EC#: 334017 (If yes, attach impact review sheet)Prepared by: Jeff W. VanStrien

..Print SOsD Reviewed by-. Brian L. Davenport

/ '\~ S2 Print I S.v Date Method of Review: [ X I Detailed [ ] Alternate

[ J Test ThisA v eds des: NbA ....'Suppkp~tei, ey***ReqPrint es N Extemal Oestin Analysis Review (Attachment 3 Attached)Reviewed by: Special,_RevewTeamLeadI I NoPrtnt SO Da*Approved by:. __Pnig Sin Date Do any ASSUMPTIONS

/ ENGINEERING JUDGEMENTS require later verification? ( ] Yes [XI No Tracked By: AT#, EC# etc.)_______

PrintI III:: Sig I I1 Page 2 of 2 E-Form CC-AA-309-1 v0. 1 for use with CC-AA-309 Revision 1 and above.

NES-G-14.01 Cor d Effective Date: 04/14/00 CALCULATION TABLE OF CONTENTS CALCULATION NO.97-195 REV. NO. AOO 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 DGO1A Al to A3 (CSCS=104 F @ Design Fouling)Attachment "B" -Proto-Hx CaIc. Report for DG01A B1 to B3 (CSCS=-104 F @ 2X Max. Tested FF)Attachment "C" -Proto-Hx Calc. Report for DG01A C1 to C3 (CSCS=104 F @ 2X Max. Tested FF, w\ 5% plugged)Attachment "D" -Proto-Hx Calc. Report for DG01A D1 to D3 (CSCS=104 F @ Max. Allowable FF, w\ 5% plugged)I &I F-FORM ColrEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO.97-195 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 Diesel Generator Coolers (ODG01A, 1DG01A, 2DG01A) 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 design fouling factor for use as a benchmark during Generic Letter 89-13 testing evaluations 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°F to 104°F and simulated for the following conditions: (Case 1) design fouling factor, (Case 2) twice the 'as-tested' fouling factor and (Case 3) twice the 'as-tested' fouling factor with a 5% tube plugging allowance.

The acceptance criteria will be for the thermal margin at Case 3 conditions to exceed the LaSalle design heat load of 8,600,000 BTU/hr (Ref. 1, Table 3-1).Additional conservatism was built into this acceptance criteria by assuming a 5% uncertainty in the Proto-HX heat transfer calculations.

The Reference 1 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.

3.0 ASSUMPTIONS

/ ENGINEERING JUDGMENTS The assumptions indicated in section 5.0 of Reference 1 are still valid.Note: The density of water at 104 0 F is 61.94 lb/ft 3 (per steam tables), this is an insignificant change to the density shown in table 4-1 of Ref. 1 for 100°F, the tube side volumetric flow rate correction made in Ref. 1 is still valid.4.0 DESIGN INPUTS The design inputs consist of References 1 and 2 listed below.

5.0 REFERENCES

1. Calculation No.97-195, Rev. A, "Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers".2. Calculation L-00221 1, Rev. 0, "2DG01A, 2A Emergency Diesel Generator Cooler Thermal Heat Transfer Performance" 3. "Standards of the Tubular Exchanger Manufacturers Association" (TEMA), Seventh Edition, 1988.I E-FORM I Cornd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO.97-195 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 0 F. At this temperature, a maximum fouling factor of 0.002782 hr*ft 2*OF/BTU was calculated within reference 1 while maintaining a heat transfer rate of 8,600,000 BTU/hr (Ref. 1, Table 6-3). This is the LaSalle Station Design Heat Load for 110% power operating conditions.

Thus, it presents the appearance that no thermal margin exists at these conditions.

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: ThermalM argin x 100% = %ThermalM arg in Re quiredHeatLoad

[Equation 2]Case 1 When the service water inlet temperatureis increased to 104 0 F for the same fouling factor (0.002782 hr*ft2*OF/BTU), heat transfer reduces to 8,234,000 BTU/hr, which is 4.3% below the design heat load of 8,600,000 BTU/hr for 110% power operating conditions

[Attachment A]. With the Diesel Generator operating at 100% power, its design heat load is 7,800,000 BTU/hr resulting in a 5.6% thermal margin at a fouling factor of 0.002782 hr*ft 2*OF/BTU.Case 2 Regular cleaning and testing of these heat exchangers limits the amount of fouling well below the values assumed above. The heat exchanger performance data taken under the G.L. 89-13 program here at LaSalle demonstrates a maximum measured fouling factor of 0.000534 hr*ft 2*OF/BTU (Ref. 2, page 9). For conservatism, this value was doubled to 0.001068 hr*ft 2*OF/BTU and simulated with 104 0 F service water inlet temperature.

The result was a heat transfer of 12,520,000 BTU/hr for a 45.6% thermal margin at 110% power operating conditions

[Attachment B].Case 3 With additional conservatism included by adding a plugging allowance of 9 tubes, 5% of the total, in the heat exchanger and running the model again at the above fouling factor (0.001068 I E-FORM I NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE I CALCULATION NO.97-195 REV. NO. A00 PAGE NO. 6 of 6 hr*ft 2*OF/BTU) and inlet temperature (104 0 F) results in a 12,210,000 BTU/hr heat transfer rate, a 42% thermal margin above the worst case heat load [Attachment C].A final case was evaluated in which the maximum fouling factor was found to be 0.002200 hr*ft 2*OF/BTU for the 110% power operating condition, 104 0 F inlet temperature and with a 5%plugging allowance

[Attachment D]. The resulting heat transferred of 9,032,000 BTU/hr accommodates the design heat load of 8,600,000 BTU/hr including analytical model uncertainty.

This is judged to be a reasonably conservative fouling factor since it is slightly higher than the typical fouling factors stated in Ref. 3, page 215. The LaSalle lake water quality will meet or exceed the "River Water Fouling Factor" (at a velocity greater than 3 ft/sec) given in this reference.

The lake water passes through strainers and is chemically treated for silt control and scale prevention.

7.0

SUMMARY

AND CONCLUSIONS The Diesel Generator Jacket Water Cooler Model was found to have adequate thermal margin for a maximum lake temperature of 104 0 F even when operated at 110% power if fouling is less than 0.002200 hr*ft 2*°F/BTU. This fouling factor has been determined to be an acceptable benchmark value that can be used in Generic Letter 89-13 testing evaluatiohs of this model heat exchanger.

8.0 ATTACHMENTS

Attachment "A" -Proto-Hx Calc. Report for DG01A (CSCS=104 F @ Design Fouling)Attachment "B" -Proto-Hx Calc. Report for DG01A (CSCS=104 F @ 2X Max. Tested FF)Attachment "C" -Proto-Hx Calc. Report for DG01A (CSCS=104 F @ 2X Max. Tested FF, w\ 5% plugged)Attachment "D" -Proto-Hx Calc. Report for DG01A (CSCS=104 F @ Max. Allowable FF, w\ 5% plugged)Final Page I E-FORM I ComEd CALCULATION NO.97-195 REVISION NO. AOO PAGE NO. Al of A3 Attachment "A" Proto-Hx Calc. Report for DG01A (CSCS=104 F @ Design Fouling)Il E-FORM 09:10:43 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler CSCS= 104 F @P Design FF 04/12/02 Shell and Tube Heat Exchanger Input Parameters Shell-Side Tube-Side Fluid Quantity, Total gpm 1,099.45 775.61 Inlet Temperature OF 190.00 100.00 Outlet Temperature OF 174.40 122.20 Fouling Factor 0.00278 0.00000 Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/hr)Design Heat Trans Coeff (BTU/hr-fV-°F)

Emprical Factor for Outside h Performance Factor (% Reduction)

Fresh Water Fresh Water 8,600,000 255.20 0.780339000 0.00 TEMA-E 471.23 0.981978184 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-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 1 0.490000000 5.000 0.7500 Triangular 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 Calculation No.97-195 Revision No. AOO Attachment A Page No. As 09:10:43 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGO 1 A -DG Jacket Water Cooler CSCS= 104 F @ Design FF 04/12/02 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 (IF) 104.0 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.-F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-ft 2-OF)Tube-Side hi (BTU/hrft 2-OF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft2-°F)

LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr.ft 2 .FIBTT 1)Property Shell-Side Tube-Side Calculation No.97-195 Velocity (ft/s) Shell Temp In (IF) Revision No. AOO Reynold's Number Shell Temp Out (IF) Attachment A Prandtl Number Tav Shell (IF) Page No. 43 of Bulk Vise (lbm/ft-hr)

Shell Skin Temp (IF)Skin Visc (Ibm/lfthr)

Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (IF)Cp (BTU/lbm-'F)

Tav Tube (IF)K (BTU/hr'ft 0'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)5.325E+5 3.978E+5 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (Ibm/ft-hr)

Density (Ibm/ft')Cp (BTUilbm'°F)

K (BTU/hr'ft

' F)Shell-Side 4.99 8.270E+04 2.13 0.82 0.87 60.52 1.00 0.39 8.234E+6 67.9 471.2 Tube-Side 8.21 6.978E+04 3.86 1.42 1.30 61.80 1.00 0.37 Overall Fouling (hr-ft 2-°F/BTU)Shell-Side ho (BTU/hr.ft2-°F)

Tube-Side hi (BTU/hr-ft 2.F)1/Wall Resis (BTU/hr.0 f-°F)LMTD Correction Factor U Overall (BTU/hr. ft 2-°F)Shell Temp In (fF)Shell Temp Out (fF)Tav Shell (°F)Shell Skin Temp (fF)Tube Temp In (fF)Tube Temp Out ('F)Tav Tube (°F)Tube Skin Temp ('F)0.002782 7 2,035.7 2,177.8 25,594.8 0.9884 260.4 190.0 174.6 182.3 173.6 104.0/124.7 114.4 123. 7** Revnolds Number Outside Range of Equation Applicability

!I With Minimum Fouling The Test Heat Load Could Not Be Achier, CornEd CALCULATION NO.97-195 REVISION NO. AOO PAGE NO. B1 of B3 Attachment "B" Proto-Hx Calc. Report for DG01A (CSCS=104 F @ 2X Max. Tested FF)I E-FORM I 09:30:07 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DG0IA -DG Jacket Water Cooler CSCS = 104 F @ 2X NDIT FF 04/12/02 Shell and Tube Heat Exchanger Input Parameters Shell-Side Tube-Side Fluid Quantity, Total gpm 1,099.45 775.61 Inlet Temperature OF 190.00 100.00 Outlet Temperature OF 174.40 122.20 Fouling Factor

0.00278 0.00000 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)

Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Fresh Water Fresh Water 8,600,000 255.20 0.780339000 0.00 TEMA-E 471.23 0.981978184 Number of Shells per Unit Shell Minimum Area Shell Velocity (if/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 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 1 0.490000000 5.000 0.7500 Triangular 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 Calculation No.97-195 Revision No. AOO Attachment

_N Page No. B2 of 633 09:30:07 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 104 F (a), 2X NDIT FF 04/12/02 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 795.3 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In (°F) Tube Inlet Temp (OF) 104.0 Shell Temp Out (OF) Shell Inlet Temp (OF) 190.0 Tube Flow (gpm)Tube Temp In (°F)Tube Temp Out (OF)

Input Fouling Factor 0.001068 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-ft 2 0-F)Tube-Side hi (BTU/hr-ft 2-0 F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2.°F)LMTD LMTD Correction Factor Effective Area (fW)Overall Fouling (hr-ft 2.°F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF) Calculation No.97-195 Reynold's Number Shell Temp Out (OF) Revision No. AOO Prandtl Number Tav Shell (OF) Attachment 0 Bulk Vise (lbm/fr-hr)

Shell Skin Temp (OF) Page No. S $ of g-Skin Vise (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 (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 3.978E+5 1.252E+7 ..58.4 471.2 Overall Fouling (hr-ft 2-°F/BTU)Shell-Side ho (BTU/hr.ft 2.-F)Tube-Side hi (BTU/hr ft 2.0 F)I/Wall Resis (BTU/hr ft 2 -F)LMTD Correction Factor U Overall (BTU/hr-ft 2-°F)0.001068 -2,006.8 2,250.9 25,594.8 0.9628 472.5 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Vise (Ibm/ft hr)Skin Vise (Ibm/ft'hr)

Density (Ibm/fi 3)Cp (BTU/lbm-'F)

K (BTU/hr'ft'°F)

Shell-Side Tube-Side 4.98 8.22 8.047E+04 7.349E+04 2.19 3.64 0.84 1.35 0.93 1.19 60.61 61.72 1.00 1.00 0.39 0.37 Shell Temp In (°F)Shell Temp Out (OF)Tav Shell ('F)Shell Skin Temp (°F)Tube Temp In (fF)Tube Temp Out (OF)Tav Tube (OF)Tube Skin Temp ("F)190.0 166.5 178.3 164.5 104.0 135.5 119.8 133.9** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie',

CornEd CALCULATION NO.97-195 REVISION NO. AOO PAGE NO. C1 of C3 Attachment "C" Proto-Hx Calc. Report for DG01A (CSCS= 104 F @ 2X Max. Tested FF & 5% plugged)I E-FORM I 09:31:56 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler CSCS=104 NDIT FF, 5% plugged 04/12/02 Shell and Tube Heat Exchanger Input Parameters Fluid Quantity, Total 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 2 F)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 (ftls)Tube Pitch (in)Tube Pitch Type Shell-Side Tube-Side 1,099.45 775.61 190.00 100.00 174.40 122.20 0.00278 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 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-°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 188 179 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 Calculation No.97-195 Revision No. AOO Attachment CU Page No. C-2. of C-1 09:31:56 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGO 1 A -DG Jacket Water Cooler CSCS=I04 F@2X NDIT FF, 5% plugged 04/12/02 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions

-* Fouling Was Input by User 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 (IF) 104.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 190.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (°F) -4 Input Fouling Factor 0.001068 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hrwft 2-°F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr'fi 2"-F)Tube-Side hi (BTU/hr-ft 2-°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr'ft2-°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) Calculation No.97-195 Reynold's Number Shell Temp Out (°F) Revision No. AOO Prandtl Number Tav Shell (OF) Attachment C Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (°F) Page No. C_ 3 ofC _3 Skin Visc (lbm/ft-hr)

Tube Temp In (°F)Density (lbm/ft 3) Tube Temp Out (°F)Cp (BTU/Ibm 0'F) Tav Tube (°F)K (BTU/hr'ft-'F)

Tube Skin Temp (°F)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 (lbm/ft.hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm 0'F)K (BTUi/hr-ft-'F)

Shell-Side 4.98 8.063E+04 2.19 0.84 0.93 60.61 1.00 0.39 5.325E+5 3.978E+5 1.221E+7 59.1 448.7 Tube-Side 8.63 7.690E+04 3.66 1.36 1.19 61.72 1.00 0.37 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-1ft 2-F)Tube-Side hi (BTU/hr ft 2-OF)I/Wall Resis (BTU/hrft 2.°F)LMTD Correction Factor U Overall (BTU/hr-ft 2.-F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube ('F)Tube Skin Temp (CF)0.001068 2,007.6 2,335.8 25,594.8 0.9655 476.7 190.0 167.1 178.6 164.5 104.0 134.7 119.4 133.3** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test bleat Load Could Not Be Achie\

CornEd CALCULATION NO.97-195 REVISION NO. AOO PAGE NO. D1 of D3 Attachment "D" Attachment "D" -Proto-Hx Calc. Report for DG01A (CSCS=104 F @ Max. Allowable FF, w\ 5% plugged)I E-FORM I 09:43: 13 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS= 104 F(iMax. FF, 5% plugged 04/12/02 Shell and Tube Heat Exchanger Input Parameters Shell-Side Tube-Side Fluid Quantity, Total gpm 1,099.45 775.61 Inlet Temperature OF 190.00 100.00 Outlet Temperature OF 174.40 122.20 Fouling Factor , 0.00278 0.00000 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)

Fresh Water Fresh Water 8,600,000 255.20 0.780339000 0.00 TEMA-E 471.23 0.981978184 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 (fIt)Tube Inside Diameter (in)Tube Outside Diameter (in)Tube Wall 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 1 0.490000000 5.000 0.7500 Triangular 2 No 188 179 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 Calculation No.97-195 Revision No. AOO Attachment Page No. D'. of (A3 09:43:13 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGO 1 A -DG Jacket Water Cooler CSCS=104 F(KMax. FF. 5% oluaed 04/12/02 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions , Fouling Was Input by User 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 (IF) 104.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 190.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF) .9 Input Fouling Factor 0.002200 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-ft 2-OF)Tube-Side hi (BTU/hr.ft 2-OF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hrft 2 0-OF)LMTD LMTD Correction Factor Effective Area (fIt)Overall Fouling (hr.ft 2.0 F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF) Calculation No.97-195 Reynold's Number Shell Temp Out (OF) Revision No. AOO Prandtl Number Tav Shell (IF) Attachment D Bulk Vise (lbm/fthr)

Shell Skin Temp (OF) Page No. 13 of D3 Skin Vise (lbm/ftfhr)

Tube Temp In (IF)Density (lbm/ft')

Tube Temp Out (OF)Cp (BTU/lbm-'F)

Tav Tube (IF)K (BTU/hr'ft-F)

Tube Skin Temp (IF)IF -Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/br)LMTD Effective Area (ft 2)5.325E+5 3.978E+5 9.032E+6 66.1 448.7 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Vise (lbm/ft hr)Skin Visc (lbm/ft-hr)

Density (lbm/fty)Cp (BTU/lbm 0'F)K (BTU/hr-ft 0'F)Shell-Side Tube-Side 4.99 8.62 8.228E+04 7.401E+04 2.14 3.82 0.83 1.41 0.89 1.28 60.54 61.78 1.00 1.00 0.39 0.37 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2-°F)Tube-Side hi (BTU/hr-ft 2.OF)I/Wall Resis (BTU/hr-fi 2-°F)LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)Shell Temp In (IF)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (IF)Tube Temp In (°F)Tube Temp Out (IF)Tav Tube (fF)Tube Skin Temp (fF)0.002200'2,029.5 2,279.5 25,594.8 0.9852 309.0 190.0 173.1 181.5 171.5 /104.0 /126.7 115.4 125. 7** Reynolds Number Outside Range of Equation Applicability H With Minimu, m Fouling The Test Heat Load Could Not Be Achie',

PROTO-POWER CORPORATION CALCULATION TITLE SHEET CLIENT: Commonwealth Edison / LaSalle County Station PROJECT: COMED / LaSalle Station GL 89-13 Program CALCULATION TITLE: Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers CALCULATION NO.: 97-195 FILE NO.: 31-003 COMPUTER CODE & VERSION (if applicable):

PROTO-HX ver 3.02 REV TOTAL NO. OF ORIGINATOR/DATE VERIFIER/DATE APPROVALDATE PAGES A 3 _________

81 als .Philpo Page i of v Form No.: P1050101 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION C NO 140.97-195 V A PAGE ii OF v GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 RIfED B! S. Ingalls JOB -0.31-003 c""ENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Revision Historv 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.97-195 REV A PAGE iii OF V GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls JOB NO.31-003 CLIINT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers C.Al ,C1JATION VERIFICATION FORM REVIEW METHOD: Approach Checked: Logic Checked: Arithmetic Checked: Alternate Method (Attach Brief Summary)Computer Program Used (Attach Listing)Other N/A E]N/A [El N/A N/A N/A EXTENT OF VERIFICATIO4N:

Complete Calculation:

R/Revised areas only: f]El Other (describe below): LI r- /A[I*Errors Detected Mi'w1f-4O a4ormJ*Error Resolution

Other Comments*Extra References Used*(Attach extra sheets if needed)CALCULATION FOUND TO BE VALID AND CONCLUSIONS TO BE CORRECT AND REASONABLE:

IDV Signature: "Akt/. L A Initials: Jtli M, Printed Name: Date: U Form No.: P1050103 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION o- 97-195 REV A PAGE iv oP V GROTON, CONNECTICUT D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls JOB O.31-003 C.IENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers TABLE OF CONTENTS CALC TITLE SHEET ...............................................................................................

I REVISIO N H ISTORY ....................................................................................................

II CALC VERIFICATION SHEET ..................................................................................

III TABLE OF CONTENTS ..........................................................................................

IV LIST OF ATTACHMENTS

.......................................................................................

V Total number of pages in Preface of Calc 5 1. PUR PO SE .........................................................................................................................

1 2. BACKGROUND

..........................................................................................................

1 3. DESIG N INPUTS .............................................................................................................

1 3.1 .LASALLE STATION REFERENCE CONDITIONS

.............................................................

2 3.2.CONSTRUCTION D ETAILS ...........................................................................................

2 3.3.P ERFORM ANCE D ETAILS ...........................................................................................

3 4. APPROACH .....................................................................................................................

4 4.1 .PROTO-HXTm PARAMETER CALCULATION

..............................................................

4 4.2.PROTO-HXTM FLOW RATE INPUTS ...........................................................................

4 4.3.PROTO-HXTM EXTRAPOLATION METHOD ..............................................................

5 5. ASSUM PTIONS ...............................................................................................................

5 6. ANALYSIS ........................................................................................................................

5 6. I.PROTO -HX Tm M ODEL ............................................................................................

5 6.2.HEAT EXCHANGER FOULING FACTOR LIMIT .............................................................

6 6.3.FOULING SENSITIVITY

.................................................

7 6.4.THERMAL MARGIN ASSESSMENT

..............................................

8 6.5.MINIMUM SERVICE WATER FLOW RATE ...................................

9 7. CO NCLUSIO N ...............................................................................................................

11 7.1 .PR O T O -H X Thf M O DEL ...............................................................................................

11 7.2.HEAT EXCHANGER FOULING FACTOR LIMIT ...................................

11 7.3.FoULING SENSITIVITY

.........

.............................................

11 7.4.THERMAL MARGIN ASSESSMENT

........................................

I1 7.5.MINIMUM SERVICE WATER FLOW RATE .................................

11 8. REFERENC ES ...............................................................................................................

12 Total number of pages in Body of Calc 12 Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CA 00.97-195 Rwv A PAGE V OF v GROTON, CONNECTICUT ,O,,UA-To3 D. Phyfe DATE 6/29/98 1F1'Ea S. Ingalls o 31-003 C,!'t COMED / LaSalle County Station PPWEC- COMED / LaSalle Station GL 89-13 Program TrTLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers LIST OF ATTACHMENTS Attachment Subject Matter Total Pages A Proto-Power Calc.97-195, Rev. A; 3 Vendor Supplied Hx. Information B Proto-Power Calc.97-195, Rev. A; 3 Sargent & Lundy Specification J-2544 C Proto-Power Calc.97-195, Rev. A; 7 Form N- I Manufacturer's Data Report for Nuclear Vesselsj D Proto-Power Calc.97-195, Rev. A;LaSalle Station UFSAR Sections: 9.2.1.1.1, 9.5.5.1.1, FSAR Q40.92 5 E Proto-Power Calc.97-195, Rev. A;PROTO-HXTm Calculation Reports and Model Data Sheets 13 F Proto-Power Calc.97-195, Rev. A; 6 PROTO-HXTm Calculation Reports for Fouling Sensitivity G Proto-Power Calc.97-195, Rev. A; 17 PROTO-HXTm Calculation Reports for Minimum Service Water Flow H Proto-Power Calc.97-195, Rev. A; 2 PROTO-HX T M Version 3.02 Model (and disk)73 Complete Calc (total number of pages)Form No.: P1050104 Rev. 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION 7A- NO.97-195 REv A PAGE: 1 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 VERIFIE.D BY S. Ingalls JOB NO.31-003 COMED / LaSalle County Station ""' COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers 1. PURPOSE The purpose of this calculation is to develop a thermal performance analysis model for the Commonwealth Edison (CoinEd) LaSalle Station, Standby Diesel Generator heat exchanger.

This model is to be used for the analysis of heat exchanger thermal performance test data as part of the LaSalle Station heat exchanger testing program.Once developed, the model is used to evaluate the thermal margin of the heat exchanger at the LaSalle Station Reference Conditions as currently defined in the LaSalle design and licensing basis.The thermal performance model documented in this calculation has been created and used with PROTO-HX, Version 3.02. The model can be used with previous versions of PROTO-HX and produce identical results as long as the following restrictions are upheld:* Versions prior to version 3.02 will not calculate a negative fouling factor when calculating the fouling factor based on test data.* Shell and tube heat exchangers analyzed in Version 3.0 or earlier must have a tube-side Reynolds Number greater than 10,000 (i.e., fully developed turbulent flow).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:* Water (fresh and salt): 32-500'F 2. BACKGROUND LaSalle Station is in the process of implementing a heat exchanger thermal performance monitoring program in response to the requirements of NRC Generic Letter 89-13 (Reference 8.2). Development of an analytical model in PROTO-HXTM, Version 3.02, will allow timely analysis of data resulting from the test program.3. DESIGN INPUTS The PROTO-HXTM program 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, 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-HXTM Version 3.02 was verified and approved for use as documented in Reference 8.10.The design inputs for this calculation consist of the heat exchanger design basis requirement (Section 3.1), construction details (Section 3.2), and performance specifications (Section 3.3)provided by the Hx manufacturer data sheets or design documents as referenced.

Construction Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CA=C No.97-195 REV A PACE 2 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DAT 6/29/98 VERIFIED BY S. Ingalls JOB NO.31-003 EcLE.rr COMED / LaSalle County Station PRoJEe' COMED / LaSalle Station GL 89-13 Program TITL Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers details give the necessary information for model construction while performance specifications provided by the manufacturer are used to benchmark the model.Thermal performance of the Standby diesel generator heat exchanger is assessed in this calculation at the LaSalle Station Reference Conditions of Section 3.1 with all tubes active at 100% and 110% of rated load. No tube plugging margin is considered.

3.1. LASALLE STATION REFERENCE CONDITIONS Table 3-1 describes the performance requirement of the jacket water cooler. These conditions ensure that the engine operating temperature range will not be exceeded.Table 3-1 LaSalle Station Reference Conditions 3.2.Parameter Value Reference Heat Load at 100% power/I 10% power (BTU/hr) 7,800,000

/ 8,600,000

8. I, 8.4 Shell-Side Flow Rate (gpm) 1,100 8.4 Shell-Side Inlet Temperature

(°F) 190 8.4 Tube-Side Flow Rate (gpm) 800 8.1, 8.4 Tube-Side Inlet Temperature

(*F) 100 8.1 CONSTRUCTION DETAILS Table 3-2 Construction Details Parameter Value Reference Heat Exchanger Type AEW 8.11 Total Effective Area per unit (ft 2) 479 8.11 Number of Shells per unit I 8.11 Shell Velocity (ft/sec) 5 8.11 Tube Passes per shell 2 8.11 U-Tubes (yes or no) No 8.11 Total Number of Tubes 188 8.11 Tube Length (ft) 13 8.11 Tube Inside Diameter (in) 0.652 (18 BWG) 8.11 Tube Outside Diameter (in) 0.750 8.11 Stationary Tubesheet Thickness (in) 0.938 8.3 Floating Tubesheet Thickness (in) 1.875 8.3 Tube Wall Conductivity (BTU/hr-ft-°F) 112 (Arsenical Cooper) 8.9, (8.11)Tube Pitch (in) 0.750 8.11 Form No.: P1050105 Rev.: 10 Date: 10/21/9 Ref.: P&I 5-1 PROTO-POWER CORPORATION ch_ "D0.97-195 REv A PAGE 3 OF 12 GROTON, CONNECTICUT D. Phyfe DATE 6/29/98 VERIFiED BY S. Ingalls JOB NO.31-003 COMED / LaSalle County Station PEcT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Table 3-2 Construction Details Parameter Value Reference Pitch Type Triangle 8.11 The vendor data sheet shows the effective area as 479 ft 2 , however, based on the outside tube diameter and tube length, this value is a gross area (Agr) approximation:

A gr = (number of tubes). (Lt,.b -(tube outside circ.) Equation 1 Agr =188-13ft-n.

(.750f =479.878ft 2 g' ( 1 2 % t The effective area (Aeff) can be approximated as follows: Aei- = (numberof tubes). (L,u, -Tf.xed -Tfloalig ). (tube outside circ.)Equation 2 Acfr=188.(13ft

-(0-938 in+1.875in)

.*7t* i =471.2251ft 2 12% ) , 12% )where: A -Heat Exchanger Gross Area, ft 2 A e'ff -Heat Exchanger Effective Area, ft 2 L tube -Tube Length, ft Tfixed Fixed End Tubesheet Thickness, ft (0.938" per Reference 8.3)

-Floating End Tubesheet Thickness, ft (1.875" per Reference 8.3)The data sheet value for the effective area will be used in the model benchmarking process. However, for PROTO-HXTM runs of the Standby heat exchanger model the above calculated effective area will be used.3.3. PERFORMANCE DETAILS Table 3-3 Performance Details Parameter Value Reference Shell Side Fluid Type Jacket Water (Fresh) 8.11 Total Fouling Factor (Design) 0.00285 8.11 Shell Side Fluid Flow Rate (lb/hr) 550,000 8.1 Shell Side Inlet Temperature (0 F) 190 8.11 Shell Side Outlet Temperature

('F) 174.4 8.11 Tube Side Fluid Type Service Water (Fresh) 8.1/8.7 Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION C- NO.97-195 RE A PAGE 4 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls JoE NO.31-003 CLIEN COMED / LaSalle County Station ""' COMED / LaSalle Station GL 89-13 Program TITLE Thliermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Table 3-3 Performance Details Parameter Value Reference Tube Side Fluid Flow Rate (lb/hr) 38S,000 8.11 Tube Side Inlet Temperature (TF) 100 8.11 Tube Side Outlet Temperature

('F) 122.2 8.11 Hx. Design Q -Service (BTU/hr) 8,600,000 8.11 Hx. Design U -Service (BTU/hr-ft 2-0 F) 255.2 8.11 4. APPROACH This calculation utilizes plant/vendor fabrication specifications provided in Attachment (A) to develop a thermal performance prediction model for the LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers. The calculation then benchmarks the model by comparing the heat transfer rate calculated by PROTO-HXTM Version 3.02 with the manufacturer's specifications for thermal performance.

4.1. PROTO-HXTM PARAMETER CALCULATION Minimum Shell Area The minimum shell area is calculated using either the shell side velocity or a shell geometry.

The preferred method of calculation is using the shell side velocity.

Reference 8.11 gives the shell side velocity to be 5 ft/sec at a flow rate of 1100 gpm. Based on this velocity and flow rate the minimum shell side area is calculated by PROTO-HXTM to be 0.490 ft 2.Outside H Factor (Hof!)The Outside H Factor is a multiplier, with value less then 1.0, used to reduce the ideal shell side film heat transfer coefficient.

The Outside H Factor accounts for inefficiency in the heat exchanger.

Using the back calculation method, based on the design overall heat transfer coefficient, the Outside H Factor was calculated by PROTO-HXTM to be 0.780.4.2. PROTO-HXTM FLOW RATE INPUTS Volumetric flow rates are converted to mass flow rates based on a set temperature of 60'F in PROTO-HX T M.Therefore, the actual PROTO-HX T M inputs have to be adjusted to give the correct mass flow rate. The PROTO-HXTM input is adjusted using the ratio of the actual water density and the density of water at 60'F.QP1X =Q IP ,P60-F Equation 3 Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION REV. 9195 ..A PAGE oF 12 GROTON, CONNECTICUT

..I.'.. D. Phyfe 'A.E.6 / 29/ 98 VERIFIEDB S. Ingalls JOB .3.1-003 COMED./ LaSalle County Station COMED LaSalle StationtGL 89-13 Program TITE" Thermal Model of COMED / LaSalle Statio0nUniiti0, ,:, and 2 Diesetl Generator Jacket Water Coolers Table 4-1 PROTO-HXr~m Flow RatetInputs__________

Parameter Density (lb/ft 3) ActualiFlow (gpm) PROTO HXTm In put (gpm).'Tube-side, 100'F 61.994 (8.12) 800 .795.25 Shell-side, 190OF .60.349 (8.12) 1,100 1,064.495 PRaoT-Hx-', :60 ý162364 (.2*5.4.3. PROTO-HXTm EXTRAPOLATION METHOD All calculations performed for this calculation are bas0e.d:on.

a .constant.

cold inlet temperature.

This allows the comparison of the heat ` transfer, outlet temperatures,.l log mean temperature difference (LMTD), and overall heat transfer coefficient, There is no comparison of the overall heat transfer coefficient in. thedesign case since PROTO-:HX

" used the data sheet value of the overall: heat.transfer:

coefficient to: calculate the shell:s ide film heat transfer coefficient.:

ASSUMPTIONS

... ...... ..5.1. The vendor data sheet (Reference 8.11) is.. considered kan accurate reflection of the vendor's expectation for the heat exchanger's..

outside film heat:transfer coefficient.

Therefore, the benchmarking of the PROTO-HXTM.

model.to the. vendor data sheet will...ensure* that the PROTO- "X .calculated outside filmih heat transfer coefficient is..consistent with the vendor's expectation..

The PROTO-HX T M model is benchinarked with the vendor data sheet effective area. However, calculations perormed with the model. use the 'effetive area determinedin Setion 3.2. .Future validation of this assumption is not reequ.ired.

6. ANALYSIS 6.1. PROTO.HXM MODEL.Table..6-1 shows the.PROTO-HXTM benchmnarking of the Jacket Water Cooler for theýStandby Diesel Generator..

The PROTO-HX T M reports can be found in Attachment.E.

Table 671. Model Benchmark Correlation Parameter PROTO-HXTM Data Sheet Percent Difference Effective.Area ft 2: 479 .479 0.00 %Shell Side. Outlet Temp, ..:. 174.4 1 744 0.00 %Tube Side Outlet Termnp, 0 F. 122.2... .122.2 0.00 %Heat Transferred, BTU/hr 8,589,000

$8600,000

-0.13 %.Corrected LMTD 70.3 70.2 0.14 %[F:orm No.: P105010 Rev.: 10 Date: 10/21197 Ref.: P&l 5-1 PROTO-POWER CORPORATION

--' o 97-195 rEv A PAGE 6 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 ,ERIFIEo BY S. Ingalls JOB NO.31-003 cL,¢I COMED / LaSalle County Station COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of CONMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Table 6-2 shows the PROTO-HXTM results for the heat exchanger design conditions using the corrected effective area, Section 3.2. The PROTO-HXTm reports can be found in Attachment E.Table 6-2 Model Design Correlation Parameter PROTO-HXT'1 Data Sheet Percent Difference Effective Area, ft 2 471.2 479 -1.63 %Shell Side Outlet Temp, 'F 174.6 174.4 0.11 %Tube Side Outlet Temp, *F 121.9 122.2 -0.25%Heat Transferred, BTU/hr 8,481,000 8,600,000

-1.38%Corrected LMTD 70.5 70.2 0.43 %All PROTO-HX T M calculations performed with the Standby Jacket Water Cooler model will use the effective area of 471.23 ft 2.This change is made to the PROTO-HX T M heat exchanger data sheet as shown in Attachment E.6.2. HEAT EXCHANGER FOULING FACTOR LIMIT In order for the jacket water cooler to meet the Reference Conditions (Table 3-1) the fouling must be limited from the values listed on the vendor's data sheet (Reference 8.11). The overall fouling factor limit was determined by iterating on the overall fouling factor, a PROTO-HXTM input, until the required heat load was matched.Table 6-3 shows the results of the PROTO-HXTM runs for the limited fouling factor case, see Attachment E.Table 6-3 Fouling Factor Limit Parameter Design Fouling Limited Fouling Overall Fouling Factor 0.00285 0.002782 Overall Heat Transfer Coefficient 255.2 259.7 Heat Transfer Rate 8,484,000 8,600,000 Required Heat Transfer Rate 8,600,000 8,600,000 Thermal Margin -116,000 0.0% Thermal Margin --1.35 % 0.00 %The limitations on the fouling factor are placed on the tube-side fouling factor, since the tube-side is the most controllable via periodic tube-side cleaning.

To be consistent with the HPCS Diesel the shell-side fouling factor will be set to 0.0005 hr ft 2 °F/Btu for this analysis.

The tube-side fouling factor is calculated from the overall fouling found from the PROTO-HX"`4 iteration process.Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION C NO'97-195 1, A PAGE 7 OF 12 GROTON, CONNECTICUT D. Phyfe DATE 6/29/98 VrRIIEG By S. Ingalls JOB NO.31-003 CLIEN COMED / LaSalle County Station PRojEcrt COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers The area ratio is used to convert the overall fouling factor to a tube-side and shell-side fouling factor ftotal = + (Area Ratio). ftbe Equation 4 Area Ratio Tube OD Equation 5 Tube ID 0.750 in_Area Ratio -= 1.150 0.652 in From the vendor datasheet the design overall fouling factor is fTotal = 0.0 0 2 8 5 0 hr ft 2 'FBtu Btu From the PROTO -HX iteration the adjusted overall fouling factor is found : fadjusted

= 0.0 0 2 7 8 2 hrf 0 F Bt*u From the new overall fouling factor the new tube -side fouling factor is calculated: (fadjusted-fshell)

(0.002782--O.

0 0 0 5)hrft 2 F/u 2 ft -=_ /Btu 0 0 0 1 9 8 4 hrft2 Area Ratio 1.150 = 07 The PROTO-HXTM heat exchanger data sheet is changed to reflect the adjusted design fouling as calculated above. Like the effective area change in the heat exchanger data sheet, this change is made without recalculating the Hoff factor.Attachment E includes a final model calculation report for the Reference Conditions and the adjusted tube-side fouling entered into the PROTO-HXTM data sheet.6.3. FOULING SENSITIVITY The fouling sensitivity of the jacket water cooler is shown in Figure 6-1. The fouling sensitivity was developed at 800 gpm CSCS flow, 100°F CSCS inlet temperature, 1100 gpm jacket water flow, and 190'F jacket water inlet temperature.

The tube-side fouling factor was varied from 0.0000 to 0.001984 (hr ft 2 'F/Btu) by increments of 0.0005 (hr ft 2°F/Btu). As in Section 6.2, the shell-side fouling factor is held constant at 0.0005 (hr ft 2°F/Btu). The PROTO-HX T M Calculation Reports for the fouling sensitivity can be found in Attachment F.Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: & 5-PROTO-POWER CORPORATION --- 97-195 Rj A PAGE 8 OF 12 GROTON, CONNECTICUT D. Phyfe DATE 6/29/98 VERIFIEBY s .Ingalls Jo" NO.31-003 COMED / LaSalle County Station PROEcT COMED / LaSalle Station GL 89-13 Program TIrLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Figure 6-1 18,000.000 16,000,000 Standby D6 -Jacket Water Cooler 14.000.000 12.000.000

[ __10,000.0001 110 % Power Load d 8,00)0,000-----------F__

____6,000,000 4,000,000 2.000.000.0 II 0.000000 0.000198 0.000397 0.000595 0.000794 0.000992 0.001190 0.001389 0.001587 0.001786 0.001984 6.4. THERMAL MARGIN ASSESSMENT The clean thermal margin is assessed by a comparison of the reference condition performance requirements to the heat exchanger performance capability with a zero (0)fouling factor. Using a zero (0) fouling factor shows the maximum available performance of the heat exchanger.

Likewise, the service thermal margin is assessed by comparing the reference condition performance requirements to the heat exchanger performance capability with the design fouling factor.The margin is calculated directly and as a percentage compared to the required heat rate to perform the component's safety function.

The PROTO-HXTM reports can be found in Attachment E.margin=Heat Rate -Heat Rate, quired% margin = 100- ( margin Heat Rateequired Equation 6 Equation 7 Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION --97-195 R A PAGE 9 OF 12 GROTON, CONNECTICUT ORGYAOR D. Phyfe DATE 6/29/98 S. Ingalls JOB NO.31-003 CL-r COMED / LaSalle County Station PROJECt COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Table 6-4 Thermal Margin Parameter Service (Design Fouling) Clean (0 Fouling)Overall Heat Transfer Coefficient 259.7 955.9 Heat Transfer Rate 8,600,000 18,850,000 Required Heat Transfer Rate 8,600,000 8,600,000 Thermal Margin 0.0 10,250,000

% Thermal Margin 0.00 % 119.19 %6.5. MINIMUM SERVICE WATER FLOW RATE The minimum service water flow rate for the adjusted design fouling condition is calculated with the shell-side inlet temperature at 190'F and a flow rate of 1,100 gpm.Iterating using the service water flow rate and inlet temperature, the minimum acceptable flow rate is found for each inlet temperature (Attachment G). The heat load for each iteration must be equal to or slightly above the required heat load of 7,800,000 BTU/hr and 8,600,000 BTU/hr, the diesel heat load at 100% and 110% power, respectively (Reference 8.1). Figure 6-2 shows the results of this iteration process.The results of the model iterations are summarized in Table 6-5 and Table 6-6 along with Figure 6-2. Density corrections of the PROTO-HXTM flow rates are made in accordance with Equation 3. Values for fluid density are obtained from Reference 8.12.Table 6-5 Minimum CSCS Flow Rate at 100% Power] CSCS Inlet Density at Inlet PROTO-HXTM Density Corrected Temperature Temperature Input Flow Rate Flow Rate (OF) (lbm/ft 3) (gpm) (gpm)35 62.41903 161.1 161.0 40 62.42184 169.8 169.6 50 62.40595 190.5 190.3 60 62.36445 217.5 217.5 70 62.30034 254.2 254.5 80 62.21603 307.0 307.7 90 62.11349 389.3 390.9 100 61.99437 534.5 537.7 Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: & 5-PROTO-POWER CORPORATION NO- 97-195 REV A PAGE 10 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls JOE No.31-003 CLIENT COMED / LaSalle County Station PRojEct COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Table 6-6 Minimum CSCS Flow Rate at 110% Power-CSCS Inlet Density at Inlet PROTO-HXT1M Density Corrected Temperature Temperature Input Flow Rate Flow Rate (OF) (lbm/ft 3) (gpm) (gpm)35 62.41903 193.5 193.3 40 62.42184 204.8 204.6 50 62.40595 232.2 232.1 60 62.36445 269.1 269.1 70 62.30034 321.0 321.3 80 62.21603 399.3 400.3 90 62.11349 530.9 533.1 100 61.99437 795.3 800.0 Figure 6-2 Minimum Service Water Flow 900.00 800.00 700.00 600.00 500.00 0 a 400.00 U 300.00 200.00 100.00 0.00 30 40 50 60 70 80 90 100 CSCS Inlet Temperature

(*F)Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref,: P&I15-1 PROTO-POWER CORPORATION CL NO. 97- :195 = A PAGE 11 o" 12 GROTON, CONNECTICUT ORIG114ATOR D. Phyfe DAT 6/29/98 VERIFIED Y S. Ingalls JORNo.31-003 CLIENT COMED / LaSalle County Station PROJEcT COMED / LaSalle Station GL 89-13 Program TXTLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers 7. CONCLUSION 7.1. PROTO-HXTM MODEL The Standby Jacket Water Cooler model was developed using PROTO-HXTM, Version 3.02. The model was benchmarked to the vendor data sheet. The benchmark model correlation to the vendor data sheet is -0.13 %. The benchmark model is for reference only based on the non-conservative approximation of heat exchanger effective area as discussed in Section 3.2 and Assumption 5.1. Calculations performed with the Standby Jacket Water Cooler model are to use the effective area developed in Section 3.2.This model should be considered suitable for use in the analysis of thermal performance test data.The model database is saved under file name dg0la.phx, with a file size of 640 KB, and a file date and time of 6/29/98 at 1:50:34 PM. The saved database is set up to run the Reference Conditions with design fouling factor selected, the design fouling factor is a shell-side fouling of 0.002782.

The database file is included as Attachment H.7.2. HEAT EXCHANGER FOULING FACTOR LIMIT For the Standby Diesel Generator Jacket Water Cooler to provide adequate heat removal at the specified LaSalle Station Reference Conditions the overall fouling factor must be equal to or less than 0.002782 hr ft 2 °F/Btu. This overall fouling factor is entered in the model as the shell-side design fouling factor.7.3. FOULING SENSITIVITY Given a constant shell-side fouling at the model design value, the sensitivity of the jacket water cooler to tube-side fouling effects is shown on Figure 6-1.7.4. THERMAL MARGIN ASSESSMENT Assuming the adjusted heat exchanger effective area and maximum overall fouling factor, the clean and service available thermal margins are 119.19 % and 0.00 % respectively.

7.5. MINIMUM SERVICE WATER FLOW RATE As shown in Figure 6-2 the service water flow can be throttled down to account for lower service water inlet temperature conditions.

The heat exchanger can remove the design heat load for the diesel at 100% (7,800,000 BTU/hr) and 110% (8,600,000 BTU/hr) rated power, by reducing service water flow rates as the service water temperature decreases.

Form No.: P1050105 Rev.: 10 Date: 10121/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO.97-195 REV A PAGE 12 oF' 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls JOB r10.31-003 CI I COMED / LaSalle County Station PRECT COMED / LaSalle Station GL 89-13 Program rTILE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers 8. REFERENCES 8.1. LaSalle Station UFSAR, Sections:

9.2.1.1.1, 9.5.5.1.1 (Attachment D)8.2. NRC Generic Letter 89-13 8.3. The National Board of Boiler and Pressure Vessel Inspectors, Form N-1 Manufacturers' Data Report for nuclear Vessels (Attachment C)8.4. LaSalle Station FSAR Q40.92 (Attachment D)8.5. Stewart & Stevens Vendor Manual, VM J-152 through VM J-157 8.6. LaSalle Station Drawing, D-22079 8.7. Sargent and Lundy Specification J-2544 (Selected Pages, Attachment B)8.8. Not used 8.9. Standard of the Tubular Exchanger Manufacturers Association 8.10. Heat Exchanger Thermal Performance Modeling Software Program PROTO-HXTM Version 3.02 Software Validation and Verification Report (SVVR) SQA No. SVVR-93948-02, Revision F, dated 2/17/98 8.11. American Standard Heat Exchanger Data Sheet for the LaSalle Station Standby Diesel Generator Jacket Water Coolers. (Attachment A)8.12. Proto-Power Calculation 93-048, "Fluid Properties

-Fresh Water -Range 32°F to 500'F", Rev. A Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&t 5-1 Attachment A to Proto-Power Calculation 97-197 Revision A Proto-Power Calc: 97-195

Attachment:

A Rev: A Page 1 of 3

-1 7j ýI ,. il L STEWART & STEVENSON SERVICES, INC.RECIPROCATING ENGINE SALES -............

.8631 EAST FREEWAY HOUSTON. TEXAS 77029 WE RE TRANSMITTING

..PAGE(S) INCLUDING COVER. IF INCOMPLETE, PLEASE CALL. 7131671-6218 OR 7131671-6152 PLEASE DELIVER TO: DATE:91 NAME: (Ugca'1 ca 1 Llet FROM: _ er___., FIRM: C)O WE 0 PHONE: 713/671-6 (FAX: -6 _ -Z--9 FAX: 713/671-6127 u 01 Proto-Power Calc: 97-195

Attachment:

A Rev: A Page 2 of 3 PA" G. nn JUN 04 '98 19:0

..H'EAT TRANS1 A 5IV3QN&PAL /~Y. 14110l *1GE SPE10MCAION~

SR=E.Z1L&J. W~L~J~Xt4l

-1 4 7 11'2.21 22 29 27 19 211 22 P F.-68683-77 CUSTOMERl

ýStekqart

& Stevenson for Comnorwealth EdisoM IREFERENCZ NO. u9426Rv PLA14T 6OCATION OT""ccOr uNIT iacker VThrz.r tEioler Iw O )t SIZE 1;1ý6 CPK TY E TEMA AEAJ* (v j CONNFECTED N _17c1447~O. i'.SU~./UIT W i 7'~ SHELLS/UNIT OeSO. FT. SUJRF./SHELL.

'~ 7 PERFORMANCE OF ONE UNIT SHEL.L SIMK TUOK sIDwe FLuIO CIZRCULAT~r)

Jacket Water Ra Water rOr¶AL FLUID ENTERING 5,0#H-r- _388,000 MLr VAPOR_____________

__LQI 50,000. /lHr 388,000 #/M-r FLUID VAPORIZWP 09% CONDSP~srEO sTrEAM COrdOErqSEEO GRAVITY VISCOSITY MOLECUJLAR WE-IGHT SPECCIPPIC H(EAT sru/LS- I STU/1La-4 F THERM.AL CONDUCTIVITY erfPF-LATENT WPAT 9 TV/ Ii I u~/LEI TE04PEPATURE IN I fn0 TempEpATURG -OUT 17-4,24 129 F OPERAT114G PRESSURE SC.PI NO. PASSES PgR SHELL ~One _________________

VrELOCITY

.5y/8P1'SC PRESSURE DROP 6SI PSI_FOULING FRESISTANC9 (IMIN. ..0285 Total PHEAT EXCb4ANGED-BTU/N14 M.6 COR4IC-7p0-F TI4ANSPECR RAi'E-3LrRVLCE 255,2 EA CONSTRUCTION OF ONE SHELL 01591ON PRESSURE 150 PSI 150 PSI TEST PRESSURE 225 PSI 2200s OESICN TEMPEOA'TURe 9030F 1'uaEs ARS Copper A!lIay 142 No. 18RD0 3/. "swo -3ZN4T1 Tr1C SHCLL Steel 1.0- 0.0.161, 14EILL C0J!R None uYG (A.EmovI CHANNEL 30AMWR MUntZ. CHANNEL COwVR ste1 TUSESI4RET -STATJON ARY Mun t; ?UWESHEE7WLOL0TIN0 U. tutZ BArFL.ES-CROSS Stee) TYPE FLOATING READ COVER I3ArFWLS-LOMG Tv P1 tPM@IN4SEMENT PROTECTION No TUSE SUPPORTS Steel TURF. TO TWOKSSEET JOINT Rolled ISASKISTS CorrIp. Asbestos Packing Neoamrer CONN ECTIONS-SMELL1.

SID3E IN )Qil OUT 0 AIg10 N CHANNEL% SIDE IN OUT 8AT,1 101 ANSI CORAOSIOII ALLOWAMCE-SHBLL 9101E 116" QnC trpeslo 510 16" onC CODE MEIJIREM~rNT&

A$MF Code III -3 Stamned TrM AL C_ ASS C WEIGHT5_68ACJ4 SHEL6. 12 6Q BUNDLE 1860 FUL-L OF WATERt 4410-NOTE: INDICATE AFTER LEACH PAPIT' WETMI!Ft STRESS RELIEVEOJS.O.1 AND WWBTHE-R RlADIOGRA.P'MO I)C-;R)REMARK~S:

RemovabTelube bundT-ePr.

oPw Cl:9719 Arneric~, Sndrd P/N 5-046-15-15i~-n1 Fuoiweac:;-r Ar~erican Standg-LA Serial No. 8-20005 AttachetA 5'3 35 36 a7 40 41 42 43 ac 47 43 so 51 S2'-I a*,0-I.1 c ýJUN 04 *38 1' :09 ev- A Paize 3 of 3 L Attachment B to Proto-Power Calculation 97-195 Revision A Proto-Power Calc: 97-195

Attachment:

B Rev: A Page 1 of 3 SARGENT & LUNDY ENGINEERS CHICAGO PEFEKENCE 9.7 J-2544 CA, 11-09-76 include a shell and tube heat exchanger which will be supplied with cooling water from the Purchaser's cooling water system.b. The closed cooling water system pump shall be of the centrifugal type and shall be driven by the. engine.C.The shell and the tube heat exchanger shall be of the capacity required for 110 percent of rated power with a fouling factor of 0.0005 on shell side and .002 on the tube side. The heat exchanger shall be in accordance with the requirements of ITEN A, TE4A (Tube Exchanger Manufacturers' Association)

Class C and the ASHE Code Section III.The type bundle shall be removable without removing shell from its mounting.

The tubes shall be 5/8 inch minimum and be of ad-miralty metal..d. The circulating water system shall be provided with controls which will sense and maintain optimum jacket water temperature.

e. Cooling water supply for the heat exchangers will inlet temperature of 1000F and a minimum of 320F.be designed for a 150 psig water working pressure hydraulic pressure of 225 psig.be at a maximum The coolers shall and tested at a F. Starting System a. Each engine shall be equipped with an independent pneumatic start-ing system complete with all valves, integral piping, controls, etc.b. The reliability of the starting system is paramount and no compromise of the starting capability shall be made with other basic require-ments of the equipment design. Any special devices or auxiliaries required to insure successful starting shall be provided, except any equipment of an experimental type will be unacceptable.

Contractor shall describe in his proposal what occurances are possible to pre-clude successful starting, and what remedies would be necessary that are not already provided for in the equipment design.c. The compressed air starting system shall consist of two redundant sets of equipment, each completely independent of the other for successful operation.

A cross-connecting line with a normally closed valve shall be provided between sets. The accumulator fur-nished with each set of equipment shall have the capacity for a minimum of three normal cranking cycles in rapid succession without the use of its air compressor.

Each accumulator shall be furnished with a shut-off cock, pressure gauge drain valve, safety valve, and sensing element for low pressure alarm. Proto-PowerCaic:

97-195

Attachment:

B 2-9. Rev: A Page 2 of 3 Proposal Technical Data for Diesel Engine-Generator Sets, Cont.La Salle County Station -Units 1 and 2'RF:FEE NaCE Name J-2544 CA, 11-09-76 of Biddter: Stewart & Stevenson Services, Inc.ENGINE-GENERATOR DATA, Cont.(Insert all data in these columns)BASE BID ALTERNATE i-DIESEL GEN. DIESEL GEN.DIESEL GEN.O IA AND 2A O,IA AND 2A p (Contractor to furnish complete infor-mation for starting system furnished)

E. Engine Cooling System: a. Cooling system capacity.(gal)

b. Pipe size for cooling water connections

.............. (in)c. Heat exchanger dimensions:

(1) Length ............... (in)(2) Diam ................. (in)(3) Height ............... (in)d. Quantity of cooling water at rated load, required at 80OF ................ (gal/min)-at 95°F............. (gal/min)at 100OF ............ (gal/min).e. Tube material ................

f. Diameter and thickness of tubes .................... (in)g. Total tube cooling surface...

......................... (ft 2)h. Water box material ...........

545 8 179.5 16" 19.5'" 550 750 840 Arsenical Copper (SBl 3/4" x 18 BWC 479 Carbon Steel Weights: 3050 lbs Dry 4350 lbs Wet 11)PTD-15 Proto-Power Caic: 97-195

Attachment:

' B Rev: A Page 3 of 3 Attachment C to Proto-Power Calculation 97-195 Revision A Proto-Power Calc: 97-195

Attachment:

C Rev: A Page 1 of 7 Ref.: P&I 5-1 Form No.: P1050104 , Rev.: 10 Date: 10/21/97 046 -157-1/5(6-oo1 FOR~I N-1 MANUFAC'TURERS' DATrA 1IPIOIIT FORl %UCLiA11 "TESS1LS As rcqalred Isy th~e 11'ravis~ioumMi ofhe ASR1!: C-le Rlules 1. 1ilnufactgted by 7_J C H_,~i 0jiZAT.RANS FEIR VIVLS 10H _=_A.. UffYALQ._JMW..QbLK1A41L.

2. Manuo(ctur~d,~O

~ 4 E R X.s.a ..J add,.@* of 9u_3 9 ( z i 3. Typ_1 0.~fR:LA.

metd Y ,4~ Q S-IL-.-~ N.i1. N~n. -Yr. BuU:J..j.../W cste. or Vo rt.) (S g & 1 @.H. at E a.) j&4ire. bieftat No.) (Siate It 61ae No.)3a. Applica~ble ASMr' Corte Section IlII, ddiendL 7...V ., Addend ZR 1-7-7V-, (:a,- No...........

lem 4- m. to bc comp feted loteý *itagc wall vessel&. jaclets of jacketed rcascls, a-* shell& of heat exchsangers.(Kintd 'k ave. "a.) (wino. of rlcda 6P.C.6#d)Girt ____________

lt.' -T. __________No. .of Course*'6. floods (a) Material_______

7.5. (b) Material ______________________

L~~~,Crown KnuI.le.1 EMIlelpa Conica of elmiapph.,ica Flat Side to P14e8, (1.9. bettlam. onclm) 1btckneae Wed ha. Rod&.. RatIio Apes Angle Radius Diameter (Convz a me..)If remnovable.

bolts used .~~.__________

________Other fasenn 7. JAClcet Cloaule (Dueaibi.0*

OF#.s ~iT Ie .e rL7. give~e~o d4ec---- = Noe skough)Drop We. t 9. ~ ~ ~ ~ ~ ~ rap Deis rutrUlpi ~ ~ jP mpacc-- ft.Ib Hydfrostaticr or To at a.Dsg Poasr '-apiat--JCJD ttemp. of C Pressure Peia.Imcaus 9 and 10 go be com.pleted oro tube sections.ý__Tb Shets 71,ieay 3atitffiT 51i tachmeo Floatig aaral afIDuLS.OO....

in. ThiciLn..es8s.

ia. Attachment

&M3 to 10. Tbea IMaetial 65 11 %. O.D.-AS4.n.

Thichiae Su...J4...,o

&age _=_.. Number JIM .Type...5MR016 T (Kind Ja Mpoe. Meo.) Stltr.iqla me U)(tems 11 to 14 Incl. W be comPleted (fo inner chambers of jacketed vessels, or channels of heat eatchanges..

II.-11 f~icall G&:ua1~'MCCU T.S GO'.LLLUhikhneass',Pin.

Allcvwsner~.rAiln.

MO~s It-if......,n.

Lea~gib-i.......is...ia.(VWlifed.

MbI., ginigl) (Y-e as No)Girth...____IT... .R1--. No. oil Couac at ....t............

fr. 4Q r. -13. Jlcadst (a) MagieA~-rs (b Af arel~id I____ IAS. W~ Matt4.ei~s]

_______.S.

_____Crown Kns., L. tIt lpit- at C..es tLs..h.tl Fiat S1,4 to. Poest.Ldlis Theinslewt 06=9. Raidum mail. At-&. Angi* W.dtis Osamotel (Co...st oi Ceanest.(C) Floating ---. -....Cap mac f-bHydtsoitatic oti"s : To at 14. no alpt plegilau.4.S Pei of......3..OflF a1 temp. oif -= _-F Veb to.fa*jgPatwei Mes-Tesmd

~~IProo-Power e.TRwcr A Parvas t~-'

.- I 10~~ 1A I I(e Fk befl Wow. %a Nt Viovrlwtae~

101 all V404Vl, U140s, e.pplicoe.-wf 4-a ~ .2-89b SA .-.R..-U0 ---277 Heir--__ I NaI n tte o e orit Attacked 4ItEL3, M latpecdon Manholes, NN I- se.L csu'Ppeniolat Iandholes, No.--.........

Size-_____

Loca~cwn The-Jede, No......,.Sire.

--___ Laccsine (Yea a Ne) C.nt..,) IDemerifra) (Where h Now~(Yoe Weai flat ~ QNwt,.t__

to-matt")

______ _IIIme" (",lttr it s~-I car fog ,ehich -@seat %ase designed)CIFSTIVI:A lION (Or DESIGN Doa. .I&Oi.cfi.on a" file .~d. 0 A~0@91416 SpeciEfreeitore tertifiedt hyA ~ Zj *Peaf. Rng. Stalse4z R4...... tE 1..4c9*tow*e.. nc1l .m report r.rifIIod by,- -~. Prof. Inc. stante -Rot. No. -Ve cereify the hestr mdin t h t c screct tend ctha this i tclear I Ie siorm to the rule, of coscecruc.

sIt o f sit A 'Ie t, it 1i .Z R C N S A U D H ~ v (Ueneuiwcturvr)

ICcaificua.

of aut~eiiit'izon Eapives.*A~g

-.t.1 1928- -Catiliikmrne of Authoesixzati No. 114-CIAIT1I: ICVE OVI'SliOr INSPEICI1ON.

V&SEL AO 01ALR1CAN STAKDARD XLAT TV.A1SPLA DIVI510ON

1 udi1o. Now York 1. Cho undcoelge-vE.

4*lding

valid emantooleon geaswed by iho Nelotewsel Meer i oft. N&cf" &"Acu. SI-cad- V-t eereet-ae owedpw~ SI" state~~ ~ n.AMutualCasualty 3p. 0iqi.MES lluou ,'41, ... & 1919.be" -oegered sthe twoosue. .cmoal dooerit~d in Ohio U.#%ufactutIr1 Dots Report an &...t ~ .........

n sloto too to thce boet al vrt kinlowdge end belief. the ilaftfactuwev he* eonat4iteerd etwo P"Gowe evaeei iot Caceedeaa.

Witk the ASUIL or ctilova" lhis Curl if14C&l. OIcaher the i.0ptowm nor tie .-Pclayer M.I.. env w...enty.

@Pf*aced of iesfittled.

concerncing the pressure'0, ewow described InOioe 101. U.twuetcwor-Dot. Repo.n. t.inc. laihar iCho In.poeele nor tile employur oliell be Home Ill,"I bmire tow any lperceesi ing..ry of pee*drtydeen&g or .i.e. of .*I Lind &lcIst fromatem cjcetaeld wccpcga.........J.L..AJiaf~

alu% -. -aiea Como.saloo state,~ZL

! preelmee sea Me.1. the ,n...,ehaldin%

.,eItc .ct c. i--1.. h.! tic M-i..,itl.ei tf L'a,mi and Prpem.,s Vir...! InspoctowsanCd/or the $ttle 4W Pr~olrwo:

ad 41-1en .pI.,itt tv........

___%ere cometd It**- t.t-.n1,t in thic T3,1~~' .fle .p-r vsitk ph. d..rr'b-dp..1 .ru. end t.H.. ithew Parts ref."ed iso .date 1. ..; .-- .- .. -.-- .-. .~ no ccl Ic.Id.41 Is C..se A-rillee.Sd0 ofchop lnsgceellees h-0e hc~ ons~te. *p- -I1f -'-' 1.~ i s~tihe he*t ..5 --, t*,-.!kcr -l. I-pii.) 0-c muow Ip-wsr he. rcontorycivd and asemblebid thi prilst~or wea.gtl In wCCOW.ctsep

'.1mb iTh ASMF .I. lic nit!. Th. iertri ecl .6. icpr rd d mkbjeciad

'to a hydrosaticl fuelt eaid/or Imniweum I c Too% 4---.. ---. --,!UV lyigýniri thie ~.tIdice't nei her Vt. Ill, r SA .1't rl- h,$ -I -r~il rce.m.ywerfoniV.

.5creea or lor~'ted, cnce~ranan the pee. mute-eecci deecEbtd in tMI. Men.-Joc,tC

... t I' m ,c.n?-v".

n..tthtrf SN. Isopertor not hib .csplayrr ahell be leiobe In any mecmnve let ed 1 porsonel Injurdy Wr I---rt Iee m f eon I-d e 1ic0n IorS Cnc-erl.4 -litt Ila inect. .D .o..le---......

Pt#rnl~d*.ij AS-L A. (7/7 1) Title f., LF.30) I. ohtimtnebi.

frý &.the ASUE, $4S 11.47th %I.. U&ew Yore, N.IY. 10411 Proto-Power Caic: 97-195

Attachment:

C PoDt- A Ponty'. I nf 7 FORMt N-1 WLSUr-AC11JREHS!

DATA REPiORT 1-1111 NU!CLEAR VESSELS An required by mAt- 1'rlsovaron tr dfie A-tE G-Je flujcso 2. Manufacurted It R- JMVICE4 A .L5TN J cu..ha. gO V fl1*%pbV6*qK*&9 9..4 ...t. U-) t. SII tt N6 t £I 1 3.. Applicable ASAIE Colev Section III, Addends date ~ ~,/~L' Case No...Iesma 4-0 ladl. 10 be ColOP104#4 (OC Oin~if Wall ItleN jfiCkP.u ofI0 h~ weassci, at $bell% of Iles. exchaaets.

Voamns[ -3! 5Corros ion 0(o'ýe 14.00 1SZ.qg5 4. Shelli WtaeraIGAIROG-

..a.~O b. es_ in. Allowanca?....in.

fa.h...lnLcrtgoh-.....

ft..... -&a.* .:116eift Les f.T.' R.T. ROIC -ffcey U2 -C x Gleth H.T.a R.T. -No. of Cosgiraeg___I__

6. Heads (a) MasteilsL.........T.S. (b) Matuerial-_________

T.S._______________

L466416" crown Krnugkl EUIP1ge.!

CVACaic 0,10ioph.,Ie.I Fiat WOd to Pres..(Top. baitted. *ad*) Thlkmooo Radius mediae Rat Re Apes Ang3* RadIlas Wimula.e (Coflsa W ogs" If comohbieht bal)te need _______________________

Other fawicalna&i-tefei.ISpe.X.K.

?.S.. SJO.. ubor) -00lie op ____________________

J. acket Clocurer -(676arti-0%ede Itjl. J o~c. Zrbo, elv* dimnales.on.

d~eeriV. or os.etck I)top Weight theee~moawic Chalpy limpect flilb Hydraccatic at Test G .Detaila Pw..sure'i.Sa.

si as....r3 F.d a: lt tup. of a F. 6~~4w.4*"oo i'rcagarc...jsp.,a

~' Items 9 and 10 ce be co~mpleted for tube seeflinas.

P' .Tube N~ecessa Stailoeuasy.

Mateli IUI.iWSa.

AII.Chate.e~

a i"'. ;V (KRA4 1A Spec. -3. (9%bjst to 0"84.) 4Wlid I01 ANMS. C40PPER VA Dia.) 15 ~10. Tube at Maetodal C- I tLL..D.;LLJft.

Thickness.1 5.a.a 8 Tub~&.ype....5m2Q6aT (Kiad as spai. too.) (tngS a~Items If to 14 fact. to be completed foe innot chaml~et of jacketed vessels. at channels of beat exchasgers.

CRAW__U w__ -It.;no I'l S atto.6 oa W00 14,o-. 1. *hTh iaus51~TS O, htna~~ n. Allowaaace:&.-

n. Die. --..-. in......a.

Length ....ft.....Js.

12.K~i Seesa Long skat. .Efficiency-e-CIO FA.W4 Obs..soi(Ya*N)(b) Channel (C) 0I1100-61-48.

-U It soeomythlo, bellIts umed (N)IZ$J~L:6('

Chattly Jlisamco-......

-(-lb Ilvdiotgumic at Tast 0' ed-~ ~. P~ a~u~r~aL ., 94tfthf1900 PeeSs 0910011q4s4 ooaWih4sa c'Attleto19oceffai 4 -ist0th. Ias~t sisw'm.Ipeas.

awes. adaet~qtsss~sis

~ho gU..~ga 0 1W 0W4 0-4 wiý -

It t I.- v I. ItP OIW N-I (Iack)L b t M Ic CMPetajt~J (Of *A ~.,~ shot. cer('ta~e.

I$. Safety V Outtiet' t't Sir*- Lfcatle, Plv 1110tireg~at Ito P~eelWait 1 Sinc o0rn%, tInuni? W..Mbeqv at*T9 qto Tpe hItol. Thecl stetoa "

Attacke*14W. L1R huc of au.t 2SlIP, No,_" ....- St ie L..o3alwnr Tp" r lat,-Jd, NO..1/2 Sierc....

Location ....... : _ ._,' " _ _ +/-_ _ii. S&in.__4 0._. l.ugs.__ý'r

".. elm."--. O.hr.O .C.-R- LEFArached UiLt B&m b )am (Iein o Kcl, (Kvnt.w) (NMbwv) (Desecibe) (Wae b Ie How)(Himat d~e~erarv'.un si *ervice to, 411 sitict. .s .-.. a t CET IFlICATTON or I)ESIGN Ove.... l,,iin I n i,, ., F R{I,: d .JAS f,. cL,,,,', C a0, t- m 0/_. I sateam aslysia. Wspal o..% fit*'4+/-4~4LlSgr~.~

I~X rtflf Deineptfctln ctl~dbyAai rr~.~ Prof. Eng. atLZ.....eq Streos ea , ,.i, ,,ci Jba..J .._ ' /i-- '9 .... ,,,,............._.

Prof. 1ag. ,, Stae Ke. No. _. .!aein hibi i 4 S a;rcoret u thiat dhis 4Ct-Ceat vi akIsi form L~e fulam of construc*CAN STALARD HiAT :/017 570-;_!_TRAýNSFER VVS0 Cetfificeae of euthoritutian Expires p vtI, 14.X S , t 9.J 78 Cetificate of Authowrdzaiom NO.1 CMIITIFICATE OF 9IOI' INSPECTION VCISZLUMADE11 0 ICAlIt STANDARD -BEAT TEANSFY* DiVISIO0NJ

.*,I -affA1o. Keu York 1*o s wdeesiltwd, 1e-9141- a valid Cenatwelce l't..d byt te Ki:lonal Heo.s ef Ue eand Piwesieeow VealjnSpesma sadti/r the litse.srareac)L York ........,eoi e ,,Ltjubecrsecs Sttusl Cnoualty g. '.£cgo, f"'lln/ts hav~e; Ialpeulsd ii. fpei~ssuee voice? described' in thul Veaufeelureve Daa ffepe en- , alie 14 tat 1o the best at my b-.nwedge end owllel, thw Mnmltetiret has r"ettsluesd hIs pFmasu in aeeetdates WPk tle AUMIt Cades facile" Ill.il.e ininr c@hi. ..i irenifitoealtoh hte I6ar.wMJ An. his waPloyet awkbe sany narromag eapcrseedeo

£se&lS4.4 Ceoeejaag Ith primer;'r4) *-scelitns In this Maisuifeureta G.1 aRe ipota. IF'vhtcrmo#, seuuhew the Inspecle.

ano his amplaycs ah0B be .Iable in'dUbaaneo leo any oeisnerl injury ec irt-ely dimige or a los. of cay kind arlsing from at cemecteti WIl 1h.laarle1.a.-

-.o .~.... .C,.iaonS

/ .________________ Ripetie S Sgnetre .tlenal Knave. elms.. Province mnd Me.CImImfI;ICATni f- I' i-,I) A.S4SIIIIA INF!ECTION

l. the 1 ndeesiis.d, holding v.14.1 ruml.ien I......e by the lH rd of UcNle, and Prlei re Vessel .endjed .the Ftoet aw ProIe Ar...n... .de..p. oý. J hite v.veo ii' ~a~~I a'i &t -ed i.-.4 at We 1.nr- in'? the dce-vgjea rsewe n..tIed 4.1. that acnee pruneid to a Emit l... _ -.. , _...... ...... .-. ..... -..no' I t- ded Ln the rentlflrste of shoi tnu W eLionr hate ta... lnrp.;i.C, hby .-.and a*It I*" l. N- 1 ,( .-.".) ,- -4 ., i t.iLfr it. m.'ilmrur 1%&t contlruae l ad sal m'c mbvW .thin prgsawie vi*a gel It, r-vedeba-L-ph Sbj ASASE C J.?, S.-'u 1~1. 1?. t"cisc,itwfl teec -.4 Int.peee e .t.j uiiee.d 5to 5 hy-drestaltc test a&-toe#Pf*ircImla T t" ff __ ........ .. l-- t.My slEr.iuna

@his ..l c tle .he.,lte,.

t ther 19t.r$.r t emrinv-r -6h.. .s.ny smeoty, einr .ed or Impht ved , cor'erint hI% uarae we..,I metrhb-d It thi s &¶ea.daelr's I %.g. tonhcnnor.*

neilh.¢ the in.p.cie n-o his veoplyer c hel hse I6ble In any mein.er r"U 5n' .petsmse i .r.h'S) vof 1"I091d#y 11 ,'t OtS I ..1n Iny -ind gf. 4ti ; hron o-.rnected with o.. ..: -..* .' ;-A'Lista ..... ...... .. -. j9 ..... " .'-....n.. ... .... ...... .. ....... .... .. .cilnredjnL I.S.A. 17/10) ahie l,- (1':3) i1 obsIsiesbts I(res the *55 V., 4 *J N, _ & ,3 , 10W.H Yroto-k'ower tarlc: 9-195

Attachment:

C Rev A Paoe 1; nF 7 rOtItt N-I MANUFACTURER115 l)ATA imI.POItI Foi NUICL'AR VE+SSELS An required ly ihe I'roIslone cr she A.WIE L*iesc HlutictI 1, IHanu(eceqned by-...IZICANI3TANOWQ

~ _LA.. SEDIVISION

..JUFL...lLOX12c.(N... ant .addu. .1 Ml x .r lW..s.Type- RC M .AKind l:3-._........

Nat'l lid. No.........r_

.(11, 14 l o f, V* ,.tm,. .N., o.l .) (S te#1 It b tL. No.)3'. Applicable AMýIF Code: S~ection III, EdroLJV~..Addenda date. t'-1tAVt.

r Z./2.LZ Cas. No_-.......

i-'s. 4-1 incl. t. be completed foe single **ai wasCIAl, jcIts Of jacketed Vessel$. of shlls Of heat escliansee..

4. Shelal MatasiEJCaB TS. CiOOflJOThicknes s,!- in. Allo.ane..._in.

Dis... ito~. In. Lengdh._ ft. -fi.(KMind b ives. 4.,) (Woan. of ' loagg .paciflted) 5ScauM L..Std.L ..A.T.' MO R.T......8014IE.......EfficiencY.

ICC)Gnb -If.T.' -LT. -No. or Cotit....°.

..- 6. Heads (a) T.S. (I) at T.S.Crolwnn Cete Knuckle Illiptical Ce alt eIVLe pheI caSO l riot side ti Ps. rees,% (tag, h1tsie ends) Thickness Ka1dwa Ratio, Aesa Radius DUiels, (Coalms Or I t se m s b ut t s u se d .S p e c .N oM a e b O th e r alste nin g 1o1111Il d( .&teI1lia Sple. T14., 51... Numb..)

ma"ilmaiN skellca)7. Jacket Closea .( fascribe so gee &1 w Kit , ea, etc. U bar giv il e. itoseein.

at sketch)'-Ditip P-'aglh: Pswmic..Chaey Impsct .ft-ih Hydoasie ow } Test Delr Paslv.s0-piat

_0

ttemp. at_______

OF. Cwesmn& o Pressure ..~..Psi , .tems 9 cad 10 to be completed (or tube sections.9.Tube Shee ts:Saslonaly. .folcpar in. I?1r13r7 a r1v6-Msscru l

l+¶p.LLo..}

j(AKbJ-za t.Ll.... n tnu d walurnlled)

Ain.- ThCcOPnVsEES-in.

Attachet5%S.Tubean MscawdeS5jj....o.D 2ý. T1iIcl DeM sa."J&anger .NsatbeiJ8&LType.t2 J U (Kind b "sIt. Ieo.) (S1sainhts

" fi(telS It so 14 1a0. to beo eqplesd feer 10ea0 ehambeua of jachesed W0a19lc, Or channels.OI beat es¢keagel,.

CKANM4EUtFS fL 911 oain sis1S?5iCartesian

11. _31wtf &I1actAOaS...

2 00mickncaaG.&=a..

n. AllowanceL..in.

Dim.......

gt.......o.

Lesssh (U_1.; ~(IKii&SIpeee.M) (Kin.. *sne41,spneled)

S 12. Sesent itl.J!.__

h~.__ I -.T. E -_E fi;ci wncip .. +._ 1 (Wetted. Dhill.. (Ye't Of N)Gikeh "l-.T.' K. -N. of Courses I I5. (a) &Iasd&t&L.S jQ(b) Ia(ew il .....__ T.S. _ _. (c) Mateai&l ..T.S. _ .,.*Clawn KnucMkle LI IIlves Cantest Hemlaphulv.s Klsl Olds gn rvle.. aW Laclic. Thislhots M1di4a l4Rdius MRatt Apes Angjl Mald.s Gaisteee (Ceese *a Cm4na40 ( a) V o , l i l A S 0 -L 8 -4( -(h) Chsnnal .-(c) Plosiag ---AL&0(6't SAI¶3 :.Uh U.Qilfl tellnl ___ __ + l It if eewweble, halh' sead (.AMlt; LtS Rumba) Oo agu rrscinI I441escab s snss ,+.~ o, -kw,.... Z.--0 Map *eight. .i. t. .0,... + .* ......,..... *a 1-1 5 pss....* ,.... .lydr a Tes 0 , 14 DsgnPlswe.4oPe o 0se1'ef op, of ý .Ol. rtsutwuIron rte..uee.2PUS..g

~~~td,?~~~~

It P"Wvt~.'V:

1: 5 tw9W i~e S -t, :I+ :.. N-. 1 , ; :1 :.,.iIP *: -ttt ,,4M .t $.9:.i(." F'T %I, N-i (haeiL) .... ., 7.. 4 -..4 -IhesM bltw to be tot all tqte 1hVat sppleahie.

Vt.t rovo*jfttlIt nes Mvol 4 16. Woaeles.i le " I " f --Uo..t ejj r Tr lr matelitl T hthnese Salelvs ' Atteahed t?. 104"ton Mnihooe,f No,--e....

Sire_- L..cai ano ..Opflit t HKadholem, No,---.-.-

Sir.:- .Locatio, .Thtecdt, No.- -__ Size Locatloa"-._

'________

'--" " ' " "._19. Supporu: S.%,__N 0 .L..ugs L...Leg .--- Other .CacR*AJLJESAittct.tUBLib -M'TY S tJ_(yea ' s b) (WuIbf.el twomb..) (Doosgibe) (Whetre tS New (St1.1 decr.ritnl at citseriec.

tar % th i easele l was 4dittal rd)C LI-IlIIFCA[ItIN OF DlNJ1bN Delf'n Sntaroslion an. file WAieaZs AAc~ksu ~~fdo , Desig ,e.erliiat....

re,,,e .hyvjC../.AJ/..<C

-,,.*L.

Pa. u. "State' Me S es .n...rsic

ee.. entitled.

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.-4.......Proto-Power Calc: 97-195 l(7'/7 t) "Tr-ia Ieo-e (t:11)a Is cfleiabla from the ASI 34i4 X. 471h ft, tfew Yark. N.Y. 10O0?AtRacPment:

7 Rev: A Page 7 of 7 Attachment D to Proto-Power Calculation 97-195 Revision A Proto-Power CaIc: 97-195 Attachflent:

D Rev: 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 equipment 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 Ecruivment Cooling Water System 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 Desian Bases 9.2.1.1.1 Safety Desian Bases a. The system is sized based on the following minimum equipment cooling water flow requirements:

1. RHR heat exchanger

-7400 gpm 2. diesel-generator cooler (division 1 and 2 only) -800 gpm 3. diesel-generator cooler (division

3) -650 gpm Proto-Power Ca~c: 97-195

Attachment:

D Rev: A Page 2 of 5 9.2-1 REV. 12 -MARCH 1998 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 stat i-n-C-hroTom-snnunciate 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 1 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 sys~tems 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-9.5.5.1.1 Safety Design Bases 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 'and 1000 F, respectively.

Total heat transfer by this system is 9.5-34 REV. 0 -APRIL 1984 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.High water temperature 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.

Beaters 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 Design 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.The engine cooling water heat exchanger is a two-pass shell and o tube type heat exchanger having admiralty tubes with a carbon O steel water box and shell. Engine cooling water is circulated U through the shell side while strained lake water is pumped U 0 through the tube side by the CSCS-ECWS (Subsection 9.2.1). ..Design pressure and temperature is 150 psig and 3000 F for both 00 9.5-35 REV. 0 -APRIL 1984 2 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 water 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 gpmN 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 Q40.92-1

Attachment:

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

Attachment:

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 DGOIA -DG Jacket Water Cooler Vendor Data Sheet -BENCHMARK 06/29/98 Shell and Tube Heat Exchanger Input Parameters II 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"°F 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 (fi/s)Tube Pitch (in)Tube Pitch Type Shell-Side Tube-Side G1099-45 ..... ....7756&T 190.00 100.00 174.40 122.20 $d661" &/Ve65 0.00285 0.00000 ,rAL Fresh Water 5 " Fresh Water f 8,600,000) ~~~255.20

~ )-C 10.780339000 i5t 0.00"om4 4..A5C~L4 TEMA-E Efcrtqf'c COJT)r(4 5. 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.°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#PIX-0000)

Commonwealth Edison Calculation Report for DGOIA -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 (OF) Tube Inlet Temp (0 F) 100.0 Shell Temp Out (OF) Shell Inlet Temp (OF) 190.0 Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (°F)Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hruft 2.°F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hrift 2.OF)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-.F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (fF)Prandtl Number Tav Shell (fF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (fF)Skin Visc (ibm/ft'hr)

Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (°F)Cp (BTU/Ibm-°F)

Tav Tube (fF)K (BTU/hr'ft.°F)

Tube Skin Temp (°F)Extrapolation Calculation Results Shell Mass Flow (Ibm/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 (lbrrift-hr)

Density (lbm/ft')Cp (BTU/Ibm-°F)

K (BTU/hr-ft-0 F)Overall Fouling (hrft 2-°F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr.ft 2..F)I/Wall Resis (BTU/hr.ft 2.OF)LMTD Correction Factor U Overall (BTU/hr.ft 2.°F)0.002850 2,075.6 2,100.5 25,594.8 0.9886 479.0 255.2 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 Shell Temp In (OF) 190.0 Shell Temp Out (°F) 174.4 Tav Shell (OF) 182.2 Shell Skin Temp (°F) 173.5 Tube Temp In (0 F) 100.0 Tube Temp Out (OF) 122.2 Tav Tube (°F) 111.1 Tube Skin Temp (°F) 121.0.roto-Power Calc: 97-195

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E Rev: A Page 3 of 13** 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 DGOIA -DG Jacket Water Cooler Vendor Design Condition

-Adj. Area Shell and Tube Heat Exchanger Input Parameters 06/29/98__ 11 Shell-Side Tube-Side Fluid--Quantity, Total gpm .099745 ----- -775-6 Inlet Temperature OF 190.00 100.00 /0A'Outlet Temperature OF 174.40 122.20 Fouling Factor L0.00285 0.00000 VA Lit 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.°F) 255.20 Emprical Factor for Outside h 0.780339000 Performance Factor (% Reduction) 0.00 (.ALALAI'0 Heat Exchanger Type TEMA-VE /SW 5Et *1.Effective Area (ftA2) 471.23 Area Factor 0.981978184 Area Ratio Number of Shells per Unit I Shell Minimum Area 0.490000000 Shell Velocity (ft/s) 5.000 Tube Pitch (in) 0.7500 Tube Pitch Type 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-.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 DG01A -DG Jacket Water Cooler Vendor Design Condition

-Adj. Area 06/29/98.1 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 (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)775.6 1,099.5 100.0 190.0 11 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr'ftz-°F)

Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr'ft 2"°F)Tube-Side hi (BTU/hr'ft 2 0 iF)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hrlft 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 (°F)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (°F)Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (IF)Skin Visc (lbm/ft-hr)

Tube Temp In (°F)Density (Ibml/ft)

Tube Temp Out (IF)Cp (BTU/Ibm-°F)

Tav Tube (IF)K (BTU/hr'ft-°F)

Tube Skin Temp (°F)Extrapolation Calculation Results Shell Mass Flow-(lbm/hr)

Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.5E+5 3.88E+5 8.48 1E+6 71.3 471.2 Overall Fouling (hr-ft 2 0-F/BTU)Shell-Side ho (BTU/hr'ft 2"°F)Tube-Side hi (BTU/hr'ft 2.°F)I/Wall Resis (BTUJ/rWft 2-°F)LMTD Correction Factor 0.002850 2,076.0 2,099.0 25,594.8 0.9889 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)

Skin Visc (lbm/ft hr)Density (lbm/ft-)Cp (BTU/Ibm 0'F)K (BTU/hr ft'°F)Shell-Side 5.15 8.543E+04 2.13 0.82 0.87 60.52 1.00 0.39 Tube-Side 8.00 6.580E+04 4.00 1.47 1.34 61.85 1.00 0.37 U Overall (BTU/hr-ft 2 0'F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin TeotoW-ower Calc: 97-195

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E Rev: A Page 5 of 13 255.2 190.0 174.6 182.3 173.5 100.0 121.9 110.9 120.9** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 12:26:44 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler Adj. Area -LSCS Ref. Conditions 06/29/98 Shell and Tube Heat Exchanger Input Parameters II Shell-Side FI uiditQu-gan-tity, -T6-tI gp- --,0994-5 ..............

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 2.0 F)Emprical Factor for Outside h Performance Factor (% Reduction)

Tube-Side-..--....

77576r 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-ft-°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 6 of 13 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 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 (0 F) Tube Inlet Temp ('F) 100.0 Shell Temp Out ('F) Shell Inlet Temp ('F) 190.0 Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out (fF)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.°F)Tube-Side hi (BTU/hr'ft 2"°F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr'ft 2 0"F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2.°F/BTU)Property Shell-Side Tube-Side Velocity (f/s) Shell Temp In ('F)Reynold's Number Shell Temp Out ('F)Prandtl Number Tav Shell ('F)Bulk Visc (lbm/ft-hr)

Shell Skin Temp ('F)Skin Visc (lbm/ft-hr)

Tube Temp In ('F)Density (lbm/ft 3) Tube Temp Out ('F)Cp (BTU/Ibm.°F)

Tav Tube (fF)K (BTU/hr-ft.°F)

Tube Skin Temp (fF)Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ftW)Property Velocity (it/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.°F) 5.325E+5 LE-S 77PAM 3.978E+5 Rep, (o .4E+1?fa Ilee 0 8.484E+6 WjjýM,71.3 471.2 Overall Fouling (hr-ft 2 -F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2-°F)I/Wall Resis (BTU/hr-ft 2-°F)LMTD Correction Factor 0.002850 2,034.1 2,138.0 25,594.8 0.9889 Shell-Side 4.99 8.257E+04 2.14 0.82 0.88 60.53 1.00 0.39 Tube-Side 8.20 6.728E+04 4.01 1.47 1.34 61.85 1.00 0.37 U Overall (BTU/hr-ft 2.°F)Shell Temp In (fF)Shell Temp Out ('F)Tav Shell ('F)Shell Skin Temp (fF)Tube Temp In ('F)Tube Temp Out ('F)Tav Tube (fF)Tube Skin Tel~3 qtPower Calc: 97-195

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E Rev: A Page 7 of 13 255.2 190.0 174.1 182.1 173.1 100.0 121.4 110.7 120.5** 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 DGOIA -DG Jacket Water Cooler Reference Condition

-Fouling Limit Shell and Tube Heat Exchanger Input Parameters 06/29/98 h.'I F1U6idQV fiit-yii gpml 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 2.0 F)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 1 .0 99T4-5 -...............

... 775 -.6I-190.00 100.00 174.40 122.20 Fc it, r"'i 0.00285 0.00000 , Fresh Water fi (, t N, Fresh Water U4{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 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-°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 8 of 13 12:29:43 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler Reference Condition

-Fouling Limit 06/29/98 Calculation Specifications 7'Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions lFouling Was Input by User I ITrFRATOtJ US.,51N6N FWt, UTsnL Daa Exrap olatIon HeAD a Test Data Extrapolation Data I 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)Input Fouling Factor 795.3 1,064.5 100.0 190.0 0.002782 Fouling Calculation Results Shell Mass Flow (Ibmrhr) U Overall (BTU/hr ft2.°F)Tube Mass Flow (lbmrhr) Shell-Side ho (BTU/hr-fte.F)

Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2.0 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 (IF)Prandtl Number Tav Shell (IF)Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (°F)Skin Visc (lbm/ft-hr)

Tube Temp In (IF)Density (Ibm/ft')

Tube Temp Out (IF)Cp (BTU/Ibm.°F)

Tav Tube (IF)K (BTU/hr-ft-°F)

Tube Skin Temp (IF)I Extrapolation Calculation Results Shell Mass Flow (lbm/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 (lbmlft-hr)

Skin Visc (Ibm/ft-hr)

Density (lbm/ft')Cp (BTU/Ibm.°F)

K (BTU/hruft.°F) 5.325E+5 3.978E+5 71.1 471.2 Shell-Side Tube-Side 4.99 8.20 8.251 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-°F/BTU) 0.002782 Shell-Side ho (BTU/hr-ft 2-°F) 2,033.3 Tube-Side hi (BTU/hr-ft 2-OF) AT',)uusM7) 2,140.0 I/Wall Resis (BTU/hr-ft 2-OF) &I, t_ 25,594.8 LMTD Correction Factor 0.9885 FOIALIAL-U Overall (BTU/hr.ft 2.°F) "'f"CT0h 259.7 Shell Temp In (°F) 190.0 Shell Temp Out (OF) 173.9 Tav Shell (IF) 181.9 Shell Skin Temp (°F) 172.9 Tube Temp In (°F) 100.0 Tube Temp Out (OF) 121.6 Tav Tube (°F) 110.8 Tube Skin TemprfPower Calc: 97-195 120.8

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E Rev: A Page 9 of 13** Reynolds Number Outside Range of Equation Applicability 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 DGO1A -DG Jacket Water Cooler**** FINAL MODEL ****06/29/98 Shell and Tube Heat Exchanger Input Parameters II I. *1 F ii d-Q-uanfify-7T6TahF Inlet Temperature Outlet Temperature Fouling Factor Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/l Design Heat Trans Coeff (B]Emprical Factor for Outside Performance Factor (% Redu Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Number of Shells per Unit Shell Minimum Area Shell Velocity (if/s)Tube Pitch (in)Tube Pitch Type Shell-Side Tube-Side gpm "I,-9945 .77..-OF 190.00 100.00 OF 174.40 ILAL 122.20 0o.002t788 1'o oooo~~ V~IO"'( .z- 0.00000 Fresh Water Fresh Water hr) 8,600,000 IU/hrft 2"°F) 255.20 h 0.780339000 ction) 0.00 PRO J 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.°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 TEMA-E 3600ti%' 2-1471.2y 0.981978184 1 0.490000000 5.000 0.7500 Triangular 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 10 of 13 12:31:13 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIX-0000)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler**** FINAL MODEL ****06/29/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions IDesign Fouling Factors Were Usedi AtTUSTEý)

O(A.- \ & ,J V P sl/-A) FoLAt.ti16-FACTo(Z ir /. OT- Hý)4 A/I01>e L 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 (IF) 100.0 Shell Temp Out (IF) Shell Inlet Temp (IF) 190.0 Tube Flow (gpm)Tube Temp In (°F)Tube Temp Out (IF)Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (lbmlhr) Shell-Side ho (BTU/hr-ft 2-0 F)Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft2.°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 (IF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ftlhr)

Shell Skin Temp (IF)Skin Visc (Ibm/ft hr) Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (IF)Cp (BTU/lbm-°F)

Tav Tube (IF)K (BTUfhr'ft 0'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')5.325E+5 3.978E+5 8.6E+6 71.1 471.2 Overall Fouling (hr-ft-F/BT1 Shell-Side ho (BTU/hr-ft 2.0 F)Tube-Side hi (BTU/hr.ft 2.°F)I/Wall Resis (BTU/hr-ft 2.°F)LMTD Correction Factor U Overall (BTU/hr.ft 2.OF)) ) 0.002782 2,033.3 A"VrIJUTE 2,140.0'OCJUA)&" 25,594.8 0.9885 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ftO)Cp (BTU/Ibm.°F)

K (BTU/hr-ft.°F)

Shell-Side Tube-Side 4.99 8.20 8.251E+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 Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (OF)Tube Skin Temp (IF)1*x"7 C%0~CI I-0 P4-C 4-4 0 259.7 190.0 173.9 181.9 172.9 100.0 121.6 110.8 120.8 4-.Ce 4-.** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 12:32:54 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DG01A -DG Jacket Water Cooler FINAL MODEL- CLEAN (0 Fouling)Shell and Tube Heat Exchanger Input Parameters 06/29/98 I.*1 Shell-Side Fk1-idQ-u-tiit-y-Total ~gpm --,0-99_45-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...... .7T5-.-6-1--

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-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

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E Rev: A Page 12 of 13 12:32:54 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler FINAL MODEL- CLEAN (0 Fouling)06/29/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions IFoulingWasInputbyUser 0 FOULI' FOR. CLEAN/HX. A *Test Data Extrapolation Data Data Date Tube Flow (gpm) 795.3 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In ('F) Tube Inlet Temp ('F) 100.0 Shell Temp Out ('F) Shell Inlet Temp ('F) 190.0 Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out ('F) Input Fouling Factor 0.000000 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ftt .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) 1/Wall Resis (BTU/hr-ft 2'0 F)LMTD LMTD Correction Factor Effective Area (fW 2)Overall Fouling (hr-ft 2.0 F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (fF)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (fF)Bulk Visc (lbm/ftrhr)

Shell Skin Temp ('F)Skin Visc (lbm/ft-hr)

Tube Temp In ('F)Density (lbm/ft')

Tube Temp Out ('F)Cp (BTU/Ibm 0'F) Tav Tube ('F)K (BTU/hr'ft'°F)

Tube Skin Temp (°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 (11C 04 1 A 3.978E+5I 1.885E+7 48.3 471.2 Overall Fouling (hr-ft 2 0.F/BTU) 0.000000 Shell-Side ho (BTU/hrft 2'F) 1,957.5 Tube-Side hi (BTU/hr-ft 2-°F) 2,318.4 I/Wall Resis (BTU/hr.ft 2-F) 25,594.8 LMTD Correction Factor 0.8656 Property Shell-Side Velocity (ft/s) 4.97 Reynold's Number 7.721E+04 Prandtl Number 2.29 Bulk Visc (lbm/ft-hr) 0.88 Skin Visc (Ibm/ft-hr) 1.05 Density (Ibri/ft 3) 60.74 Cp (BTU/Ibm,'F) 1.00 K (BTU~hr ft°F) 0.38 Tube-Side 8.22 7.626E+04 3.50 1.30 1.07 61.65 1.00 0.37 U Overall (BTU/hr-ft 2.°F)Shell Temp In (7F)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (°F)Tube Temp In (7F)Tube Temp Out ('F)Tav Tube ('F)Tube Skin Temp (°F)0~PU 0 0 955.9 190.0 154.6 172.3 148.6 100.0 147.4 123.7 146.8 to 4)** 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

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F Rev: A Page 1 of 6 15:49:57 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler Tube-side Fouling = 0.0000 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 (°F)Shell Inlet Temp (°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.°F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-ft 2'.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-F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (°F)Bulk Vise (lbm/ft-hr)

Shell Skin Temp (IF)Skin Visc (Ibm/ftrhr)

Tube Temp In (°F)Density (lbm/ft 3) Tube Temp Out (IF)Cp (BTU/lbm'°F)

Tav Tube (IF)K (BTU/hr-ft-°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) 4.98 Reynold's Number 7.993E+04 Prandtl Number 2.24 Bulk Visc (Ibm/ft-hr) 0.86 Skin Visc (lbm/ft-hr) 0.98 Density (lbm/ft 3) 60.68 Cp (BTU/Ibm 0'F) 1.00 K (BTU/hrft 0'F) 0.39 5.325E+5 3.978E+5 1.57E+7 55.4 471.2 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2.°F)I/Wall Resis (BTU/hr-ft 2.°F)LMTD Correction Factor 0.000500 1,983.9 2,261.9 25,594.8 0.9332 Tube-Side 8.22 7.349E+04 3.64 1.35 1.15 61.72 1.00 0.37 U Overall (BTU/hr.ft 2.°F) 644.5 Shell Temp In (°F) 190.0 Shell Temp Out (IF) 160.6 Tav Shell (IF) 175.3 Shell Skin Temp (IF) 157.2 Tube Temp In (IF) 100.0 Tube Temp Out (°F) 139.5 Tav Tube (IF) 119.8 Tube Skin Tem ¶t~b-Power Calc: 97-195 138.0

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F Rev: A Page 2 of 6** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 15:5 1:47 PROTO-IX 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 II I,!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 (IF)Shell Inlet Temp (IF)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-°F)Tube Mass Flow (lbmihr) Shell-Side ho (BTU/hr-ft 2--F)Tube-Side hi (BTU/hr-ft 2-°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hrft 2.°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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (OF)Skin Visc (Ibm/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'-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)5.325E+5 3.978E+5 1.304E+7 61.3 471.2 Overall Fouling (hr'ft 2.0 F/BTU)Shell-Side ho (BTU/hr-ft 2-*F)Tube-Side hi (BTU/hrft 2.°F)I/Wall Resis (BTU/hr ft 2.-F)LMTD Correction Factor 0.001075 2,003.3 2,216.1 25,594.8 0.9633 Property Shell-Side Tube-Side Velocity (ft/s) 4.98 8.21 Reynold's Number 8.020E+04 7.118E+04 Prandtl Number 2.20 3.77 Bulk Visc (Ibm/ft-hr) 0.85 1.39 Skin Visc (lbm/ft-hr) 0.94 1.21 Density (lbmi/ft) 60.62 61.77 Cp (BTU/Ibm 0'F) 1.00 1.00 K (BTU/hr'ft 0'F) 0.39 0.37** Reynolds Number Outside Range of Equation Applicability 1! 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 (IF)Tav Shell (IF)Shell Skin Temp (fF)Tube Temp In (°F)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Ternkjrdt1jPower Calc: 97-195

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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 15:53:34 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIX-0000)

Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler Tube-side Fouling = 0.0010 06/29/98.1 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 (OF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (OF)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 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 0-F)Tube-Side hi (BTU/hr-ft 2.'F)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.°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 (Ibm/ft hr) Tube Temp In (°F)Density (lbm/fl3)

Tube Temp Out (OF)Cp (BTUIlbm.°F)

Tav Tube (°F)K (BTU/hr-ft-°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')Property Shell-Side Velocity (ft/s) 4.98 Reynold's Number 8.120E+04 Prandtl Number 2.17 Bulk Visc (lbm/ft-hr) 0.84 Skin Visc (lbm/ft-hr) 0.91 Density (lbm/ft')

60.58 Cp (BTU/Ibm.°F) 1.00 K (BTU/hr.ft-°F) 0.39 5.325E+5 3.978E+5 1.112E+7 65.5 471.2 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2 0.F)Tube-Side hi (BTU/hr-ft 2.-F)1/Wall Resis (BTU/hr ft 2-OF)LMTD Correction Factor 0.001650 2,016.5 2,183.2 25,594.8 0.9770 Tube-Side 8.20 6.953E+04 3.87 1.43 1.27 61.80 1.00 0.37 U Overall (BTU/hrft 2 0.°F)Shell Temp In (OF)Shell Temp Out (°F)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (°F)Tav Tube (OF)Tube Skin Temp (IF)0n U I-0 0 0 I..04 0 368.8 190.0 169.2 179.6 167.6 100.0 128.0 114.0 126.7 ctl** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 15:54:32 PROTO-HIX 3.02 by Proto-Power Corporation (SN#PIIX-0000)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler Tube-side Fouling = 0.0015 06/29/98.1 Calculation Specifications 11 it.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 (IF)Shell Inlet Temp (IF)Input Fouling Factor 795.3 1,064.5 100.0 190.0 0.002225 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTUihr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2 0-F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2'.F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft2.°F/BTU)

Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (OF)Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (IF)Skin Visc (Ibm/ft-hr)

Tube Temp In (°F)Density (lbm/ft')

Tube Temp Out (°F)Cp (BTU/lbm-0 F) Tav Tube (°F)K (BTU/hr-ft'°F)

Tube Skin Temp (°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 3.978E+5 9.683E+6 68.7 471.2 Overall Fouling (hr-ft 2-°F/BTU)Shell-Side ho (BTU/hriftt.°F)

Tube-Side hi (BTU/hr.ft 2.F)I/Wall Resis (BTU/hr.ft 2.°F)LMTD Correction Factor U Overall (BTU/br-ft 2-0 F)0.002225 2,026.2 2,158.6 25,594.8 0.9842 Property Shell-Side Tube-Side Velocity (ft/s) 4.99 8.20 Reynold's Number 8.194E+04 6.830E+04 Prandtl Number 2.15 3.95 Bulk Visc (lbm/ft-hr) 0.83 1.45 Skin Visc (lbm/ft-hr) 0.89 1.31 Density (lbmlft 3) 60.55 61.83 Cp 1.00 1.00 K (BTU/hr'ft 0'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 (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In ('F)Tube Temp Out (°F)Tav Tube (IF)Tube Skin Temp (°F)0\~1)0 0 Cd 303.9 190.0 171.9 180.9 170.6 100.0 124.4 112.2 123.3 Cd 15:55:33 PROTO-HX 3.02 by Proto-Power Corporation (SN#PMIX-0000)

Commonwealth Edison Calculation Report for DG01A -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 (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 0.002782 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.°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-'F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ftihr)

Shell Skin Temp (IF)Skin Visc (lbm/ft-lr)

Tube Temp In (OF)Density (Ibm/fl 3) Tube Temp Out (IF)Cp (BTU/lbm-°F)

Tav Tube (IF)K (BTU/hr-ft.°F)

Tube Skin Temp (°F)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')Property Shell-Side Velocity (ft/s) 4.99 Reynold's Number 8.25 1EE+04 Prandtl Number 2.14 Bulk Visc (lbmr/ft-hr) 0.82 Skin Visc (Ibm/ft-hr) 0.88 Density (Ibm/ft 3) 60.53 Cp (BTU/Ibm.°F) 1.00 K (BTU/hr-ft.°F) 0.39 5.325E+5 3.978E+5 8.6E+6 71.1 471.2 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr.ft2.OF)

I/Wall Resis (BTU/hr ft 2.IF)LMTD Correction Factor 0.002782 2,033.3 2,140.0 25,594.8 0.9885 Tube-Side 8.20 6.738E+04 4.01 1.47 1.34 61.85 1.00 0.37 U Overall (BTU/hr ft 2.°F)Shell Temp In (IF)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (IF)Tube Temp In (°F)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (°F)U 0 0 04 C 4-4 0\0 259.7 190.0 173.9 181.9 172.9 100.0 121.6 110.8 120.8 44(** 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

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G Rev: A Page 1 of 17 09:31:42 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIHX-0000)

Commonwealth Edison Calculation Report for DG01A -DG Jacket Water Cooler CSCS = 35'F 06/29/98 I -._ .Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used 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 (IF)Shell Inlet Temp (IF)193.5 1,064.5 35.0 190.0 Fouling Calculation Results Shell Mass Flow (lbmlhr) 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-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.°F/BTU)Property Shell-Side Tube-Side Velocity (ft's) Shell Temp In (°F)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (OF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (°F)Skin Visc (lbm/ft-hr)

Tube Temp In (IF)Density (Ibm/ft 3) Tube Temp Out (°F)Cp (BTU/Ibm 0'F) Tav Tube (°F)K (BTU/hr'ft 0'F) Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow. (lbm/hr)Tube Mass Flow (lbrn/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 (Ibm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm 0'F)K (BTU/hrft°F)

Shell-Side 4.99 8.25 1E+04 2.14 0.82 0.88 60.53 1.00 0.39 5.325E+5 9.68E+4 8.6E+6 98.1 471.2 Tube-Side 1.98 1.155E+04 5.90 2.09 1.39 62.22 1.00 0.35 U Overall (BTU/hr-ft2.°F)

Shell Temp In (°F)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (IF)Tube Temp In (°F)Tube Temp Out (°F)Tav Tube (°F)Tube Skin Temp (°F)Proto-Power Calc: 97-195 191.1 190.0 173.9 181.9 172.3 35.0 123.9 79.4 117.0 Overall Fouling (hr-ft 2'°F/BTU)Shell-Side ho (BTU/hr1ft 2.°F)Tube-Side hi (BTU/hr'ft 2-OF)1/Wall Resis (BTU/hr-ft 2-°F)LMTD Correction Factor 0.002782 2,032.2 599.1 25,594.8 0.9740** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie

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G Rev: A Page 2 of 17 09:28:13 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-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 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)204.8 1,064.5 40.0 190.0 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/hr-ft 2.°F)Tube-Side hi (BTU/hr'ft 2.-F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr ft 2.°F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hrift 2'.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 (IF)Skin Visc (lbm/ft-hr)

Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (IF)Cp (BTU/lbm 0'F) Tav Tube (IF)K (BTU/hr-ft-°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 (Wt 2)Property Shell-Side Velocity (ft/s) 4.99 Reynold's Number 8.25 1E+04 Prandtl Number 2.14 Bulk Visc (lbm/ft-hr) 0.82 Skin Visc (Ibm/ft-hr) 0.88 Density (Ibm/fl 3) 60.53 Cp (BTU/Ibm-°F) 1.00 K (BTU/hr-ft.°F) 0.39 5.325E+5 1.024E+5 8.6E+6 96.0 471.2 Tube-Side 2.10 1.261E+04 5.70 2.02 1.38 62.20 1.00 0.36 Overall Fouling (hri ft 2-'F/BTU)Shell-Side ho (BTU/hr-ft 2-°F)Tube-Side hi (BTU/hr-ft 2 0.F)1/Wall Resis (BTU/hr'ft 2.°F)LMTD Correction Factor 0.002782 2,032.3 634.9 25,594.8 0.9744 U Overall (BTU/hr-ft 2.°F)Shell Temp In (°F)Shell Temp Out (IF)Tav Shell (°F)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (°F)Tav Tube (IF)Tube Skin Temp (fF)Proto-Power Calc: 97-195

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G Rev: A Page 3 of 17 195.1 190.0 173.9 181.9 172.3 40.0 124.0 82.0 117.3** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 09:23:51 PROTO-LIX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGO1A -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 (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 (lbmlhr) Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTUfhr) I/Wall Resis (BTU/hr-ft 2-°F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr.ft.F/BTU)

Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (°F)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (IF)Skin Visc (lbm/ftrhr)

Tube Temp In (°F)Density (lbm/ft')

Tube Temp Out (IF)Cp (BTU/lbm 0'F) Tav Tube (°F)K (BTU/hr'ft-°F)

Tube Skin Temp (°F)Extrapolation Calculation Results Shell Mass Flow (Ibm/hr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')5.325E+5 1.162E+5 8.6E+6 91.9 471.2 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr.ft2.°F)

I/Wall Resis (BTU/hr ft 2-OF)LMTD Correction Factor 0.002782 2,032.5 719.6 25,594.8 0.9756 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.°F)

Shell-Side Tube-Side 4.99 2.38 8.251E+04 1.520E+04 2.14 5.33 0.82 1.91 0.88 1.37 60.53 62.15 1.00 1.00 0.39 0.36 U Overall (BTU/hr-ft 2.°F) 203.6 Shell Temp In (OF) 190.0 Shell Temp Out (OF) 173.9 Tav Shell (OF) 181.9 Shell Skin Temp (IF) 172.4 Tube Temp In (°F) 50.0 Tube Temp Out (OF) 124.1 Tav Tube (IF) 87.0 Tube Skin Tem p (OF) 117.9 Proto-Power Calc: 97-195

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G Rev: A Page 4 of 17** Reynolds Number Outside Range of Equation Applicability

!I With Minimtm Fouling The Test Heat Load Could Not Be Achie 09:11:37 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIIX-0000)

Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler CSCS = 60'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 (IF)Shell Temp Out (°F)Tube Flow (gpm)Tube Temp In (°F)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (°F)Shell Inlet Temp (°F)269.1 1,064.5 60.0 190.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hrft 2 0-°F)Tube-Side hi (BTU/hr-ft 2-IF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2.OF)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 (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/ft-hr)

Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (OF)Cp (BTU/Ibm 0'F) Tav Tube (°F)K (BTU/hr'ft'°F)

Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (lbmihr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 1.346E+5 8.6E+6 87.8 471.2 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2.°F)I/Wall Resis (BTU/h1f0t 2-°F)LMTD Correction Factor U Overall (BTU/hr-ft 2-°F)0.002782 2,032.7 828.7 25,594.8 0.9770 212.7 Property Shell-Side Tube-Side Velocity (ft/s) 4.99 2.76 Reynold's Number 8.25 1 E+04 1.865E+04 Prandtl Number 2.14 5.00 Bulk Visc (lbmift-hr) 0.82 1.80 Skin Visc (lbm/ft-hr) 0.88 1.37 Density (Ibm/ft?)

60.53 62.09 Cp (BTU/Ibm 0'F) 1.00 1.00 K (BTU/hr"ft°F) 0.39 0.36** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Shell Temp In (OF) 190.0 Shell Temp Out (OF) 173.9 Tav Shell (OF) 181.9 Shell Skin Temp (OF) 172.5 Tube Temp In (OF) 60.0 Tube Temp Out (°F) 123.9 Tav Tube (OF) 92.0 Tube Skin Temp(°F) 118.5 Proto-Power Calc: 97-195

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G Rev: A Page 5 of 17 09:06:52 PROTO-HX 3.02 by Proto-Power Coriporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler CSCS = 70OF 06/29/98-I 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 (°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 (fF)Shell Inlet Temp (IF)321.0 1,064.5 70.0 190.0 IF -Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hrfte-°F)

Tube Mass Flow (ibm/hr) Shell-Side ho (BTU/hr ft 2-OF)Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) l/Wall Resis (BTU/hr-ft 2-IF)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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (°F)Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (IF)Skin Visc (Ibm/ft-hr)

Tube Temp In (°F)Density (Ibml/ft)

Tube Temp Out (OF)Cp (BTU/Ibm-°F)

Tav Tube (IF)K (BTU/hr'ft-°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)5.325E+5 1.606E+5 8.6E+6 83.7 471.2 Overall Fouling (hr-ft 2-F/BTU)Shell-Side ho (BTU/hr.ft 2-°F)Tube-Side hi (BTU/hr.ft 2.OF)I/Wall Resis (BTU/hr.ftO'IF)

LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)0.002782 2,032.8 975.6 25,594.8 0.9790 222.6 Property Shell-Side Tube-Side Velocity (ft/s) 4.99 3.30 Reynold's Number 8.25 1E+04 2.348E+04 Prandtl Number 2.14 4.71 Bulk Visc (Ibm/ft-hr) 0.82 1.71 Skin Visc (lbm/ft-hr) 0.88 1.36 Density (lbm/ft 3) 60.53 62.03 Cp (BTU/Ibm 0'F) 1.00 1.00 K (BTU/hr-ft.°F) 0.39 0.36** Reynolds Number Outside Range of Equation Applicability

!! With Minimum Fouling The Test Heat Load Could Not Be Achie Shell Temp In (°F) 190.0 Shell Temp Out (OF) 173.9 Tav Shell (IF) 181.9 Shell Skin Temp (OF) 172.6 Tube Temp In (IF) 70.0 Tube Temp Out (°F) 123.6 Tav Tube (IF) 96.8 Tube Skin Temp (°F) 119.2 Proto-Power Calc: 97-195

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G Rev: A Page 6 of 17 09:03:56 PROTO-HX 3.02 by Proto-Powver Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGO 1 A -DG Jacket Water Cooler CSCS = 80°06/29/98 t ---_ __ ___ -----1 Calculation Specifications II[I.t 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 (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (°F)399.3 1,064.5 80.0 190.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2-0 F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTUfr.ftt.°F)

Tube-Side hi (BTU/hr ft 2.-F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2-OF)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hrift 2-°F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (IF)Bulk Vise (Ibm/ft-hr)

Shell Skin Temp (OF)Skin Vise (Ibmn/ft-hr)

Tube Temp In (°F)Density (lbm/ft 3) Tube Temp Out (OF)Cp (BTU/Ibm.°F)

Tav Tube (IF)K (BTU/hr'ft'°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)5.325E+5 1 .997E+5 8.6E+6 79.6 471.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-lhi)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm 0-F)K (BTU/hr.ft.°F)

Shell-Side Tube-Side 4.99 4.11 8.251E+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 Overall Fouling (hr-ft 2-°F/BTU)Shell-Side ho (BTU/hrift 2 0 F)Tube-Side hi (BTU/hr'ft 2"-F)I/Wall Resis (BTU/hr-ft 2-OF)LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (OF)0.002782 2,033.0 1,186.3 25,594.8 0.9814 0.-It (4.4 0 4)4)233.5 190.0 173.9 181.9 172.7 80.0 123.1 101.5 119.8** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 09:00:52 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DG0lA -DG Jacket Water Cooler CSCS = 90'F 06/29/98 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 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)530.9 1,064.5 90.0 190.0 Fouling Calculation ResultsI Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr-ft 2-0 F)Tube-Side hi (BTU/hr-ft 2-°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-fe-°F)

LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr'ft1-°F/BTU)

Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (°F)Bulk Visc (lbrr'fthr)

Shell Skin Temp (IF)Skin Visc (Ibm/ft hr) Tube Temp In (IF)Density (lbrn/ft')

Tube Temp Out (°F)Cp (BTU/1bm-'F)

Tav Tube (°F)K (BTU/hr-ftr'F)

Tube Skin Temp (°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 Shell-Side Tube-Side Velocity (ft/s) 4.99 5.47 Reynold's Number 8.25 1E+04 4.293E+04 Prandtl Number 2.14 4.22 Bulk Visc (lbm/ft-hr) 0.82 1.54 Skin Visc (lbm/ft-hr) 0.88 1.34 Density (Ibm/ft 3) 60.53 61.91 Cp (BTU/Ibm 0'F) 1.00 1.00 K (BTU/hr'ft.°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.°F/BTU)Shell-Side ho (BTU/hr.ft 2.OF)Tube-Side hi (BTU/hr-ft 2.-F)I/Wall Resis (BTU/hr-ft 2.°F)LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (°F)Shell Skin Temp (°F)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (IF)U D"-C 0 0 00 0 t 00 -0.002782 2,033.2 1,519.8 25,594.8 0.9845 245.7 190.0 173.9 181.9 172.8 90.0 122.4 106.2 120.3 08:54:07 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIHX-0000)

Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler CSCS = 100°F 06/29/98 Calculation Specifications HI 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 (IF)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (°F)Shell Inlet Temp (OF)795.3 1,064.5 100.0 190.0 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.°F)Tube-Side hi (BTU/hr.ft 2.°F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hrI.ft 2.°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 (°F)Reynolds Number Shell Temp Out (IF)Prandtl Number Tav Shell (°F)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (°F)Skin Visc (lbm/ft-hr)

Tube Temp In (°F)Density (lbm/ft 3) Tube Temp Out (°F)Cp (BTU/lbm 0'F) Tav Tube (°F)K (BTU/hr'ft'°F)

Tube Skin Temp (°F)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 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 (Ibm/fl 3)Cp (BTU/lbm'°F)

K (BTU/hr-ft-°F)

Shell-Side Tube-Side 4.99 8.20 8.251 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'.F/BTU)Shell-Side ho (BTU/hr-ft 2-°F)Tube-Side hi (BTU/hrft 2.F)I/Wall Resis (BTU/hr-ft 2-°F)LMTD Correction Factor U Overall (BTU/hr.ft 2.°F)Shell Temp In (IF)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (°F)Tav Tube (IF)Tube Skin Temp (OF)0.002782 2,033.3 2,140.0 25,594.8 0.9885 0'0 0%+6 cr 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-HX 3.02 by Proto-Powver Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 35°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 (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)161.1 1,064.5 35.0 190.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr ft 2-°F)Tube Mass Flow (lbr/lhr)

Shell-Side ho (BTU/hii.ft 2*.F)Tube-Side hi (BTU/hr-ft 2.°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.°F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (°F)Bulk Visc (lbm/ftrhr)

Shell Skin Temp (°F)Skin Visc (Ibm/ft-hr)

Tube Temp In (°F)Density (lbmr/ft 3) Tube Temp Out (°F)Cp (BTU/Ibm 0'F) Tav Tube (°F)K (BTU/hr'ft-°F)

Tube Skin Temp (°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 8.059E+4 7.8E+6 93.3 471.2 Property Shell-Side Tube-Side Velocity (ft/s) 4.99 1.65 Reynold's Number 8.292E+04 1.010E+04 Prandtl Number 2.13 5.59 Bulk Visc (lbm/ft-hr) 0.82 1.99 Skin Visc (lbm/ft-hr) 0.87 1.31 Density (Ibmn/ft')

60.52 62.18 Cp (BTU/lbm.°F) 1.00 1.00 K (BTU/hr.ft.°F) 0.39 0.36** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Overall Fouling (hr'ft 2.°F/BTU)Shell-Side ho (BTU/hrwft 2 F)Tube-Side hi (BTU/hr-ft 2.°F)1/Wall Resis (BTU/hr ft 2-°F)LMTD Correction Factor U Overall (BTU/hr.ft 2.°F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (°F)Tav Tube (IF)Tube Skin Temp CF)0.002782 2,037.1 531.4 25,594.8 0.9713 182.6 W)ON 0~0 C4-4 0 to)190.0 175.4 182.7 173.8 35.0 131.8 83.4 122.7 10:45:26 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-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)169.8 1,064.5 40.0 190.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr.-°tF)

Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft'.°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')Overall Fouling (hr'ft 2.°F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (°F)Bulk Vise (lbm/ft-hr)

Shell Skin Temp (IF)Skin Vise (lbm/ft-hr)

Tube Temp In (°F)Density (lbm/ft 3) Tube Temp Out (°F)Cp (BTU/lbm.°F)

Tav Tube (IF)K (BTU/hr-ft.°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 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 (lbm/ft')

60.52 Cp (BTU/lbm.0 F) 1.00 K (BTU/hr-ft-°F) 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.F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2-°F)I/Wall Resis (BTU/hr'ft 2 a'F)LMTD Correction Factor U Overall (BTU/hr ft 2.IF)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (°F)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)0.002782 2,037.2 561.0 25,594.8 0.9716 0\K-0\U 0 I...P-0 t'-11 186.5 190.0 175.4 182.7 173.8 40.0 131.9 86.0 122.9 0 V** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:40:50 PROTO-HX 3.02 by Proto-Power Corporation (SN#fPHX-0000)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 50'F 06/29/98 I 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 (OF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (OF)Shell Inlet Temp (OF)190.5 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 (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.°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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (OF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (fF)Skin Vise (Ibm/ft-hr)

Tube Temp In (fF)Density (Ibm/ft 3) Tube Temp Out ("F)Cp (BTU/Ibm-°F)

Tav Tube (°F)K (BTU/hr'ft-0 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)5.325E+5 9.527E+4 7.8E+6 87.5 471.2 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-°F)

K (BTU/hr-ft.°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-it 2.OF)Tube-Side hi (BTU/hrft'-°F)

I/Wall Resis (BTU/hr'ft 2 a'F)LMTD Correction Factor U Overall (BTU/hr-ft2.°F)

Shell Temp In (fF)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (OF)Tube Skin Temp (fF)tn U 0 0 4..I.-0.002782 2,037.4 629.9 25,594.8 0.9726 0 C14 194.6 190.0 175.4 182.7 173.9 50.0 131.9 91.0 123.6 V-** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:24:06 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 60°F 06/29/98.1 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 (OF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (OF)Shell Inlet Temp (OF)217.5 1,064.5 60.0 190.0 Fouling Calculation Results Shell Mass Flow (Ibm/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 0 F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr ft 2.OF)LMTD LMTD Correction Factor Effective Area (ft1)Overall Fouling (hr-ft 2.°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/Ibm-'F)

Tav Tube (OF)K (BTU/hr'ft'°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)Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbmlft-hr)

Density (Ibm/ft')Cp (BTU/Ibm 0'F)K (BTU/hr-ft.°F)

Shell-Side 4.99 8.292E+04 2.13 0.82 0.87 60.52 1.00 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'ft 2.°F/BTU)Shell-Side ho (BTU/hr.ft 2.°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.°F)Shell Temp In (0 F)Shell Temp Out (°F)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (°F)Tube Skin Temp (OF)Irn ON U 0-0 2 0q 0.002782 2,037.6 716.3 25,594.8 0.9739 0 P.4 203.3 190.0 175.4 182.7 174.0 60.0 13,1.8 95.9 124.2** Reynolds Number Outside Range of Equation Applicability 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 = 70'F 06/29/98 Calculation Specifications II I.I 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)254.2 1,064.5 70.0 190.0 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-°F)Tube-Side hi (BTU/hr-ft 2-0 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-*F/BTU)Property Shell-Side Tube-Side Velocity (tf/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/ftrhr)

Tube Temp In (IF)Density (lbmr/ft)

Tube Temp Out (IF)Cp (BTU/Ibm-°F)

Tav Tube (IF)K (BTU/hr-ft.°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')5.325E+5 1.272E+5 7.8E+6 79.7 471.2 Property Shell-Side Tube-Side Velocity (ft/s) 4.99 2.62 Reynold's Number 8.292E+04 1.940E+04 Prandtl Number 2.13 4.50 Bulk Visc (Ibm/ft-hr) 0.82 1.63 Skin Visc (lbm/ft-hr) 0.87 1.29 Density (lbm/ft 3) 60.52 61.99 Cp (BTU/lbm.°F) 1.00 1.00 K (BTU/hr-ft-°F) 0.39 0.36** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Overall Fouling (hr-ft 2 0.F/BTU)Shell-Side ho (BTU/hr-ft 2°F)Tube-Side hi (BTUThr-ft 2-°F)1/Wall Resis (BTU/hr-ft 2-OF)LMTD Correction Factor U Overall (BTU/hr-ft 2-OF)Shell Temp In (°F)Shell Temp Out (OF)Tav Shell (°F)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (°F)U0~0~S-.CJ 4-0.002782 2,037.8 829.2 25,594.8 0.9757 0 212.8 190.0 175.4 182.7 174.1 70.0 131.4 100.7 124.9 10:12:25 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOI A -DG Jacket Water Cooler CSCS = 80'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 (OF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (OF)Shell Inlet Temp (OF)307.0 1,064.5 80.0 190.0 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-°F)Tube-Side hi (BTUIhr.fte-OF)

Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr'ft 2-F)LMTD LMTD Correction Factor Effective Area (ftf)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-(°F)Prandtl Number Tav Shell (fF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (OF)Skin Vise (lbnmft-hr)

Tube Temp In (OF)Density (lbmlft 3) Tube Temp Out (OF)Cp (BTU/lbm 0'F) Tav Tube (OF)K (BTU/hr-ft'°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 (Wt 2)5.325E+5 1.536E+5 7.8E+6 75.8 471.2 Overall Fouling (hr'ft 2 0'F/BTU)Shell-Side ho (BTU/hr'ft2-OF)

Tube-Side hi (BTU/hr.ft 2.OF)I/Wall Resis (BTU/hrft 2 0.OF)LMTD Correction Factor 0.002782 2,038.0 984.2 25,594.8 0.9779 Property Shell-Side Tube-Side Velocity (ft/s) 4.99 3.16 Reynold's Number 8.292E+04 2.462E+04 Prandtl Number 2.13 4.26 Bulk Visc (lbm/ft-hr) 0.82 1.56 Skin Visc (lbm/ft-hr) 0.87 1.28 Density (lbm/ft 3) 60.52 61.92 Cp (BTU/Ibm 0'F) 1.00 1.00 K (BTU/hr-ft 0'F) 0.39 0.37** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie U Overall (BTU/hr-ft2-°F)

Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (OF)Tube Skin Temp (°F)trn 0%Cd 0%0 0 a'.'223.2 190.0 175.4 182.7 174.2 80.0 130.8 105.4 125.6 10:08:33 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOIA -DG Jacket Water Cooler CSCS = 90°F 06/29/98 I.Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Design Fouling Factors Were Used II 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)389.3 1,064.5 90.0 190.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr ft 2-OF)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr'ft 2.F)Tube-Side hi (BTU/hr-ftz.°F)

Heat Transferred (BTU/hr) I/Wall Resis (BTJ/hr.ft 2.°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 (°F)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (°F)Bulk Visc (Ibm/ft-hr)

Shell Skin Temp (OF)Skin Visc (Ibm/ft hr) Tube Temp In (OF)Density (lbm/ft) Tube Temp Out (OF)Cp (BTU/Ibm'°F)

Tav Tube (OF)K (BTU/hr-ft.

0 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 (ft')5.325E+5 1.947E+5 7.8E+6 71.9 471.2 Property Shell-Side Tube-Side Velocity (ft/s) 4.99 4.01 Reynold's Number 8.292E+04 3.273E+04 Prandtl Number 2.13 4.04 Bulk Visc (Ibm/ft-hr) 0.82 1.48 Skin Visc (Ibm/ft-hr) 0.87 1.27 Density (Ibm/ft3) 60.52 61.86 Cp (BTU/lbm-0 F) 1.00 1.00 K (BTU/hr-ft.°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.°F/BTU)Shell-Side ho (BTU/hr-ft2.

0 F)Tube-Side hi (BTU/hr-ft 2.*F)1/Wall Resis (BTU/hr-ft 2.-F)LMTD Correction Factor U Overall (BTU/hr-ft 2-IF)Shell Temp In (OF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (`F)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (°F)tn U 0 a, 0 C 4-4 0 0.002782 2,038.2 1,213.3 25,594.8 0.9808 234.8 190.0 175.4 182.7 174.3 90.0 130.1 110.1 126.2 43 10:03:05 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIIX-0000)

Commonwealth Edison Calculation Report for DGO1A -DG Jacket Water Cooler CSCS = 100'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) 534.5 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In ('F) Tube Inlet Temp (OF) 100.0 Shell Temp Out (OF) Shell Inlet Temp ('F) 190.0 Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out ('F)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-ft 2.°F)Tube-Side hi (BTU/hr-ft 2-°F)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.°F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (°F)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')

Tube Temp Out (OF)Cp (BTU/lbm 0'F) Tav Tube (OF)K (BTU/hr'ft-°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 2.674E+5 7.8E+6 67.8 471.2 Overall Fouling (hr'ft 2.°F/BTU)Shell-Side ho (BTU/hr'ft 2 0.F)Tube-Side hi (BTU/hr-ft 2.°F)I/Wall Resis (BTU/hr-ft 2-°F)LMTD Correction Factor 0.002782 2,038.4 1,592.6 25,594.8 0.9844 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/Ibm-'F)

K (BTU/hr'ft'°F)

Shell-Side 4.99 8.292E+04 2.13 0.82 0.87 60.52 1.00 0.39 Tube-Side 5.52 4.701E+04 3.85 1.42 1.27 61.79 1.00 0.37 U Overall (BTU/hr-ft 2-°F)Shell Temp In (OF)Shell Temp Out ('F)Tav Shell (°F)Shell Skin Temp (°F)Tube Temp In (°F)Tube Temp Out (OF)Tav Tube (°F)Tube Skin Temp (°F)t0-4 U 0 0 a4-I-.a42 247.9 190.0 175.4 182.7 174.4 100.0 129.2 114.6 126.8** 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 Cale: 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. 1 Attachment B, B2 Analysis No.:'97-197 Revision:

2 A04 Title: I Thermal Model of ComEd/LaSalle Station HPCS Diesel Generator Jacket Water Coolers ECIECR No.: ' 388666 Revision:

000 Station(s):'

LaSalle Unit No.: 1 01 & 02 Safety/QA Class: SR System Code(s): HP, DG, E22 Is this Design Analysis Safeguards Information?" Yes [] No g If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?

12 Yes El No 1Z If yes, ATI/AR#: N/A This Design Analysis SUPERCEDES:

,3 N/A in its entirety.Description of Changes (list affected pages):4 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 -3, Attachment A, Pages Al -A2, and Attachment B, Pages B1-B2 Disposition of Changes: Is See attached pages. The changes made are acceptable.

Prearer.:"-ata\

1M Print Name Sign Name Method of Review: " Detailed Review j Alternate Calculations El Testing El Reviewer:.

SE2ote-C-V 2 --E ./2-Print Name Sign Name Date Review Independent review Peer review 0l Notes: 19 (For External Analyses Only)External Approver:

20 PA_Print Name Sign Name Date Exelon Reviewer' 2111 Print Name Sign Name Date Exelon Approver:

`2 .sciAi __& 5-1 /8l. ,-.Print Name i4 Sign Name Date 97-197 Rev. A04 Page 2 of 3 Purpose: The purpose of this revision is to verify that the 1(2)E22-S001 coolers can remove the design heat load of 7,800,000 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)* Cooling water flow rate = 650 gpm* (References 1, 3, and 4)* Jacket water temperature for 1(2)E22-S001

= 190 °F (Reference 1)* Jacket water flow rate for 1(2)E22-SO01

= 1100 gpm (Reference 1)* Fouling factor for 1(2)E22-SO01

= 0.00223 hrft 2.OF/BTU** (Reference 1, 3, and 4)* 4 tubes plugged (1% tube plugging) (Reference 1)*The flow rate for this cooler was reduced to 550 gpm for both units per References 3 and 4. An additional case is run with this flow rate and a CSCS temperature of 107 OF.**The fouling factor for this cooler was increased to 0.00196 hrft 2per References 3 and 4. An additional case is run with this fouling factor and a CSCS temperature of 107 OF.

References:

1. Design analysis97-197, Rev. A, up to and including Rev A03 2. EC 388666, Rev. 000 3. EC 370853, Rev. 000 4. EC 384525, Rev. 000 5. EC 382117, Rev. 000 Identification of Computer Pro-grams:

The computer program used in this analysis is Proto HX version 4.01. This program has been validated per DTSQA tracking number EXOOOO103.

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.Results /

Conclusions:

The 1(2)E22-SO01 coolers can remove the design heat load of 7,800,000 BTU/hr with the following conditions:

107 OF cooling water temperature

650 gpm and 550 gpm cooling water flow* fouling factor of 0.00223 hr-ft 2.°F/BTU and 0.00196 hr-ft 2-°F/BTU* 4 tubes plugged 0 jacket water temperature of 190 OF 0 jacket water flow rate of 1100 gpm The total heat removed at 650 gpm with a fouling factor of 0.00223 hr-ft 2.F/BTU is 7,916,590 BTU/hr, which provides 1.5% thermal margin over the design heat load. The total heat removed at 550 gpm with a fouling factor of 0.00196 hr-t 2 OF/BTU is 7,936,128 BTU/hr, which provides 1.7% thermal margin over the design heat load.The model benchmark was shown to conservatively underestimate the heat transfer of the cooler by 2.68%.Therefore, any positive margin shown in the model would be an underestimate of actual thermal performance, which would show more margin than what is calculated.

Additionally, the most recent thermal performance ( evaluation (Ref. 5) shows a maximum fouling factor of 0.000447 hr-ft2.°F/BTU, which also shows that additional margin exists. The calculated thermal margin of 1.5% and 1.7% for the two cases is acceptable.

The maximum fouling factor of 0.00196 hrft 2.OF/BTU shall be used for acceptance criteria in thermal performance evaluations after ECs 370853 and 384525 have been implemented on Units 1 & 2, respectively.

The two cases are shown in Attachments A and B.97-197 Rev. A04 Page 3 of 3 Attachments:

A. Data Report for 1(2)E22-SO01 at 650 gpm with FF = 0.00223 hr-ft 2.OF/BTU (2 pgs)B. Data Report for 1(2)E22-SO01 at 550 gpm with FF = 0.00196 hr-ft 2-OF/BTU (2 pgs) 05-01-2012 10:37:30 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-1002)

Commonwealth Edison Data Report for DG01B -LSCS -HPCS DG Hx.IB, 2B DG -107 OF tube side, 650 gpm, 190 OF shell side, 1100 gpm, FF = 0.00223, 4 tubes plugged I.1 Shell and Tube Heat Exchanger Input Parameters II Shell-Side Tube-Side Fluid Quantity, Total gpm 1,064.46 795.25 Mass Fluid Quantity, Total Ibm/hr 0.00 0.00 Inlet Temperature OF 190.00 100.00 Outlet Temperature OF 175.00 121.00 Fouling Factor hr.ft 2.°F/BTU 0.00050 0.00193 Shell Fluid Name Tube Fluid Name Design Q (BTU/hr)Design U (BTU/hr'ft 2"°F)Outside h Factor (Hoff)Fixed U (BTU/hr-ft 2.°F)Fixed Area (ft 2)Performance Factor (% Reduction)

Heat Exchanger Type Total Effective Area per Unit (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 K (BTU/hr'fr'°F)

Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0 0.00 0.00 TEMA -E 468.17 0.973212339 0.00000 1 0.438000000 5.600 0.7500 Triangular 2 No 420 416 7.00 0.541 0.625 58.00 Lbc, Central Baffle Spacing (in)Lbi, Inlet Baffle Spacing (in)Lbo, Outlet Baffle Spacing (in)Dotl, Tube Circle Diameter Bh, Baffle Cut Height (in)Ds, Shell Inside Diamter (in)Lsb, Diametral difference between Baffle and Shell (in)Ltb, Diametral difference between Tube and Baffle (in)Nss, Number Sealing Strips 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 0.000 97-197 Rev. A04 Attachment A Page Al of A2 05-01-2012 10:37:30 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-1002)

Page I Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.IB, 2B DG -107 IF tube side, 650 gpm, 190 IF shell side, 1100 gpm, FF = 0.00223, 4 tubes plugged 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 (°F)Shell Inlet Temp (IF)Input Fouling Factor 645.10 1,064.50 107.00 190.00 0.002230 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft2-°F)

Tube Mass Flow (ibm/hr) Shell-Side ho (BTU/hr. ft 2.°F)Tube-Side hi (BTU/hr.ft2.*F)

Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2.0 F)LMTD LMTD Correction Factor Effective Area (ft2)Overall Fouling (hr-ft 2.°F/BTU)Property Shell-Side Tube-Side Velocity (fi/s) Shell Temp In (IF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ftlhr)

Shell Skin Temp (IF)Skin Visc (Ibm/ft hr) Tube Temp In (IF)Density (Ibm/ft 3) Tube Temp Out (IF)Cp (BTU/Ibm'°F)

Tav Tube (IF)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/ifthr)

Skin Visc (lbm/ft'hr)

Density (Ibm/fl 3)Cp (BTU/Ibm'0 F)K (BTU/hrifi.

0 F)532,515.63 322,710.98 7,916,590.94 63.2 463.7 Shell-Side Tube-Side 5.58 4.37 77,252 32,323 2.1276 3.6616 0.8197 1.3556 0.8730 1.1913 60.5172 61.7228 1.0025 0.9988 0.3862 0.3698 Overall Fouling (hr-ftl 2.F/BTU)Shell-Side ho (BTU/hr-ft 2.0 F)Tube-Side hi (BTU/hr-ft 2.°F)I/Wall Resis (BTU/hr-ft 2'.F)LMTD Correction Factor U Overall (BTU/hr-ftl 2.F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)274.4 190.0 175.2 182.6 173.4 107.0 131.6 119.3 133.5 0.002230 1,891.2 1,408.2 15,431.0 0.9847** Reynolds Number Outside Range of Equation Applicability With Zero Fouling The Test Heat Load Could Not Be Achieved 97-197 Rev. A04 Attachment A Page A2 of A2 05-01-2012 10:41:41 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-1002)

Commonwealth Edison Data Report for DGOIB -LSCS -HPCS DG Hx.IB, 2B DG -107 OF tube side, 550 gpm, 190 OF shell side, 1100 gpm, FF = 0.00196, 4 tubes plugged Shell and Tube Heat Exchanger Input Parameters Shell-Side Tube-Side Fluid Quantity, Total gpm 1,064.46 795.25 Mass Fluid Quantity, Total Ibm/hr 0.00 0.00 Inlet Temperature OF 190.00 100.00 Outlet Temperature OF 175.00 121.00 Fouling Factor hr-ft'2.F/BTU 0.00050 0.00193 Shell Fluid Name Tube Fluid Name Design Q (BTU/hr)Design U (BTU/hr.ft 2 -F)Outside h Factor (Hoff)Fixed U (BTU/hr ft 2 .F)Fixed Area (ft 2)Performance Factor (% Reduction)

Heat Exchanger Type Total Effective Area per Unit (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 K (BTU/hr-ft 0.F)Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0 0.00 0.00 TEMA -E 468.17 0.973212339 0.00000 1 0.438000000 5.600 0.7500 Triangular 2 No 420 416 7.00 0.541 0.625 58.00 Lbc, Central Baffle Spacing (in)Lbi, Inlet Baffle Spacing (in)Lbo, Outlet Baffle Spacing (in)Dotl, Tube Circle Diameter Bh, Baffle Cut Height (in)Ds, Shell Inside Diamter (in)Lsb, Diametral difference between Baffle and Shell (in)Ltb, Diametral difference between Tube and Baffle (in)Nss, Number Sealing Strips 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 0.000 97-197 Rev. A04 Attachment B Page B1 of B2 05-01-2012 10:41:41 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-1002)

Commonwealth Edison Page 1 Calculation Report for DGOIB -LSCS -HPCS DG Hx.IB, 2B DG -107 OF tube side, 550 gpm, 190 IF shell side, 1100 gpm, FF = 0.00196, 4 tubes plugged 01--A IF-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 ("F)Shell Inlet Temp ("F)Input Fouling Factor 545.90 1,064.50 107.00 190.00 0.001960 11 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr.ft2.F)

Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr'ft 2"°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2-IF)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hrif't.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/f hr) Shell Skin Temp (IF)Skin Visc (Ibm/ft hr) Tube Temp In (IF)Density (Ibm/fl 3) Tube Temp Out ("F)Cp (BTU/Ibm'°F)

Tav Tube (IF)K (BTU/hr'ft'°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 2)Property Shell-Side Velocity (Ifts) 5.58 Reynold's Number 77,243 Prandtl Number 2.1278 Bulk Visc (lbm/ft-hr) 0.8198 Skin Visc (lbm/ftrhr) 0.8737 Density (Ibm/ft 3) 60.5176 Cp (BTU/Ibm'"F) 1.0025 K (BTU/hr'ft-'F) 0.3862 532,515.63 273,086.22 7,936,128.27 60.7 463.7 Tube-Side 3.70 27,941 3.5771 1.3270 1.1487 61.6875 0.9988 0.3705 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2.°F)I/Wall Resis (BTU/hr'ft 2.°F)LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)0.001960 1,890.9 1,248.7 15,431.0 0.9802 287.5 Shell Temp In ("F)Shell Temp Out ("F)Tav Shell (IF)Shell Skin Temp ("F)Tube Temp In ("F)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)190.0 175.1 182.6 173.3 107.0 136.1 121.5 137.8 97-197 Rev. A04 Attachment B Page B2 of B2** Reynolds Number Outside Range of Equation Applicability With Zero Fouling The Test Heat Load Could Not Be Achieved CC-AA-309-1 001 Revision 6 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page 1 Design Analysis (Minor Revision)

Last Page No. 1 Analysis No.:'97-197 Revision:

2 A03 Title: 3 Thermal Model of Corn Ed / LaSalle Station HPCS Diesel Generator Jacket Water Coolers ECIECR No.: ' EC 384525 Revision:'

000 Station(s):

7 LaSalle Unit No.: 8 02 Safety/QA Class: ' SR System Code(s): 10 HP, E22, DG Is this Design Analysis Safeguards Information?" Yes [] No 0 If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?

'2 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): 4 EC 384525 revised the flows in Division 3 of the Unit 2 CSCS. This revision makes the changes made in Revision A02 applicable to both Units.Disposition of Changes:" As shown in Attachment A of Revision A02, the changes made are acceptable.

The revised flows in combination with the reduced fouling factor allow the heat exchanger to remove the design basis heat load.System engineering has agreed to accept more stringent criteria for the cleanliness of the 2E22-S001 cooler.Preparer:

16 Sean Tanton 4 x Print Name Sidi-Nm 44ý -t Method of Review: 11 Detailed Review Z] Alternate Testing [Review Independent review Z Peer review [I Notes: " (For Extemal Analyses Only)External Approver:

20 N/A N/A N/A Print Name Sign Name Date Exelon Reviewer 2' N/A N/A N/A Print Name Sion Name Date Exelon Approver:

Dan Schmit 3 /Print Name " Sign Name te CC-AA-309-1 001 Revision 6 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page 1 Design Analysis (Minor Revision)

Last Page No. 6 Attachment A, pg A2 Analysis No.: I 97-197 Revision:

2 A02 Title: I Thermal Model of ComEd / LaSalle Station HPCS Diesel Generator Jacket Water Coolers EClECR No.: 4 370853 Revision:

000 Station(s):'

LaSalle Unit No.: 1 01 Safety/QA Class: 9 SR System Code(s): 10 HP, E22, DG Is this Design Analysis Safeguards Information? " Yes [] No s If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?

"2 Yes [] No s If yes, ATI/AR#: N/A This Design Analysis SUPERCEDES:

"3 N/A in its entirety.Description of Changes (list affected pages): " To recover margin in Division 3 of Unit 1 of the CSCS, EC 370853 revises the flows of the 1 E22-S001 cooler.100 gpm will be diverted from the 1E22-S001 cooler. Of this 100 gpm, 50 gpm will be returned to the 1E22-C002 pump, while the other 50 gpm will be given to the 1VY02A cooler. This revision determines if the revised flows are acceptable and can remove the required amount of heat for the heat exchangers.

This revision only applies to Unit 1. The flows shown for Unit 2 remain valid and are not impacted by this revision.Disposition of Changes: 15 Attachment A shows that a sufficient heat transfer rate can be achieved by reducing the fouling factor to 0.00196 hr*ft 2*OF/BTU. By inputting 546.26 9pm tube flow, 104 OF tubeside inlet water temperature, 4 tubes plugged, and a fouling factor of 0.00196 hr*ft*OF/BTU the resulting heat transfer rate is approximately 8.21 E+06 BTU/hr, which maintains the 5% margin above the design heat transfer rate. System engineering has agreed to accept more stringent criteria for the cleanliness of the 1 E22-S001 cooler. Therefore, the changes to the flows are acceptable and can remove the required amount of heat.Preparer:

Sean Tanton Print Name Sign Name 0 e Method of Review: 17 Detailed Review [ Alternate Calculations Testing I]Reviewer:

,8 Matthew Cosenza "o Print Name Sigate Review Independent review s Peer review El Notes: 19 (For External Analyses 00ly)External Approver:

N/A , N/A N/A Print Name Sign Name Date Exelon Reviewer N/A N/A N/A Print Name Sin Name Date Exelon Approver:

22 Dan Schmit Print Name j/" Sign Name " te r 97-197 Rev. A02 Page 2 of 2 Purpose: To recover margin in Division 3 of Unit 1 of the CSCS, EC 370853 revises the flows of the 1 E22-Soo1 cooler. 100 gpm will be diverted from the 1E22-SO01 cooler. Of this 100 gpm, 50 gpm will be returned to the 1 E22-C002 pump, while the other 50 gpm will be given to the 1 VY02A cooler. This minor revision documents the change in flow. These flow revisions were selected by system engineering and are specified in reference 2.This revision only applies to Unit 1. A later EC and revision to this calculation will incorporate the changes on Unit 2.Inputs: Tubeside flow 1 = 550 gpm (Ref. 2)Plugging allowance

= 1% (4 tubes) (Ref. 1)Tubeside inlet water temperature

= 104 OF (Ref. 1)Overall fouling factor 2 = 0.00223 hr*fe**F/BTU (Ref. 1)Design heat load 3 = 7.8E+06 BTU/hr (Ref. 1)Note that since Proto HX assumes a water density at 60 OF, the impact on the required mass flow due to the density change at a CSCS water temperature of 104 OF was evaluated and the actual flow input in Proto-HX was 546.26 gpm.2 A fouling factor of 0.00223 hrift 2*OF/BTU was used as a starting point for iterations to achieve the design heat transfer + 5% margin. The fouling factor that resulted in the desired margin (5%, see note 3) was 0.00196 hr*ft 2*°F/BTU 3 The design heat load for the Division 3 jacket water coolers is 7.8E+06 BTU/hr, however, the desired heat load is a 8.189E+06 BTU/hr to maintain 5% thermal margin at 100% operating conditions.

The 5%margin accounts for uncertainty in the Proto HX heat transfer calculations. (Ref. 1)Assumptions:

There are no assumptions associated with this revision.

References:

1. .97-197, Rev. A, up to and including Revs AOO through A01, Thermal Model of CoinEd / LaSalle Station HPCS Diesel Generator Jacket Water Coolers 2. AT 595380-11-13, CSCS HIT team -Use values provided by System Engineering to determine the new Div 3 accident penalty 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 EX00001 03.Method of Analysis I Numerical Analysis: The existing heat exchanger model will be revised by changing the input of the "Tube Flow" from 646.1 gpm to 546.26 gpm. Iterations are made by adjusting the fouling factor to achieve the desired heat transfer rate. The results are detailed below.Results I

Conclusion:

Attachment A shows that a sufficient heat transfer rate can be achieved by reducing the fouling factor to 0.00196 hr*ft 2*°F/BTU. By inputting 546.26 gpm tube flow, 104 OF tubeside inlet water temperature, 4 tubes plugged, and a fouling factor of 0.00196 hr*ft2*°F/BTU the resulting heat transfer rate is approximately 8.21 E+06 BTU/hr, which maintains the 5% margin above the design heat transfer rate.Attachments:

rf A. Proto HX Calculation Report (2 pages) 02-14-2011 04:25:25 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Page I Calculation Report for DGO1B -LSCS -HPCS DG Hx.546.26 gpm Tube Flow, 104 F Tube Temp, FF = 0.00196, 4 Tubes Plugged Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 546.26 Shell Flow (gpm) Shell Flow (gpm) 1,064.50 Shell Temp In (OF) Tube Inlet Temp (*F) 104.00 Shell Temp Out (IF) Shell Inlet Temp (IF) 190.00 Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (IF) Input Fouling Factor 0.001960 Fouling Calculation Results Shell Mass Flow (ibm/hr) U Overall (BTU/hr.ft 2.°F)Tube Mass Flow (Ibm/hr) Shell-Side ho (BTU/hr.ft2.°F)

Tube-Side hi (BTU/hr-ft 2-0 F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2.°F)LMTD LMTD Correction Factor Effective Area (ftW)Overall Fouling (hr-ft 2.0 F1BTrL)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 Vise (lbm/ft-hr)

Shell Skin Temp (OF)Skin Vise (Ibm/ft-hr)

Tube Temp In (OF)Density (Ibm/ft 3) Tube Temp Out (IF)Cp (BTU/Ibm.°F)

Tav Tube (*F)K (BTU/hr.ft.

0 F) Tube Skin Temp (OF)Extrapolation Calculation Results Shell Mass Flow (Ibm/br)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft')Propertv Velocity (ft/s)Reynold's Number Prandtl Number Bulk Vise (Ibm/ft.hr)

Skin Vise (Ibm/ft'hr)

Density (Ibm/ft 3)Cp (BTU/Ibm.°F)

K (BTU/hr.ft.TF)

Shell-Side 5.58 77,111 2.1317 0.8212 0.8772 60.5233 1.0025 0.3862 532,515.63 273,266.31 8,206,590.75 63.0 463.7 Tube-Side 3.70 27,306 3.6710 1.3588 1. 1663 61.7266 0.9988 0.3697 Overall Fouling (hr-ft 2-.F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr.ft 2-*F)I/Wall Resis (BTU/hr.ft 2.0 F)LMTD Correction Factor U Overall (BTU/hr-ft 2-°F)0.001960 1,889.2 1,235.3 15,431.0 0.9803 Shell Temp In (IF)Shell Temp Out (°F)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (°F)Tube Temp Out (IF)Tav Tube (OF)Tube Skin Temp (OF)286.6 190.0 174.6 182.3 172.7 104.0 134.1 119.0 136.0 97-197 Rev. A02** Reynolds Number Outside Range of Equation Applicability

!! With Zero Fouling The Test Heat Load Could Not Be Achieved Attachment A Page Al of A2 02-14-2011 04:25:25 PROTO-HX 4.00 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Data Report for DGO1B -LSCS -HPCS DG Hx.546.26 gpm Tube Flow, 104 F Tube Temp, FF = 0.00196,4 Tubes Plugged Shell and Tube Heat Exchanger Input Parameters II Shell-Side Tube-Side Fluid Quantity, Total gpm 1,064.46 795.25 Mass Fluid Ouantitv.

Total lbm/hr 0.00 0.00 Inlet Temperature OF 190.00 100.00 Outlet Temperature OF 175.00 121.00 Fouling Factor hr-ft 2.OFJBTU 0.00050 0.00193 Shell Fluid Name Tube Fluid Name Design Q (BTU/hr)Design U (BTU/hr-ft 2-°F)Outside h Factor (Hoff)Fixed U (BTU/hr.ft 2-*F)Fixed Area (ft 2)Performance Factor (% Reduction)

Heat Exchanger Type Total Effective Area per Unit (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 K (BTU/hr.ft-°F)

Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0 0.00 0.00 TEMA -E 468.17 0.973212339 0.00000 1 0.438000000 5.600 0.7500 Triangular 2 No 420 416 7.00 0.541 0.625 58.00 Lbc, Central Baffle Spacing (in)Lbi, Inlet Baffle Spacing (in)Lbo, Outlet Baffle Spacing (in)Dotl, Tube Circle Diameter Bh, Baffle Cut Height (in)Ds, Shell Inside Diamter (in)Lsb, Diametral difference between Baffle and Shell (in)Ltb, Diametral difference between Tube and Baffle (in)Nss, Number Sealing Strips 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 0.000 97-197 Rev. A02 Attachment A Page A2 of A2 CC-AA-309-1 001 Revision 3 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Design Analysis (Minor Revision)

ý Last Page No. 1 Attach. B Pg. 4/5 Analysis No.: 97-197 Revision:

2 A01 Title: I Thermal Model of COMED / LaSalle Station 1 B(2B) Diesel Generator Jacket Water Coolers ECIECR No.: EC 366846 Revision:

0 Station(s):'

LaSalle Unit No.: 8 1 and 2 Safety/QA Class: 9 SR System Code(s): ,o E22 Is this Design Analysis Safeguards Information? " Yes [] No [ If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?

"2 Yes El No Z If yes, ATI/AR#: This Design Analysis SUPERCEDES:

13 NA in its entirety.Description of Changes (list affected pages): ,4* Revised pg. 2/12 of Rev. A to add new Reference 8.12 to Table 3-1* Added Reference 8.12 to references list on page 12 of 12 of Rev. A* Replaced pgs. 3 and 4 of Attachment B in Rev. A, UFSAR Section 9.5.5.1.1 Rev. 0, with new pg. 3, UFSAR Section 9.5.5.1.1 from pending approved UFSAR Change LUCR-0082 for Rev. 17 of the UFSAR Added new Ref. 8.12 (pg. PTD-7 from Specification J-2544 Amd. 2) to Attachment B as page 4 Verified no UFSAR change to the 650 gpm minimum cooling water flow value shown on Attachment B pg. 2/5 of Rev. A (UFSAR Section 9.2.1.1.1

a. 3) has occurred over time.Disposition of Changes: Is This revision updates an included UFSAR section reference with the latest approved UFSAR information, and provides an additional reference for the basis of the heat load from the DG cooler. This revision also addresses A/R (Issue Report) No.628211 and associated assignment 02.Based on diesel generator nameplate data obtained by the System Manager, the Div. 3 diesel is from the same manufacturer, is the same model number, and has the same rated output as the Div. 1 and 2 DGs. Technical proposal heat balance data for the Div. 1 and 2 DGs, submitted by the supplier (see Ref. 8.12 in Attachment B, pg. PTD-7 from Purchase Specification J-2544 Amendment 2), shows that the energy absorbed by the cooling water at rated load and design ambient conditions is 2284 kW, which converts to 7.8E+06 Btu/hr, as stated in the UFSAR and used in previous revisions of the calculation.

Preparer:

'5 Dan Schmit .8/03/07 Print Name 9 SgNae Date Method of Review: ' Detailed Review [ Alternate Calculations El Testing El Reviewer:

'8 aaV- -T&~*cct Z'A Print Name Sign Name ate Review Independent review [ Peer review nl Notes: "9 (For External Analyses Only)External Approver:

o NA Print Name Sign Name Date Exelon Reviewer 2' NA Print Name Si am Date Exelon Approver:

22 Bill Hilton Print Name ,in Name Date PROTO-POWER CORPORATION CALCNO. 9 7.1 9 7 REv A 01 PAGE 2 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB No.31-003 CWENmT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station IB(213) Diesel Generator Jacket Water Coolers.I the necessary information for model construction while performance specifications provided by the vendor are used to benchmark the model.Thermal performance of the HPCS diesel generator heat exchanger is assessed in this calculation at the LaSalle Station Reference Conditions of Section 3.1 with all tubes active and 100% of rated load. No tube plugging margin or load conditions beyond 100% are considered.

3.1. LASALLE STATION REFERENCE CONDITIONS Table 3-1 describes the performance requirement of the jacket water cooler. These conditions ensure that the engine operating temperature range will not be exceeded.Table 3-1 LaSalle Station Reference Conditions 3.2.Parameter Value Reference Heat Load at 100% power (BTU/hr) 7,800,000 8.1, 8.4, 8. I, Shell-Side Flow Rate (gpm) 1,100 8.4 Shell-Side Inlet Temperature (0 F) 190 8.4 Tube-Side Flow Rate (gpm) 650 8.1 Maximum Tube-Side Inlet Temperature (0 F) 100 8.1 CONSTRUCTION DETAILS Table 3-2 Vendor Construction Detail Parameter Value Reference Heat Exchanger Type TEMA -E 8.7, 8.8 Number of Shells per unit I 8.7 Total Effective Area per unit (ft 2) 482 8.6, See Below Shell Velocity (ft/sec) 5.6 8.6 Baffle Thickness (in) 3/8 (min) 8.8 Fixed Tubesheet Thickness (in) 1 8.8 Floating Tubesheet Thickness (in) 1-1/4 8.8 Tube Passes per shell 2 8.7 U-Tubes (yes or no) No 8.7 Total Number of Tubes 420 8.6, 8.8 Tube Length (ft) 7 8,6 Tube Inside Diameter (in) 0.541 (19 BWG) 8,6 Tube Outside Diameter (in) 5/8 8.6 I Form NO.' P1050105 Rev.: 10 Date 10/21197 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO. 9 7_1 9 7 REV AoI PAGE 12 OF 12 GROTON, CONNECTICUT 010.IJIArMR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls ,uB NO.31-003 CLIENT COMED.' LaSalle County Station PROIEr COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station I B(2B) Diesel Generator Jacket Water Coolers.

8.0 REFERENCES

8.1. LaSalle Station UFSAR, Sections:

9.2.1 and 9.5.5.1.1 (Attachment B)8.2. NRC Generic Letter 89-13 8.3. GE Purchase Specification

-211872RO-SW9 Item 4.3.6.1 8.4. LaSalle Station FSAR Q40.92 (Attachment B)8.5. Stewart & Stevens Vendor Manual, VM J-152 through VM J-157 8.6. 0 & M Manufacturing Hx Data Sheet (Attachment A)8.7. LaSalle Station Drawing, VPF -3411-080(1)-I, J-2500 (Attachment A)8.8. LaSalle Station Drawing, VPF -3411-080(2)-I, J-2500 (Attachment A)8.9. Standard of the Tubular Exchanger Manufacturers Association 8.10. Heat Exchanger Thermal Performance Modeling Software Program PROTO-HXTM Version 3.02 Software Validation and Verification Report (SVVR) SQA No. SVVR-93948-02, Revision F, dated 2/17/98 8.11. Proto-Power Calculation 93-048, "Fluid Properties

-Fresh Water -Range 32°F to 500 0 F", Rev. A 8.12 Proposal Technical Data for Diesel Engine-Generator Sets from Specification J-2544 Amd. 2, pg. PTD-7 I Form No. P1050105 Re,.. 10 Date: 10/21;97 Ref :P&1 5-1 (f*,1c.4 -771r LSCS-UFSAR 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 9.5.5.1.1 Safety Design Bases Cooling capacity of this system is based on a diesel enerator output of 2860 kW with an environmental temperature of 1220 F m mum and a minimum and maximum lake water temperature of 320 F and 102 F, respectively.

Total heat transfer by this system is approximately 7.8 x 100 Btu/hr per diesel-generator set at rated engine capacity.

The Division I and II diesel cooling water heat exchangers are sized based on operation of 110% of rated load. The Division III diesel cooling water heat exchangers are sized based on operation of 100% of rated load.High water temperature is alarmed at 200° F and the engine is automatically shut down if the cooling water temperature at the engine outlet exceeds 208° 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 Design 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 9.5-34 REV. 15, APRIL e-"7 Proposal Technical Data for Dienel Engine-Generator Sets, Cont.La Salle County Station -Units I and 2 J-2544 Amd. 2, 01-27-78 Name of Bidder: Steward & Stevenson Services.

Inc.Y I ENGINE-GENERATOR DATA, Cont.k. WK,2 value of all rotating parts .............. (lb-ft 2)1. Is base frame stress re-lieved after fabrication but before machining

.......m. Vibration Dampers: (1) Type ...................

(2) Number .................

n. Full load speed ..... (r/min)o. Diesel Heat Balance at rated load and design ambient temperature:

(1) Diesel shaft output(kW)

(2) Energy absorbed by cool ing water .......... (kW)(3) Energy dissipated in exhaust gases ...... (kW)(4) Energy lost to ambient by radiation and con-vection ............ (kW)(Insert all data in these columns)BASE BID I ALTERNATE I" DIESEL GEN. DIESEL GEN.DIESEL (EN.OL]A AND 2A 1 02 IA AND 2A 34,690 no or recommen None N/A requir, 900* 2,600 2,284 X 3. 4/4.>12 3 led Amd.Amd./,.1 p.Environmental Data: (1) Maximum ambient tempera ture for continuous operation

.......... (OF)2,689 260 1040 30*98 derate 4%(2) Minimum ambient tempera ture for continuous operation

.......... (OF)(3) Generator losses to ambient at rated load and design ambient.(kW) kW at 90°F Ambient (This wotild 2 2*Note: 2,600.n 40*C -1044)PTD-7 LASALLE CALCULATION EDITORIAL

-COMMENT TO CALCULATION Calculation No.: Rev: NOPage No.The use of this form shall be limited to document corrections of'editorial nature. Return to Sylvia Venecia Prepared by-_Reiw dby: _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _Print Sign D~ate A p p r o v e d b y : _ _ _ _ _ _ _ __ _ __ _ _ _ _Print Sign Date Des tion of Correction:

I jen these comments are incorporated, return this form with the revised calculation.

I Incorporated on Calc Rev. By: I Date:

CC-AA-309

-ATTACHMENT 1 -Design Analysis Approval Page 1 of 2 DESIGN ANALYSIS NO.: Caic. # 97-197 PAGE NO. 1 Major REV Number: A Minor Rev Number: 00[]BRAIDWOOD STATION BYRON STATION DESCRIPTION CODE:(c0i8)

MY10 CLINTON STATION DRESDEN STATION[XI LASALLE CO. STATION DISCIPLINE CODE: (Coi0) M[ I QUAD CITIES STATION Unit:[ ]0 [X]l [X]2 [ J3 SYSTEM CODE: (C011) E22 TITLE: THERMAL MODEL OF COMED/LASALLE STATION UNIT I AND 2 HPCS DIESEL GENERATOR COOLERS[X] Safety Related [ ] Augmented Quality [ ] Non-Safety Related ATTRIBUTES (C016)TYPE VALUE TYPE VALUE Elevation 710' 0" Software PROTO-HX COMPONENT EPN: (C014 Panel) DOCUMENT NUMBERS: (C012 Panel) (Design Analyses References)

EPN TYPE peISub Document Number Input (Y/N)1E22-S001 H15 DCP EC# 334017 Y 2E22-S001 H15 /REMARKS: NA E-Form CC-AA-309-1 v1.1 for use with CC-AA-309 Revision 1 and above.

CC-AA-309

-ATTACHMENT 1 -Design Analysis Approval Page 2 of 2 DESIGN ANALYSIS NO.97-197 REV: AOO PAGE NO. 2 Revision Summary (including EC's incorporated):

Updated Proto-HX model for 104OF Service Water inlet temperature and calculated Unit 1 and 2 HPCS DG Cooler thermal margins for different fouling factors and 1% tubes plugged.Electronic Calculation Data Files: ProtoHX 3.02, dg0lb.phx, 192 KB, 04/14/2002.

5:04pm (Program Name, Version, File Name extension/size/datelhour/min)

Design impact review completed?(If yes. attach impact review sheet)[ I Yes [ X ) NIA, Per EC#- 334017 Prepared by: Jeff W. VanStrien Reviewed by: Brian L. Davenport I 'ý1AJ w/ T" 'J-,g'I -f , ý ) I.' n Date J Print[X I Detailed ) Aitemate-]T igns IITest Date Method of Review: Approved by: 25 ' "" ' P -/Print Sign External Design Analysis Review (Attachment 3 Attached)Reviewed by: / I Plnt Sim Approved by: I I Print Sign Date Do any ASSUMPTIONS

/ ENGINEERING JUDGEMENTS require later verification?

[ I 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 Cor d Effective Date: 04/14/00 CALCULATION TABLE OF CONTENTS CALCULATION NO.97-197 REV. NO. AOO 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 DGO1 B Al to A3 (CSCS=104 F @ Design Fouling)Attachment "B" -Proto-Hx Calc. Report for DG01 B B1 to B3 (CSCS=104 F @ 2X Max. Tested FF)Attachment "C" -Proto-Hx Cabc. Report for DG01 B C1 to C3 (CSCS=104 F @ 2X Max. Tested FF, w\ 1% plugged)I I I E-FORM I ComEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO.97-197 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 this heat exchanger for a 104 0 F Service Water inlet temperature.

This assessment will evaluate the adequacy of HPCS Diesel Generator Coolers during a maximum allowable inlet service water temperature of 104 0 F to ensure adequate thermal margin still exist. Also an acceptable design fouling factor for use as a benchmark during Generic Letter 89-13 testing evaluations 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 104 0 F and simulated for the following conditions: (Case 1) design fouling factor, (Case 2) twice the 'as-tested' fouling factor and (Case 3) twice the 'as-tested' fouling factor with 1 %of the tubes plugged. The acceptance criteria will be for the thermal margin during Case 3 conditions to exceed the LaSalle design heat load of 7,800,000 BTU/hr at 100% rated power output (Ref. 1, Table 3-1). Additional conservatism is built into this acceptance criteria by assuming a 5% uncertainty in the Proto-HX heat transfer calculations.

The Reference 1 model developed for this heat exchanger demonstrated a correlation to vendor performance specification well within this assumed 5% margin.3.0 ASSUMPTIONS I ENGINEERING JUDGMENTS The assumptions indicated in section 5.0 of Reference 1 are still valid.Note: The density of water at 104 0 F is 61.94 lb/ft (per steam tables), this is an insignificant change to the density shown in table 4-1 of Ref. 1 for 100°F, the tube side volumetric flow rate correction made in Ref. 1 is still valid.4.0 DESIGN INPUTS The design inputs consist of References 1 and 2 listed below.

5.0 REFERENCES

1. Calculation No.97-197, Rev. A, "Thermal Model of COMED / LaSalle Station HPCS Diesel Generator Jacket Water Coolers".2. Calculations L-002399, Rev. 0 (Unit 2) & L-002684, Rev. 0 (Unit 1), "1 & 2E22-S001 HPCS Diesel Generator Cooler Thermal Heat Transfer Performance" 3. "Standards of the Tubular Exchanger Manufacturers Association" (TEMA), Seventh Edition, 1988.I[ E-FORM I Comn£d NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO.97-197 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°F. At this temperature and with a fouling factor of 0.002732 hr*ft2*F/BTU, the amount of heat transferred is 7,801,000 BTU/hr compared with a LaSalle Station design heat load of 7,800,000 BTU/hr at 100%rated power output resulting in a 0.01% thermal margin (Ref. 1, Table 6-3). The cooler appears to have little thermal margin.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: ThermalM arg in x 100% = %ThermalM arg in Re quiredHeatLoad

[Equation 2]Case 1 When the service water inlet temperature is increased to 104 0 F for the same fouling factor (0.002732 hr*ft 2*°F/BTU), the heat transfer reduces to 7,474,000 BTU/hr, which is 4.2% below the required load of 7,800,000 BTU/hr for 100% power operating conditions

[Attachment A].Case 2 Regular cleaning and testing of these heat exchangers limits the amount of fouling well below the values assumed above. The heat exchanger performance data taken under the G.L. 89-13 program here at LaSalle demonstrates a maximum measured fouling factor of 0.001117 hr*ft 2*°F/BTU (Ref. 2). For conservatism, this value was doubled to 0.00223 hr*ft 2*°F/BTU and simulated with 104 0 F service water inlet temperature.

The result was a heat transfer of 8,237,000 BTU/hr for a 5.6% thermal margin at 100% power operating conditions

[Attachment B].IE-FORM I Comn NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO.97-197 REV. NO. AOO PAGE NO. 6 of 6 Case 3 When additional conservatism was included by adding a plugging allowance of 4 tubes, 1% of the total, in the heat exchanger and running the model again at the above fouling factor (0.00223 hr~ft 2*°F/BTU) and inlet temperature (104 0 F) for a 8,189,000 BTU/hr heat transfer rate, representing a 5% thermal margin at 100% power operating conditions

[Attachment C].This is judged to be a reasonably conservative fouling factor since it is slightly higher than the typical fouling factors stated in Ref. 3, page 215. The LaSalle lake water quality will meet or exceed the "River Water Fouling Factor" (at a velocity greater than 3 ft/sec) given in this reference.

The lake water passes through strainers and is chemically treated for silt control and scale prevention.

7.0

SUMMARY

AND CONCLUSIONS The Diesel Generator Water Cooler Model was found to have adequate thermal margin for a maximum lake temperature of 104 0 F when operated at 100% rated power output with a fouling factor of less than or equal to 0.00223 hr*ft 2*°F/BTU and a plugging allowance of 1% (4 tubes).This fouling factor has been determined to be an acceptable benchmark value that can be used in Generic Letter 89-13 testing evaluations of this model heat exchanger.

8.0 ATTACHMENTS

Attachment "A" -Proto-Hx Calc. Report for DG01 B (CSCS=104 F @ Design Fouling)Attachment "B" -Proto-Hx Calc. Report for DG01 B (CSCS=104 F @ 2X Max. Tested FF)Attachment "C" -Proto-Hx Calc. Report for DGO1 B (CSCS=104 F @ 2X Max. Tested FF, w\ 1% plugged)Final Page (Last Page)I E-FORM I ComEd CALCULATION NO.97-197 REVISION NO. AOO PAGE NO. Al of A3 Attachment "A" Proto-Hx Calc. Report for DGO1 B (CSCS=104 F @ Design Fouling)If E-FORM I 09:48:47 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.CSCS = 104 F @ Design Fouling 04/12/02 Shell and Tube Heat Exchanger Input Parameters

ý I Fluid Quantity, Total 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 2.°F)Emprical Factor for Outside h Performance Factor (% Reduction)

Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Shell-Side 1,064.46 190.00 175.00 0.00050 Tube-Side 795.25 100.00 121.00 0.00193 Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0.00 TEMA-E 468.17 0.973212339 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-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 1 0.438000000 5.600 0.7500 Triangular 2 No 420 420 7.00 0.541 0.625 58.00 0.000 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 Calculation No.97-197 Revision No. AO0 Attachment A Page No. A; of /-3 09:48:47 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.CSCS = 104 F (elb Desien Fouling 04/12/02 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) 646.1 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In (IF) Tube Inlet Temp (IF) 104.0 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.ft2.OF)

Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2.0 F)Tube-Side hi (BTU/hr.ft 2.OF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr.ft 2.OF)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-ft 2..F/BTU)Property Shell-Side Tube-Side Velocity (htis) Shell Temp In (IF) Calculation No.97-197 Reynold's Number Shell Temp Out (IF) Revision No. AOO Prandtl Number Tav Shell ('F) Attachment Bulk Vise (Ibm/ft hr) Shell Skin Temp (IF) Page No. A3 of___Skin Vise (lbrn/ftrhr)

Tube Temp In (°F)Density (Ibm/ft 3) Tube Temp Out (IF)Cp (BTU/lbm.°F)

Tav Tube (IF)K (BTU/hr-ft-°F)

Tube Skin Temp (°F)Extrapolation Calculation Results Shell Mass Flow (lbmnhr)Tube Mass Flow (lbm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)5.325E+5 3.232E+5 7.474E+6 67.3 468.2 Property Shell-Side Velocity (ft/s) 5.58 Reynold's Number 7.746E+04 Prandtl Number 2.12 Bulk Visc (lbm/ft-hr) 0.82 Skin Vise (lbm/ft'hr) 0.87 Density (Ibm/ftO) 60.51 Cp (BTUIbni 0.F) 1.00 K (BTUJ/hr-ft.TF) 0.39 Tube-Side 4.34 3.095E+04 3.81 1.41 1.24 61.78 1.00 0.37 Overall Fouling (hrft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2-OF)I/Wall Resis (BTU/hr.ft2;OF)

LMTD Correction Factor U Overall (BTU/hrft 2-°OF)Shell Temp In (OF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (OF)Tube Temp Out (OF)Tav Tube (°F)Tube Skin Temp (OF)0.002732 1,894.1 1,372.6 15,431.0 0.9880 240.0 190.0 176.0 183.0 174.5 104.0 127.2 115.6 129, 2** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achile' CornEd CALCULATION NO.97-197 REVISION NO. AOO PAGE NO. B1 of B3 Attachment "B" Proto-Hx Calc. Report for DG01 B (CSCS=104 F @ 2X Max. Tested FF)IE E-FORM I 09:50:40 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.CSCS = 104 F @ 2X NDIT FF 04/12/02 Shell and Tube Heat Exchanger Input Parameters I Fluid Quantity, Total 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 2-0 F)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 1,064.46 190.00 175.00 0.00050 Tube-Side 795.25 100.00 121.00 0.00193 Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0.00 TEMA-E 468.17 0.973212339 1 0.438000000 5.600 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.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 420 420 7.00 0.541 0.625 58.00 0.000 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 Calculation No.97-197 Revision No. AOO Attachment b Page No. 0,2. of 8&1:0-j't I'Llc+or i-Apwr 09:50:40 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.CSCS = 104 F @ 2X NDIT FF 04/12/02-Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions q Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 646.1 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In (°F) Tube Inlet Temp (IF) 104.0 Shell Temp Out (°F) Shell Inlet Temp (°F) 190.0 Tube Flow (gpm)Tube Temp In (IF)Tube Temp Out (IF) i Input Fouling Factor 0.002230 1L _ 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.°F)Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-fi 2-IF)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) Calculation No.97-197 Reynold's Number Shell Temp Out (OF) Revision No. AOO Prandti Number Tav Shell (°F) Attachment B_Bulk Visc (Ibm/ft.hr)

Shell Skin Temp (IF) Page No. __1 of Skin Visc (Ibm/ft-hr)

Tube Temp In ('F)Density (lbm/fl 3) Tube Temp Out (OF)Cp (BTU/Ibm'°F)

Tav Tube (IF)K (BTU/hr'ft'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')5.325E+5 3.232E+5 8.237E+6 65.4 468.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft'hr)

Skin Vise (Ibm/ft-hr)

Density (Ibm/ft 3)Cp (BTU/Ibrn'F)

K (BTU/hr" ft-'F)Shell-Side Tube-Side 5.58 4.34 7.709E+04

3. 130E+04 2.13 3.76 0.82 1.39 0.88 1.21 60.52 61.76 1.00 1.00 0.39 0.37 Overall Fouling (hr-ft 2-°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 0.F)LMTD Correction Factor U Overall (BTU/hr-ft 2.°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (°F)Shell Skin Temp (OF)Tube Temp In ('IF)Tube Temp Out (OF)Tav Tube (°F)Tube Skin Temp (TF)0.002230 1,889.3 1,383.0 15,431.0 0.9845 273.3 190.0 174.6 182.3 172.8 104.0 129.5 116.8 131.7** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achicer CorEd CALCULATION NO.97-197 REVISION NO. AOO PAGE NO. C1 of C3 Attachment "C" Proto-Hx Calc. Report for DGO1B (CSCS=104 F @ 2X Max. Tested FF, w\ 1% plugged)I E-FORM I 09:57:54 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.CSCS= 104 F64 2X NDIT FF, I% plug 04/12/02 3. .3 01, 11 Shell and Tube Heat Exchanger Input Parameters II Fluid Quantity, Total 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 2 f-F)Emprical Factor for Outside h Performance Factor (% Reduction)

Heat Exchanger Type Effective Area (ftA2)Area Factor Area Ratio Shell-Side 1,064.46 190.00 175.00 0.00050 Tube-Side 795.25 100.00 121.00 0.00193 Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0.00 TEMA-E 468.17 0.973212339 Number of Shells per Unit Shell Minimum Area Shell Velocity (fi/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'ftl'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 1 0.438000000 5.600 0.7500 Triangular 2 No 420 416 7.00 0.541 0.625 58.00 0.000 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 Calculation No.97-197 Revision No. AOO Attachment C.Page No. C2. of -Cý- :D." I i. ) , A P.'f 0" Jýwr pps'l .

09:57:54 PROTO-HX 3.02 by Proto-Power Corporation (SN#663-7371)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.CSCS= 104 Fa, 2X NDIT FF, I% plug 04/12/02 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions 4 Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 646.1 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 Shell Temp In (IF) Tube Inlet Temp (IF) 104.0 Shell Temp Out (IF) Shell Inlet Temp (OF) 190.0 Tube Flow (gpm)Tube Temp In (°F)Tube Temp Out (IF)

Input Fouling Factor 0.002230 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft2-IF)

Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2-OF)Tube-Side hi (BTU/hr-ft 2-OF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-ft 2-OF)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-fit 2-F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (IF) Calculation No.97-197 Reynold's Number Shell Temp Out (IF) Revision No. A00 Prandtl Number Tav Shell (IF) Attachment C Bulk Visc (Ibm/ff-hr)

Shell Skin Temp (OF) Page No. C 3 of C Skin Visc (lbm/ft-hr)

Tube Temp In (OF)Density (Ibm/ft')

Tube Temp Out (IF)Cp (BTU/lbm 0'F) Tav Tube (IF)K (BTU/hr't 0'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/ft 3)Cp (BTU/Ibm 0'F)K (BTU/hr"ft-'F)

Shell-Side 5.58 7.712E+04 2.13 0.82 0.88 60.52 1.00 0.39 5.325E+5 3.232E+5 8. 189E+6 65.5 463.7 Tube-Side 4.38 3.158E+04 3.76 1.39 1.21 61.76 1.00 0.37 Overall Fouling (hr- f°2 F/BTU)Shell-Side ho (BTU/hr-ftz-°F)

Tube-Side hi (BTU/hr ft 2-°F)I/Wall Resis (BTU/hr-ft 2 0.F)LMTD Correction Factor U Overall (BTU/hr.ft 2 F)Shell Temp In (°F)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (°F)Tube Temp In (fF)Tube Temp Out (°F)Tav Tube (°F)Tube Skin Temp (°F)0.002230 1,889.4 1,393.0 15.431.0 0.9848 273.7 190.0 174.7 182.3 172.8 104.0 129.4 116.7 131.6** Reynolds Number Outside Range of Equation Applicability With Mlininium Fouling 'Fhe Test Heat Load Could Not Be ,%chie\

PROTO-POWER CORPORATION CALCULATION TITLE SHEET CLIENT: PROJECT: Commonwealth Edison / LaSalle County Station COMED / LaSalle Station GL 89-13 Program CALCULATION TITLE: CALCULATION NO.: FILE NO.: Thermal Model of COMED / LaSalle Station HPCS Diesel Generator Jacket Water Coolers.97-197 31-003 COMPUTER CODE & VERSION (if applicable):

PROTO-HX T M ver 3.02 REV TOTAL NO. OF ORIGINATOR/DATE VERIFIER/DATE APPROVAL/DATE PAGES A 58 Philpot Page I of V Form No.: P1050101 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC rO.97-197 REV A PAGE II OF V GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB NO.31-003 CUENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station HPCS Diesel Generator Jacket Water Coolers.Revision History Form No.: P1050102 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-PIOWER COIRPORAI'1ON C.ALC NO.97-197 FRI' A PAGE III OF v GROTON, CONNECTICUT ORIGINAlOR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB NO- 31-003 CLIENT COMED / LaSalle County Station PROJECt COMED / LaSalle Station GL S9-13 Program TITLE Thermal Model of COMED / LaSalle Station HPCS Diesel Generator Jacket Water Coolers.CALCULATION VERIFICATION FORM REVIEW METHOD: Approach Checked: Logic Checked: Arithmetic Checked: Alternate Method (Attach Brief Summary)Computer Program Used (Attach Listing)Other*Errors Detected LI N/A N/A N/A N/A N/A N/A E3 LI 91 EXTENT OF VERIFICATION:

Complete Calculation:

21 Revised areas only: El Other (describe below): []*Error Resolution 26mbw OcvigtJ ar X.s-,ýAe " AA ' /Va LIA4e4 Ae- Dk 4LI4 iPn4rh4x AU4Jv £F6eCir i'eAW ý4 t w4L ff*Other Comments/*Extra References Used*(Attach extra sheets if needed)CALCULATION FOUND TO BE VALID AND CONCL TO BE CORRECT AND REASONABLE:

IDV Signature:

.A Initials:.5co# A, ýqjlv Printed Name: Date:ý4 (114 ý/fs d Form No.: P1050103 Rev.: 10 Date: 10/21197 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC ,NO'9 7-1 9 7 REV A PAGE IV OF v GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB NO 31-003 CLIENT COMED / LaSalle County Station PROJECTr COMED / LaSalle Station GL 89-13 Program TIT.E Thermal Model of COMED / LaSalle Station HPCS Diesel Generator Jacket Water Coolers.TABLE OF CONTENTS CALC TITLE SHEET ............................................................................................

I REVISION HISTORY ...........................................................................................

II CALC VERIFICATION SHEET .........................................................................

III TABLE OF CONTENTS ..................................................................................

IV LIST OF ATTACHMENTS

...............................................................................

V Total number ofpages in Preface of Calc 5 1.0 PU R PO SE ............................................................................................................

I 2.0 BACKGROUND

.............................................................................................

1 3.0 DESIGN INPUTS ..........................................................................................

1 3.1. LASALLE STATION REFERENCE CONDITIONS...........................................

2 3.2. CONSTRUCTION D ETAILS ..............................................................................

2 3.3. PERFORM ANCE D ETAILS ...........................................................................

3 4.0 APPROACH ....................................................................................................

4 4.1. PROTO-HXTM PARAMETER CALCULATION

.............................................

4 4.2. PROTO-HX T M FLOW RATE INPUTS ..........................................................

5 4.3. PROTO-HXTM EXTRAPOLATION METHOD ..............................................

5 5.0 ASSUMPTIONS

..................................................................................................

5 6.0 ANALYSIS ......................................................................................................

6 6.1. PROTO -H X 'r M ODEL ...........................................................................

6 6.2. HEAT EXCHANGER FOULING FACTOR LIMIT .............................................

6 6.3. FOULING SENSITIVITY

..............................................................................

8 6.4. THERMAL MARGIN ASSESSMENT

.............................................................

9 6.5. MINIMUM SERVICE WATER FLOW RATE ...................................................

9

7.0 CONCLUSION

.............................................................................................

11 7.1. PR OTO -H X TM M ODEL .........................................................................

11 7.2. HEAT EXCHANGER FOULING FACTOR LIMIT ...........................................

11 7.3. FO U LIN G S EN SITIV ITY .................................................................................

11 7.4. THERMAL MARGIN ASSESSMENT

.............................................................

11 7.5. MINIMUM SERVICE WATER FLOW RATE .....................................................

1 1

8.0 REFERENCES

..............................................................................................

12 Total number of pages in Body of Calc 12 Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO.97-197 RV A PAGE v OF v GROTON, CONNECTICUT ORIGINATOR.

D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB NO.31-003 CLIENT COMED / LaSalle County Station PROJECt COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station HPCS Diesel Generator Jacket Water Coolers.LIST OF ATTACHMENTS Attachment Subject Matter Total Pages A Proto-Power Calc.97-197, Rev. A; 4 Vendor Data Sheet & Drawings Proto-Power Calc.97-197, Rev. A;B LaSalle Station UFSAR Section: 9.5.5.1.1, 5 and FSAR Q40.92 Proto-Power Calc.97-197, Rev. A;C PROTO-HXTN HPCS Model Development 13 Calculation Reports Proto-Power Calc.97-197, Rev. A;D PROTO-HXTm Calculation Reports for 7 Fouling Sensitivity Proto-Power Cale.97-197, Rev. A;E PROTO-HXTm Calculation Reports for 10 Minimum Service Water Flow F Proto-Power Cale.97-197, Rev. A; 2 (and disk)PROTO--X T M Version 3.02 Model Number of Attachment Pages: Complete Calc (total number ofpages)41 58 Form No.: P1050104 Rev.: 10 Date: 10/21/97 Ref.: & 5-PROTO-POWER CORPORATION CALC NO.97-197 REV A PAGE 1 O'12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB NO.31-003 CLUENT COMED / LaSalle County Station PROJECt COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station IB(2B) Diesel Generator Jacket Water Coolers.1.0 PURPOSE The purpose of this calculation is to develop a thermal performance analysis model for the Commonwealth Edison (ComEd) LaSalle Station, High Pressure Core Spray (HPCS) Diesel Generator heat exchanger.

This model is to be used for the analysis of heat exchanger thermal performance test data as part of the LaSalle Station heat exchanger testing program.Once developed, the model is used to evaluate the thermal margin of the heat exchanger at the LaSalle Station Reference Conditions as currently defined in the LaSalle design and licensing basis.The thermal performance model documented in this calculation has been created and used with PROTO-HX, Version 3.02. The model can be used with previous versions of PROTO-HX and produce identical results as long as the following restrictions are upheld: " Versions prior to version 3.02 will not calculate a negative fouling factor when calculating the fouling factor based on test data." Shell and tube heat exchangers analyzed in Version 3.0 or earlier must have a tube-side Reynolds Number greater than 10,000 (i.e., fully developed turbulent flow).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:* Water (fresh and salt): 32-500'F 2.0 BACKGROUND LaSalle Station is in the process of implementing a heat exchanger thermal performance monitoring program in response to the requirements of NRC Generic Letter 89-13 (Reference 8.2). Development of an analytical model in PROTO-HXTm, Version 3.02, will allow timely analysis of data resulting from the test program.3.0 DESIGN INPUTS The PROTO-HXTm program 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, 10CFR21, 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-HXTM Version 3.02 was verified and approved for use as documented in Reference 8.10.The design inputs for this calculation consist of the LaSalle Station Reference Condition (Section 3.1), Construction Details (Section 3.2), and Performance Details (Section 3.3) provided by the heat..exchanger vendor, data sheets or design documents as referenced:

Construction details give Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO. 9 7-1 9 7 REV A PAGE 2 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB NO.31-003 CUENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station 1B(2B) Diesel Generator Jacket Water Coolers.the necessary information for model construction while performance specifications provided by the vendor are used to benchmark the model.Thermal performance of the HPCS diesel generator heat exchanger is assessed in this calculation at the LaSalle Station Reference Conditions of Section 3.1 with all tubes active and 100% of rated load. No tube plugging margin or load conditions beyond 100% are considered.

3.1. LASALLE STATION REFERENCE CONDITIONS Table 3-1 describes the performance requirement of the jacket water cooler. These conditions ensure that the engine operating temperature range will not be exceeded.Table 3-1 LaSalle Station Reference Conditions 3.2.Parameter Value Reference Heat Load at, 100% power (BTU/hr) 7,800,000 8.1, 8.4 Shell-Side Flow Rate (gpm) 1,100 8.4 Shell-Side Inlet Temperature (0 F) 190 8.4 Tube-Side Flow Rate (gpm) 650 8.1 Maximum Tube-Side Inlet Temperature

(*F) 100 8.1 CONSTRUCTION DETAILS Table 3-2 Vendor Construction Detail Parameter Value Reference Heat Exchanger Type TEMA -E 8.7, 8.8 Number of Shells per unit I 8.7 Total Effective Area per unit (fti) 482 8.6, See Below Shell Velocity (ftlsec) 5.6 8.6 Baffle Thickness (in) 3/8 (min) 8.8 Fixed Tubesheet Thickness (in) I 8.8 Floating Tubesheet Thickness (in) 1-1/4 8.8 Tube Passes per shell 2 8.7 U-Tubes (yes or no) No 8.7 Total Number of Tubes 420 8.6, 8.8 Tube Length (ft) 7 8.6 Tube Inside Diameter (in) 0.541 (19 BWG) 8.6 Tube Outside Diameter (in) 5/8 8.6 Form No.: P105010 Rev.: 10 Date: 10/21197 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO.97-197 REV A PAGE 3 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB NO.31-003 CLIENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station IB(2B) Diesel Generator Jacket Water Coolers.Table 3-2 Vendor Construction Detail Parameter Value Reference Tube Wall Conductivity (BTU/hr-ft-°F) 58 (Admiralty Naval Brass) 8.6, 8.9 Tube Pitch (in) 3/4 8.6 Pitch Type Triangle 8.8 The vendor data sheet shows the effective area as 482 ft 2 , however, based on tube diameter and tube length, this value is a gross area (Ag,) approximation:

A g, = (number of tubes)- (L,,, -(tube outside circ.)Ag, = 420 -71ft. R7 .61nJ481.056ft2 S12 %/ft The effective area (Aeff) can be approximated as follows: A" 0 f = (number of tubes). (L tut -Tfixed -Tnoa.ng )- (tube outside circ.)Aeff = 420.7 (in+25in)t 0.625 in) 468.171f 2 12%- ) 12% = 8 the outside Equation 1 Equation 2 where: AU -Heat Exchanger Gross Area, ft 2 A¢ff -Heat Exchanger Effective Area, ft 2 L tube -Tube Length, ft Tfixed -Fixed End Tubesheet Thickness, ft (1" per Reference 8.8)T oaing -Floating End Tubesheet Thickness, ft (1.25" per Reference 8.8)The data sheet value for the effective area will be used in the model benchmarking process. However, for PROTO-HXTM runs of the HPCS heat exchanger model the above calculated effective area will be used.3.3. PERFORMANCE DETAILS Table 3-3 Vendor Performance Detail Parameter Value Reference Shell Side Fluid Type Water (Fresh) 8.6 Shell Side Fouling Factor (Design) 0.0005 8.6 Shell Side Fluid Flow Rate (gpm) 1100 8.6 Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: & 5-PROTO-POWER CORPORATION CALC NO.97-197 REV A PAGE 4 OF 1 2 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB NO.31-003 CLIENr COMED / LaSalle County Station PROJECr COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station IB(2B) Diesel Generator Jacket Water Coolers.Table 3-3 Vendor Performance Detail Parameter Value Reference Shell Side Inlet Temperature (0 F) 190 8.6 Shell Side Outlet Temperature (0 F) 175 8.6 Tube Side Fluid Type Raw Water (Fresh) 8.6 Tube Side Fouling Factor (Design) 0.002 8.6 Tube Side Fluid Flow Rate (gpm) 800 8.6 Tube Side Inlet Temperature (0 F) 100 8.6 Tube Side Outlet Temperature

(°F) 121 8.6 Hx. Design Q -Service (BTU/hr) 8,505,000 8.6 Hx. Design U -Service (BTU/hr-ft 2-°F) 241.7 8.6 Corrected LMTD 73 8.6 I-4.0 APPROACH This calculation utilizes plant/vendor fabrication specifications provided in Attachment A to develop a thermal performance prediction model for the LaSalle Station HPCS Diesel Generator Jacket Water Coolers. The calculation then benchmarks the model by comparing the heat transfer rate calculated by PROTO-HXTM Version 3.02 with the vendor's specifications for thermal performance.

4.1. PROTO-HXTm PARAMETER CALCULATION Minimum Shell Area The minimum shell area is calculated using either the shell side velocity or a shell geometry.

The preferred method of calculation is using the shell side velocity.Reference 8.6 gives the shell side velocity to be 5.6 ft/sec at a flow of 1100 gpm. Based on this velocity and flow rate the minimum shell side area is calculated by PROTO-HXTM to be 0.438 ft'.Outside H Factor (Hoff)The Outside H Factor is a multiplier, with value less then 1.0, used to reduce the ideal shell-side film heat transfer coefficient.

The Outside H Factor accounts for inefficiency in the heat exchanger.

Using the back calculation method based on the design overall heat transfer coefficient, the Outside H Factor was calculated by PROTO-HXTM to be 0.616913.

Values of the Outside H Factor in the range of 0.6 are considered to be representative of a "well designed" heat exchanger.

o Form No.: P151 Rev.: 10 Date: 10/21/97 Ref.: P&I 5 5-1 PROTO-POWER CORPORATION CALC NO.97-197 REV A rAGE 5 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERIF'IED BY S. Ingalls JOB NO.31-003 CLIENT COMED / LaSalle County Station IPROJ"'r COMED / LaSalle Station GL 89-13 Program rITLE Thermal Model of COMED / LaSalle Station 11B(2B) Diesel Generator Jacket Water Coolers.4.2. PROTO-HXTM FLOW RATE INPUTS When the volumetric flow rates are entered into PROTO-HXT.1 they are converted to rnass flow rates based on a set temperature of 60'F. Therefore, the actual PROTO-HXTM inputs have to be adjusted to give the correct mass flow rate. The PROTO-HXTM input is adjusted using the ratio of the actual water density and the density of water at 60'F.Q phx -Qtemp P temp P 6 o0F Equation 3 Table 4-1 PROTO-HX T M Flow Rate Inputs Parameter Density (Ib/ft 3) Actual Flow (gpm) PROTO-HXV h-Input (gpm)Tube-side, 100'F 61.994 (8.11) 800 795.25 61.994 (8.11) 650 646.14 Shell-side, 190'F 60.349 (8.11) 1,100 1,064.495 PROTO-HX T , 60.F 62.364 (8.11) i..-f-...:-, .- , 4.3. PROTO-HXTM EXTRAPOLATION METHOD All calculations performed for this calculation are based on a constant cold inlet temperature.

This allows the comparison of the heat transfer, outlet temperatures, log mean temperature difference (LMTD), and overall heat transfer coefficient.

There is no comparison of the overall heat transfer coefficient in the design case since PROTO-HXTM used the data sheet value of the overall heat transfer coefficient to calculate the outside film heat transfer coefficient.

5.0 ASSUMPTIONS

5.1. The vendor data sheet (Reference 8.6) is considered to be an accurate reflection of the vendor's expectation for the heat exchanger's outside film heat transfer coefficient.

Therefore, the benchmarking of the PROTO-HXTM model to the vendor data sheet will ensure that the PROTO-FHXTM calculated outside film heat transfer coefficient is consistent with the vendor's expectation.

The PROTO-HXTM model is benchmarked with the vendor data sheet effective area. However calculations performed with the model use the effective area determined in Section 3.2. Future validation of this assumption is not required.Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO. 9 7-1 9 7 REV A PAGE 6 0F 1 2 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERINFED BY S. Ingalls JOB NO.31-003 CLIENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL S9-13 Program TITLE Thermal Model of COMED I LaSalle Station I B(2B) Diesel Generator Jacket Water Coolers.6.0 ANALYSIS 6.1. PROTO-HXTM MODEL Table 6-1 shows the PROTO-HXT1t benchmarking of the Jacket Water Cooler for the HPCS Diesel Generator.

The PROTO-HXTm reports can be found in Attachment C.Table 6-1 Model Benchmark Correlation Parameter PROTO-liXTM Data Sheet Percent Difference Effective Area, ft 2 482 482 0.00%Shell Side Outlet Temp, 'F 174.5 175 -0.29 %Tube Side Outlet Temp, 'F 120.8 121 -0.1 7%Heat Transferred, BTU/hr 8,277,000 8,505,000

-2.68 %Corrected LMTD 71.0 73 -2.74%Table 6-2 shows the PROTO-HXTM results for the heat exchanger design conditions using the corrected effective area, Section 3.2. The PROTO-HXTM reports can be found in Attachment C.Table 6-2 Model Design Correlation Parameter PROTO-HXTm Data Sheet Percent Difference Effective Area, ft2 468.17 482 -2.87 %Shell Side Outlet Temp, *F 174.8 175 0.11%Tube Side Outlet Temp, 'F 120.4 121 -0.50 %Heat Transferred, BTU/hr 8,089,000 8,505,000

-4.89 %Corrected LMTD 71.5 73 -2.05%All PROTO-HX T M calculations performed with the HPCS Jacket Water Cooler model will use the effective area of 468.17 ft 2.This change is made to the PROTO-HX T M heat exchanger data sheet as shown in Attachment C.6.2. REAT EXCHANGER FOULING FACTOR LIMIT In order for the jacket water cooler to meet the Reference Conditions (Table 3-1) the fouling must be limited from the values listed on the vendor's data sheet (Reference 8.6).The overall fouling factor limit was determined by iterating on the overall fouling factor, a PROTO-HXTM input, until the required heat load was matched. Table 6-3 shows the results of the PROTO-HXT1l runs for the limited fouling factor case, see Attachment C.Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: & 5-PROTO-POWER CORPORATION CALCNO.97-197 REV A PAGE 7 OF 1 2 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 S. Ingalls JO0 NO.31-003 CLIENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station 1B(2B) Diesel Generator Jacket Water Coolers.Table 6-3 Fouling Factor Limit Parameter Design Fouling Limited Fouling Tube-side Fouling Factor 0.002 0.001932 Shell-side Fouling Factor 0.0005 0.0005 Total Fouling Factor 0.002811 0.002732 Overall Heat Transfer Coefficient 234.7 239.2 Heat Transfer Rate 7,718,000 7,801,000 Required Heat Transfer Rate 7,800,000 7,800,000 Thermal Margin -82,000 1,000% Thernmal Margin -1.05% 0.01 %The limitations on the fouling factor are placed on the tube-side fouling factor, since the tube-side is the most controllable via periodic tube-side cleaning.

The tube-side fouling factor is calculated from the overall fouling found from the PROTO-HXTM iteration process. The area ratio is used to convert the overall fouling factor to a tube-side and shell-side fouling factor fto.,i = fshe, + (Area Ratio). fube Area Ratio -TubeOD Tube ID Area Ratio = 0.625 in 1.15527 0.541 in From the vendor datasheet the design overall fouling factor is calculated f " 0 0 hr 2t FBtu=0.0005 and ftube = 0.002 hr 11 2 ýF 0.0005 + 1.15527 "0.002h, f2 °F 0.002811 hrft F/nu ltu 131u From the PROTO -HX iteration the adjusted overall fouling factor is found:= 0.002732 hr ft2 °I3'u Equation 4 Equation 5 Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 I'ROTO-POWER CORPORATION CALC NO.97-197 UV A PAGE 8 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VRIFIED BY S. Ingalls Jo0 NO 31-003 CLIENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station IB(2B) Diesel Generator Jacket Water Coolers.From the new overall fouling factor the new tube -side fouling factor is calculated:

S(fadjusted-fshel)(0.002732-0.0 0 0 5)hr 12 .Fji_ 2 tubc -Area Ratio 1.15527 Btu The PROTO-HXTM heat exchanger data sheet is changed to reflect the adjusted design fouling as calculated above. Like the effective area change in the heat exchanger data sheet, this change is made without recalculating the Hoff factor.Attachment C includes a final model calculation report for the Reference Conditions and the adjusted tube-side fouling entered into the PROTO-HXTM data sheet.6.3. FOULING SENSITIVITY The fouling sensitivity of the jacket water cooler is shown in Figure 6-1. The fouling sensitivity was developed at 650 gpm CSCS flow, 100'F CSCS inlet temperature, 1100 gpm jacket water flow, and 190'F jacket water inlet temperature.

The tube-side fouling factor was varied from 0.0000 to 0.001932 (hr ft 2 °F/Btu) by increments of 0.0005 (hr ft 2°F/Btu). The shell-side fouling factor is held constant at the design value of 0.0005 (hr ft 2 °F/Btu). The PROTO-HX T M Calculation Reports for the fouling sensitivity can be found in Attachment D Figure 6-1 Tube-side Fouling Sensitivity 14,000,000 12.000.000

' ____--HPCS DG -Jacket Water Co/ler 1 0 .0 0 0 ,0 0 0 --------S8.000.000

---___ _____Re eConditionHeat Rate I 6.000,000

- -_ _ _ ---_ , M 6,000,000.

-... '- .......- -- ...... .. ..... ... ".. ... ..... ...-.. .. -..._ _4,000,000 I i 2 .0 0 0.,0.0. ...... .-....... .... ........ .. ..... ........ .. ...0.000000 0.000195 0.000390 0.000585 0.000780 0.000975 0001170 0.001365 0.001560 0.001755 0.001950 Tube-side Fouling (hr ft2 *F/Btu)Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO 97-197 REV A PAGE 9 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERMIUED BY S. Ingalls JOB NO.31-003 CIENT COMED / LaSalle County Station "O"" COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station 113(2B) Diesel Generator Jacket Water Coolers.6.4. THERMAL MARGIN ASSESSMENT The clean thermal margin is assessed by a comparison of the reference condition performance requirement (Table 3-1) to the heat exchanger performance capability with a zero (0) fouling factor. Using a zero (0) fouling factor shows the maximum available performance of the heat exchanger.

Likewise the service thermal margin is assessed by comparing the reference condition performance requirement (Table 3-1) to the heat exchanger performance capability with the design fouling factor.The margin is calculated directly and as a percentage compared to the required heat rate to perform the component's safety function.

The PROTO-HXTM reports can be found in Attachment C.margin=Heat Rate -Heat Raterquicd

% margin = 100. margin (Heat Raterquid)

Equation 6 Equation 7 Table 6-4 Thermal Margin Parameter Service (Design Fouling) Clean (0 Fouling)Overall Heat Transfer Coefficient 239.2 713.2 Heat Transfer Rate 7,801,000 15,420,000 Required Heat Transfer Rate 7,800,000 7,800,000 Thermal Margin 1,000 7,620,000% Thermal Margin 0.01 % 97.69 %6.5. MINIMUM SERVICE WATER FLOW RATE The minimum service water flow rate for the adjusted design fouling condition is calculated with the shell-side inlet temperature at 190'F and a flow rate of 1,100 gpm.Iterating using the service water flow rate and inlet temperature, the minimum acceptable flow rate is found for each inlet temperature (Attachment E). The heat load for each iteration must be equal to or slightly above the required heat load of 7,800,000 BTU/hr, the diesel heat load at 100% power (reference 8.1).The results of the model iterations are summarized in Table 6-5 and Figure 6-2. Density corrections of the PROTO-HXTM flow rates are made in accordance with Equation 3.Values for fluid density are obtained from Reference 8.11.Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALCNO'97-197 REV A CAGE I0 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe .ATE 6/26/98 VERIFIED BY S. Ingalls JOB NO.31-003 CLIENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station IB(2B) Diesel Generator Jacket Water Coolers.Table 6-5 Minimum Required CSCS Flow Rate CSCS Inlet Density at Inlet PROTO-HXTht Density Corrected Temperature Temperature Input Flow Rate Flow Rate (O 0 F) (lbm/ft 3) (gpm) (gpm)35 62.41903 202.4 202.2 40 62.42184 209.1 208.9 50 62.40595 227.4 227.2 60 62.36445 255.0 255.0 70 62.30034 298.7 299.0 80 62.21603 362.9 363.8 90 62.11349 464.2 466.1 100 61.99437 646.1 650.0 Figure 6-2 Minimum CSCS Flow at Adjusted Design Fouling 700.000 _ -600.000 _ -- --500.000 .- *jI ._ _ _ _ _ _ _ _ _ _I I 0L 400.000 __ ___300.000 It I 35 40 45 50 55 60 65 70 75 80 85 90 95 100 CSCS Inlet Temperature

(*F)Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: &5-PROTO-POWER CORPORATION CALC NO. 97197 REV PAGE O OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB NO.31-003 CLIE.NT COMED / LaSalle County Station PROJEC- COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station I1B(2B) Diesel Generator Jacket Water Coolers.

7.0 CONCLUSION

7.1. PROTO-HX T If MODEL The HPCS Jacket Water Cooler model was developed using PROTO-HXTM, Version 3.02. The model was benchmarked to the vendor data sheet. The benchmark model correlation to the vendor data sheet heat rate is 2.68 %. The benchmark model is for reference only based on the non-conservative approximation of heat exchanger effective area as discussed in Section 3.2 and Assumption 5.1. Calculations performed with the HPCS Jacket Water Cooler model are to use the effective area developed in Section 3.2.This model should be considered suitable for use in the analysis of thermal performance test data.The model database is saved under file name dg0lb.phx, with a file size of 864 KB, and a file date and time of 6/26/98 at 11:25:36 AM. The saved database is set up to run the Reference Conditions with design fouling factor selected, the design fouling factor is a shell-side fouling of 0.002782.

The database file is included as Attachment F.7.2. HEAT EXCHANGER FOULING FACTOR LIMIT For the HPCS Diesel Generator Jacket Water Cooler to provide adequate heat removal at the specified LaSalle Station Reference Conditions the overall fouling factor must be equal to or less than 0.002732 hr ft 2 0 F/Btu. This overall fouling factor is broken down into a 0.001932 and 0.0005 hr ft 2 OF/Btu for the tube-side and shell-side fouling factors respectively and entered in the model as the design fouling factors.7.3. FOULING SENSITIVITY Given a constant shell-side fouling at the model design value, the sensitivity of the jacket water cooler to tube-side fouling effects is shown on Figure 6-1.7.4. THERMAL MARGIN ASSESSMENT The clean and service available thermal margins are 97.69 % and 0.01 % respectively.

7.5. MINIMUM SERVICE WATER FLOW RATE As shown in Figure 6-2 the service water flow can be throttled down to account for lower service water inlet temperature conditions.

The heat exchanger can remove the design heat load for the diesel at 100% rated power, 7,800,000 BTU/hr, by reducing service water flow rates as the service water temperature decreases.

Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref-: P&! 5-1 PROTO-POWER CORPORATION CALC NO. 9 7_1 9 7 REV A PAGE 12 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/26/98 VERIFIED BY S. Ingalls JOB NO.31-003 CI T colED / LaSalle County Station """ COMED / LaSalle Station GL 89-13 Program ITI.E Thermal Model of COMED / LaSalle Station 113(2B) Diesel Generator Jacket Water Coolers.

8.0 REFERENCES

8.1. LaSalle Station UFSAR, Sections:

9.2.1 and 9.5.5.1.1 (Attachment B)8.2. NRC Generic Letter 89-13 8.3. GE Purchase Specification

-211872RO-SW9 Item 4.3.6.1 8.4. LaSalle Station FSAR Q40.92 (Attachment B)8.5. Stewart & Stevens Vendor Manual, VM J-152 through VM J-157 8.6. 0 & M Manufacturing Hx Data Sheet (Attachment A)8.7. LaSalle Station Drawing, VPF -3411-080(1)-I, J-2500 (Attachment A)8.8. LaSalle Station Drawing, VPF -3411-080(2)-1, J-2500 (Attachment A)8.9. Standard of the Tubular Exchanger Manufacturers Association 8.10. Heat Exchanger Thermal Performance Modeling Software Program PROTO-HXrm Version 3.02 Software Validation and Verification Report (SVVR) SQA No. SVVR-93948-02, Revision F, dated 2/17/98 8.11. Proto-Power Calculation 93-048, "Fluid Properties

-Fresh Water -Range 32TF to 500'F", Rev. A Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 Attachment A to Proto-Power Calculation 97-197 Revision A Proto-Power Caic: 97-197

Attachment:

A Rev: A Page 1 of 4 a,-)81,0 (.0 o & I( 2:3 CiPANY z~. 7.ras OCT 11 1974 cO~jNsczM%;

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OR NrviEV USLLSS SIC"a(f AC~vir NLIA~rO IT Y ý ICLEASE so.--- MIM~~iu ~Proto-lower No TE: 0" ,-: -'S -1 3 OCS, ~ ~ sst I- SLDCosri(.Ak2t)4t 0 L (Cabc: 97-197 A ge of 4 (L 7 L 7 D 6 5 //~ S 6.... 6.6%" GA,- I) --"I,?" !C *0P, 1 M V O C'D::1 C I I .1(1, s. -...- .- IV I., --EMPVRtL.:--SIPE ViEW-Hk1LL 000.tA w~

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Attachment:

B Rev: 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 equipment 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 Ecruipment Cooling Water System 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 Desian Bases 9.2.1.1.1 Safety Design Bases a. The system is sized based on the following minimum equipment cooling water flow requirements:

1. RHR heat exchanger

-7400 gpm 2. diesel-generator cooler (division 1 and 2 only) -800 gpm 3. diesel-generator cooler (division

3) -650 gpm Proto-Power Ca~c: 97-197

Attachment:

B Rev: A Page 2 of 5 9.2-1 REV. 12 -MARCH 1998 veReN cE .I 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 h. C oo -- annunciate -I 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-gene'rator skid-mounted system fuel oil parameters:

fuel oil temperature, fuel pump suction strainer inlet and outlet pressure (Divisions 1 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 I 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 9.5.5.1.1 Safety Design Bases 0 SCooling capacity of this system is based on a diesel-generator output of 2860 kW with an environmental temperature of 1220 F maximum and a minimum and maximum lake water temperature of 320 F and 1000 F, respectively.

Total heat transfer by this system is o9 9.5-34 REV. 0 -APRIL 1984 I\5 WaUNC5 UII LSCS-UFSAR approximately 7.8 x 106 Btu/hr per diesel-generator set at rated capacity.

The diesel cooling water heat exchangers are O~sized based on operation of 110% of rated load.High water temperatiue 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 Design 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.The engine cooling water heat exchanger is a two-pass shell and 0 0 tube type heat exchanger having admiralty tubes with a carbon T steel water box and shell. Engine cooling water is circulated through the shell side while strained lake water is pumped U M through the tube side by the CSCS-ECWS (Subsection 9.2.1). -Design pressure and temperature is 150 psig and 3000 F for both 0 0 0-9.5-35 REV. 0 -APRIL 1984 0 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 water system when the diesel generator is operating at rated capacity.

Also, in section 9.5.5.2 you mention that the cooling waterflow 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 SThe design conditions for each diesel-generator cooling water system are:Shell side flow 1100 gpm i Design shell side inlet temperature 1900-F.Shell side outlet temperature 175a- F.Tube side design flow 800 gpm Tube side inlet temperature 1000 F Tube side outlet temperature 1220 F ChHeat exchanger design eat 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 Caic: 97-197 Q40.92-1

Attachment:

B Rev: A Page 5 of 5 Attachment C to Proto-Power Calculation 97-197 Revision A Proto-Power Calc: 97-197

Attachment:

C Rev: A Page 1 of 13 15:41:55 P ROTO-LX 3.02 by Proto-Power Corporation (SN#PIIX-0000)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.Vendor Data -BENCHMARK 06/26/98 Shell and Tube Heat Exchanger Input Parameters V iidQ antiTy, gTpa- .........m ---- ....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-ftt 2.F)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-106474 .795-.2-5--

190.00 100.00 '175.00 121.00 -P A 0.00050 0.00200 Fresh Water Fresh Water 8,505,000 241.70 0.633693000

~~~0.00 j¢tOPý07D- fly,. CALC U OP 00 4 CO T M- 14 C O IJ 1.I T I O A I T E M A -E .-D A T A 5 O C E '482.00 ALUG 1.001961568 1 0.438000000 5.600 0.7500 Triangular Number of Tube Passes 2 U-Tubes No Total Number of Tubes 420 Number of Active Tubes 420 Tube Length (ft) 7.00 Tube Inside Diameter (in) 0.541 Tube Outside Diameter (in) 0.625 Tube Wall Conductivity (BTU/hr-ft.°F) 58.00 Ds, Shell Inside Diameter (in) 0.000 Lbc, Central Baffle Spacing (in) 0.000 Lbi, Inlet Baffle Spacing (in) 19.688 Lbo, Outlet Baffle Spacing (in) 19.688 Dotl, 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: 97-197

Attachment:

C Rev: A Page 2 of 13 15:41:55 PROTO-IHX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonvealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.Vendor Data -BENCHMARK 06/26/98 I.Cjalculation Specitications 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)795.3 1,064.5 100.0 190.0 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.°F)Tube-Side hi (BTU/hr-ft 2.°F)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.°F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (OF)Skin Visc (lbm/ft-hr)

Tube Temp In (°F)Density (lbm/ft 3) Tube Temp Out (OF)Cp (BTU/lbm'°F)

Tav Tube (°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)5.325E+5 C01nP4Rj 3.978E+5 5] .277E+6]71.8 482.0 Overall Fouling (hr'fta'°F/BTU)

Shell-Side ho (BTU/hr-ft 2 0'F)Tube-Side hi (BTU/hr-ft 2.-F)I/Wall Resis (BTU/hr.ft 2.°F)LMTD Correction Factor 0.002811 1,889.7 1,576.5 15,431.0 0.9895 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.°F)

Shell-Side 5.58 7.707E+04 2.13 0.82 0.88 60.53 1.00 0.39 Tube-Side 5.33 3.620E+04 4.03 1.48 1.31 61.85 1.00 0.37 U Overall (BTU/hr-ft2.°F)

Shell Temp In (IF)Shell Temp Out (°F)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (fF)Proto-Power Calc: 97-197

Attachment:

C Rev: A Page 3 of 13 241.7 190.0 174.5 182.2 173.1 100.0 120.8 110.4 123.1** Reynolds Number Outside Range of Equation Applicability 1! With Minimum Fouling The Test Heat Load Could Not Be Achie 16:18:54 PROTO-HX 3.02 by Proto-Power Corporation (SN#PtHX-0000)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.Design Conditions

-Adjusted Eff. Area 06/26/98 Shell and Tube Heat Exchanger Input Parameters Shell-Side Flii 0-Q-uTiaq f-, Trt-al ... .. p_-n ...... .I_,G064T.46--

Inlet Temperature OF 190.00 Outlet Temperature OF 175.00 Fouling Factor 0.00050 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)

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 Tube-Side..-- 7972-5-100.00 121.00 0.00200 Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0.00 CALCuLATE.0 TEMA-E t~io SE.3.,[468. 17 0.973212339 1 0.438000000 5.600 0.7500 Triangular Number of Tube Passes 2 U-Tubes No Total Number of Tubes 420 Number of Active Tubes 420 Tube Length (ft) 7.00 Tube Inside Diameter (in) 0.541 Tube Outside Diameter (in) 0.625 Tube Wall Conductivity (BTU/hr'ft.°F) 58.00 Ds, Shell Inside Diameter (in) 0.000 Lbc, Central Baffle Spacing (in) 0.000 Lbi, Inlet Baffle Spacing (in) 19.688 Lbo, Outlet Baffle Spacing (in) 19.688 Dotl, 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: 97-197

Attachment:

C Rev: A Page 4 of 13 16:18:54 PROTO-HIX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report, for DGOIB -LSCS -HPCS DG Hx.Design Conditions

-Adjusted Eff. Area 06/26/98 I. .1 Calculation Speciications II Iw I 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)795.3 1,064.5 100.0 190.0 IF Fouling Calculation Results Shell Mass Flow (Ibrn/lh)

U Overall (BTU/hr-ft 2.F)Tube Mass Flow (Ibm/hi) Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr'ft 2'°F)Heat Transferred (BTU/hr) I/Wall Resis (BTUJ/hr-ft2-.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 (OF)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (IF)Bulk Vise (lbm/ft-hr)

Shell Skin Temp (°F)Skin Vise (lbm/ft-hr)

Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (°F)Cp (BTUilbm 0'F) Tav Tube (°F)K (BTU/hr'ft'°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 (Ibm./ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm 0 F)K (BTU/hrft°F)

Shell-Side 5.58 7.717E+04 2.13 0.82 0.87 60.52 1.00 0.399 5.325E+5 3.978E+5 8.089E+6 72.2 468.2 Tube-Side 5.33 3.612E+04 4.04 1.48 1.31 61.86 1.00 0.37 U Overall (BTU/hr-ft 2.°F)Shell Temp In (OF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (IF)Tav Tube (OF)Tube Skin Temp (IF)Proto-Power Calc: 97-197

Attachment:

C Rev: A Page 5 of 13 241.7 190.0 174.8 182.4 173.2 100.0 120.4 110.2 123.0 Overall Fouling (hr-ft 2"°F/BTU)Shell-Side ho (BTUfhr'ft 2.°F)Tube-Side hi (BTU/hrift 2-0 F)I/Wall Resis (BTU/hr-ft 2-°F)LMTD Correction Factor 0.002811 1,890.3 1,574.7 15,431.0 0.9901** Reynolds Number Outside Range of Equation Applicability

' With Minimum Fouling The Test Heat Load Could Not Be Achie 10:11:56 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DG0IB -LSCS -HPCS DG Hx.LSCS Reference Cond. Vendor Fouling 06/26/98 Shell and Tube Heat Exchanger Input Parameters I Shell-Side Fleit d-TeimpierTure-

---pill p .19 I-,1o_90-00 Inlet Temperature OF 190.00 Outlet Temperature OF 175.00 Fouling Factor 0.00050 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)

Heat Exchanger Type Effective Area (ftA2)Area Factor Area Ratio Tube-Side 100.00 121.00 0.00200 Fresh Water Fresh Water 8,505,000 241.70 0.616913000 0.00 TEMA-E 468.17 0.973212339 1 0.438000000 5.600 0.7500 Triangular 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/hrift.°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 420 420 7.00 0.541 0.625 58.00 0.000 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-197

Attachment:

C Rev: A Page 6 of 13 10:11:56 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.LSCS Reference Cond. Vendor Fouling 06/26/98 I. .1 Cralculation Specifications II itI 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 (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 (OF)650.0 1,100.0 100.0 190.0 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'ft 2"°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 (hrift 2.°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 (°F)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (OF)Skin Visc (lbm/ftfhr)

Tube Temp In (IF)Density (lbmr/ft 3) Tube Temp Out (OF)Cp (BTU/Ibm 0'F) Tav Tube (IF)K (BTU/hr-ft."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')Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)

Skin Vise (lbrr/ft'hr)

Density (Ibm/ft 3)Cp (BTU/Ibmc'F)

K (BTU/hr-ft.°F)TgUtJ 5.503E+5.CS , 3.252E+5.gui~D. 7.718E+6 Overall Fouling (hr-ft 2-F1BT1U)Shell-Side ho (BTU/hr ft 2.°F)Tube-Side hi (BTU/hr-ft 2.F)1/Wall Resis (BTU/hr-ft 2.°F)LMTD Correction Factor 0.002811 1,880.7 1,354.4 15,431.0 0.9890 Shell-Side 5.77 8.005E+04 2.12 0.82 0.87 60.51 1.00 0.39 Tube-Side 4.36 3.003E+04 3.96 1.46 1.27 61.83 1.00 0.37 U Overall (BTU/hr-ft 2.°F)Shell Temp In (IF)Shell Temp Out (°F)Tav Shell (IF)Shell Skin Temp (OF)Tube Temp In (°F)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)Proto-Power Calc: 97-197 234.7 190.0 176.0 183.0 174.1 100.0 123.8 111.9 126.1** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie

Attachment:

C Rev: A Page 7 of 13 21:11:51 PROTO-FIX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.Reduced FF to meet LSCS Ref. Cond.06/26/98 I Shell and Tube Heat Exchanger Input Parameters Ii 1.FI id-Qi.-iit T6Tur F gpF Inlet Temperature OF Outlet Temperature

°Fouling Factor Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/hr)Design Heat Trans Coeff (BTU/hr'ft 2 0-F)Emprical Factor for Outside hi 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;hell-Side Tube-Side ,0-644-6 .795_2-5-190.00 100.00 vN,%Oo2 VALUES 175.00 121.00 A .or ' SC .I 0.00050 0.00200 r0LLt-'O3L

________I CALfL*-rtG"-T0)

Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0.00 TEMA-E 468.17 0.973212339 1 0.438000000 5.600 0.7500 Triangular 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 Wall 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)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 420 420 7.00 0.541 0.625 58.00 0.000 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-197

Attachment:

C Rev: A Page 8 of 13 21:11:51 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHIX-0000)

Commonwealth Edison Calculation Report for DGO1B -LSCS -HPCS DG Hx.Reduced FF to meet LSCS Ref. Cond.06/26/98'I Calculation Specifications II II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions I Fouling Was Input by User]- Fou,,,G"/i:'AcTop R) U Ce D Extrapolation Data'RCA c14C-D 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)Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (°F)Shell Inlet Temp (°F)646.1 1,064.5 100.0 190.0 0.002732 Input Fouling Factor Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft'° 0 F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr'ft 2"°F)Tube-Side hi (BTU/hr'ftt'°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"F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (°F)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (°F)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (°F)Skin Visc (lbm/fthr)

Tube Temp In (°F)Density (Ibm/fe) Tube Temp Out (°F)Cp (BTU/Ibm-°F)

Tav Tube (°F)K (BTU/hr'ft-°F)

Tube Skin Temp (°F)Extrapolation Calculation Results Shell Mass Flow (lbm/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 (lbm/ft-hr)

Skin Visc (lbm/ft'hr)

Density (lbm/ft 3)Cp (BTU/1bm 0'F)K (BTU/hr-ft'°F) 5.325E+5 3.232E+5 7.801.E+6/./o 70.5 468.2 Overall Fouling (hr.ft 2°F/BTU) 0.002732 Shell-Side ho (BTU/hr'ft 2-IF) " 1,892.1 Tube-Side hi (BTU/hrW'f"F)

AJ)3"U!T" 1,349.8 I/Wall Resis (BTU/hr'ft 2"F) O PlI-L..- 15,431.0 LMTD Correction Factor ixLI tic'" 0.9881 rFqCT U Overall (BTU/hr ft 2.OF)239.2 Shell-Side 5.58 7.731 E+04 2.13 0.82 0.87 60.52 1.00 0.39 Tube-Side 4.33 2.991 E+04 3.95 1.45 1.27 61.83 1.00 0.37 Shell Temp In (°F) 190.0 Shell Temp Out (°F) 175.4 Tav Shell (IF) 182.7 Shell Skin Temp (OF) 173.8 Tube Temp In (IF) 100.0 Tube Temp Out (OF) 124.2 Tav Tube (°F) 112.1 Tube Skin Temp (OF) 126.5 Proto-Power Calc: 97-197

Attachment:

C Rev: A Page 9 of 13** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 21:09:55 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.LSCS Ref. Condition

-FINAL MODEL 06/26/98 Shell and Tube Heat Exchanger Input Parameters II I. 'Shell-Side Fluiid Qiiaiiiitiy-, T6t-a.1 ....... -.46 .Inlet Temperature OF 190.00 Outlet Temperature OF 175.00 Fouling Factor 0.00050 Shell Fluid Name Tube Fluid Name Design Heat Transfer (BTU/Ihr)Design Heat Trans Coeff (BTU/hr'ft 2"°F)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 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-°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 Tube-Side.795_25.100.00 RetuCD- ?121.00 ,7'1E-5$IDC 0.00193 F- ()-Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0.00 , M0 1-TEMA-E 0 0.973212339 1 0.438000000 5.600 0.7500 Triangular 2 No 420 420 7.00 0.541 0.625 58.00 0.000 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-197

Attachment:

C Rev: A Page 10 of 13 21:09:55 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIIX-0000) 06/26/98 Commonwealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.LSCS Ref. Condition

-FINAL MODEL Calculation Specitications II I.Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions

'U1; r I 1,.,k 11'.L IL-' ' -L .1ý2 .1 --., I INCLWr)ES Re 6`SoD- Extrapolation Data 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)Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)646.1 1,064.5 100.0 190.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr.ft2.°F)

Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr.wft 2-F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/ir ft 2-OF)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 (IF)Prandtl Number Tav Shell (IF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (OF)Skin Visc (lbm/ft-hr)

Tube Temp In (OF)Density (Ibm/ft')

Tube Temp Out (IF)Cp (BTU/Ibm 0'F) Tav Tube (IF)K (BTU/hr.ft-°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)5.325E+5 3.232E+5 7.801E+6 70.5 468.2 Overall Fouling (hr ft 2-°F/BTU) 0.002732 Shell-Side ho (BTU/hr'ft 2"F) 1,892.1 Tube-Side hi (BTU/hr-ft 2.-F) DF51 & 1,349.8 I/Wall Resis (BTU/hr-ft 2.°F) 1'AT S0SIV) 15,431.0 LMTD Correction Factor OcU6(2,LL-0.9881 U Overall (BTU/hr-ft 2-OF) ' "/O/( 239.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ftl)Cp (BTU/Ibm.°F)

K (BTU/hr-ft-°F)

Shell-Side 5.58 7.731 E+04 2.13 0.82 0.87 60.52 1.00 0.39 Tube-Side 4.33 2.991 E+04 3.95 1.45 1.27 61.83 1.00 0.37 Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (°F)Tube Skin Temp (°F)Proto-Power Caic: 97-197

Attachment:

C Rev: A Page 11 of 13 190.0 175.4 182.7 173.8 100.0 124.2 112.1 126.5** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 10:17:46 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIHX-0000)

Commonwealth Edison Calculation Report for DGO1B -LSCS -HPCS DG Hx.CLEAN -FINAL MODEL 06/26/98 Shell and Tube Heat Exchanger Input Parameters Shell-Side Tub II Fluid Quantity, Tht-aT ..g.p.m1 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

'°F)Emprical Factor for Outside h Performance Factor (% Reduction)

-1V,064.46

.. ..__.7 190.00 1 175.00 1 0.00050 0.'--Side!95725--00.00 21.00 00193 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 Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0.00 TEMA-E 468.17 0.973212339 1 0.438000000 5.600 0.7500 Triangular Number of Tube Passes U-Tubes Total Number of Tubes Number of Active Tubes Tube Length (fit)Tube Inside Diameter (in)Tube Outside Diameter (in)Tube Wall 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)Dot], 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 420 420 7.00 0.541 0.625 58.00 0.000 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-197

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C Rev: A Page 12 of 13 10:17:46 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.CLEAN -FINAL MODEL 06/26/98 Calculation Specifications 11 Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by Oser. 0 F0(ji,& FQ0iZ ",CLCAN" 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 (OF)Input Fouling Factor 646.1 1,064.5 100.0 190.0 0.000000 Fouling Calculation Results Shell Mass Flow (Ibm/hir)

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.°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hruft 2.°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 (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/ft 3) Tube Temp Out (IF)Cp (BTU/Ibm-'F)

Tav Tube (IF)K (BTU/hr'ft.

0 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)5.325E+5 lylgifIIUt 3.232E+5 51.1 468.2 Overall Fouling (hr-ft 2.°F/BTU Shell-Side ho (BTU/hrlft 2-°F)Tube-Side hi (BTU/hrbft 2.0 F)I/Wall Resis (BTU/hr-ft 2.°F)LMTD Correction Factor 0.000000 1,839.7 1,455.3 15,431.0 0.9039 Property Shell-Side Velocity (hf/s) 5.57 Reynold's Number 7.363E+04 Prandtl Number 2.24 Bulk Visc (Ibm/ft-hr) 0.86 Skin Visc (lbm/ft'hr) 1.00 Density (lbm/ft 3) 60.67 Cp (BTU/Ibm-'F) 1.00 K (BTU/hr ft 0'F) 0.39 Tube-Side 4.34 3.347E+04 3.49 1.30 1.01 61.65 1.00 0.37 U Overall (BTU/hr ft 2.°F)Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Ter (°F)Proto-Power Cabc: 97-197

Attachment:

C Rev: A Page 13 of 13 713.2 190.0 161.1 175.5 155.5 100.0 147.8 123.9 153.1** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Attachment D to Proto-Power Calculation 97-197 Revision A Proto-Power Caic: 97-197

Attachment:

D Rev: A Page 1 of 7 21:09:55 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PIHX-0000)

Commonwealth Edison Calculation Report for DGO1B -LSCS -HPCS DG Hx.LSCS Ref. Condition

-FINAL MODEL 06/26/98 I Shell and Tube Heat Exchanger Input Parameters 11 11 FIii-QiYidWl-tfyi-TT6t

...p.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"°F Emprical Factor for Outside h Performance Factor (% Reduction)

Heat Exchanger Type Effective Area (ft^2)Area Factor Area Ratio Shell-Side Tube-Side-170-6-4746-

........ ..79-5-.2-5

--190.00 100.00 175.00 121.00 0.00050 0.00193 Fresh Water Fresh Water 8,505,000) 241.70 0.633693000 0.00 TEMA-E 468.17 0.973212339 Number of Shells per Unit Shell Minimum Area Shell Velocity (ft/s)Tube Pitch (in)Tube Pitch Type 1 0.438000000 5.600 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-.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 420 420 7.00 0.541 0.625 58.00 0.000 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-197

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D Rev: A Page 2 of 7 09:18:47 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.Tube--side Fouling = 0.0000 06/26/98 Calculation Specitications II I.l 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 (IF)Shell Inlet Temp (IF)Input Fouling Factor 646.1 1,064.5 100.0 190.0 0.000500 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr.ft 2 .F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hrlft 2..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'fte.OF/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 Vise (lbm/ft-hr)

Shell Skin Temp (IF)Skin Visc (lbm/ft-hr)

Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (OF)Cp (BTU/Ibm 0'F) Tav Tube (IF)K (BTU/hr-ft."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)Property Shell-Side Velocity (ft/s) 5.57 Reynold's Number 7.47 1E+04 Prandtl Number 2.20 Bulk Visc (lbm/ft.hr) 0.85 Skin Visc (lbm/ft-hr) 0.95 Density (Ibm/ftl) 60.63 Cp (BTU/lbm.°F) 1.00 K (BTU/hr'ft.°F) 0.39 5.325E+5 3.232E+5 1.316E+7 56.9 468.2 Tube-Side 4.34 3.240E+04 3.62 1.34 1.09 61.71 1.00 0.37 Overall Fouling (hr-ft 2-°F/BTU)Shell-Side ho (BTU/hr-ft 2"°F)Tube-Side hi (BTU/hr-ft 2.0 F)I/Wall Resis (BTU/hr-ft 2.°F)LMTD Correction Factor U Overall (BTU/hr ft 2.°F)Shell Temp In (IF)Shell Temp Out (OF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (IF)Tube Temp Out (IF)Tav rube (IF)Tube Skin TempF)Proto-Power Calc: 97-197

Attachment:

D Rev: A Page 3 of 7 0.000500 1,856.7 1,423.4 15,431.0 0.9458 522.2 190.0 165.3 177.7 161.6 100.0 140.8 120.4 144.7** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat. Load Could Not Be Achie 09:19:59 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHlX-0000)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.Tube--side Fouling = 0.0005 06/26/98 Calculation Specifications Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Tube Flow (gpm) 646.1 Shell Flow (gpm) Shell Flow (gpm) 1,064.5 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 (OF) Input Fouling Factor 0.001078 Fouling Calculation Results Shell Mass Flow (Ibm/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 .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 .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 (°F)Skin Visc (Ibm/ft-hr)

Tube Temp In (IF)Density (Ibrn/ft)

Tube Temp Out (IF)Cp (BTU/lbm 0'F) Tav Tube (IF)K (BTU/hr-ft-0 F) Tube Skin Temp (IF)Extrapolation Calculation Results Shell Mass Flow (lbmr/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)Property Shell-Side Velocity (ft/s) 5.57 Reynold's Number 7.566E+04 Prandtl Number 2.18 Bulk Visc (lbm/ft-hr) 0.84 Skin Visc (lbm/ft-hr) 0.92 Density (Ibrn/ft')

60.59 Cp (BTU/Ibm 0'F) 1.00 K (BTU/hr.ft 0'F) 0.39 5.325E+5 3.232E+5 1. 12E+7 61.9 468.2 Tube-Side 4.34 3.148E+04 3.74 1.38 1.15 61.75 1.00 0.37 Overall Fouling (hr-ft 2-°F/BTU)Shell-Side ho (BTU/hr'ft 2'°F)Tube-Side hi (BTU/hr.ft 2.OF)1/Wall Resis (BTU/hrft 2 0-IF)LMTD Correction Factor 0.001078 1,870.2 1,396.4 15,431.0 0.9675 U Overall (BTU/hr-ft 2.°F)Shell Temp In (°F)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (OF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin TWOWEPo ower Calc: 97-197

Attachment:

D Rev: A Page 4 of 7 399.2 190.0 169.0 179.5 166.2 100.0 134.7 117.3 137.9** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 09:20:56 0 1 PROTO-HIX 3.02 by Proto-Power Corporation (SN#PIIX-0000)

Commonwealth Edison Calculation Report for DGO1B -LSCS -HPCS DG Hx.Tube--side Fouling = 0.00 10 06/26/98 Calculation Specifications II ,I 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 (IF)Shell Inlet Temp (IF)Input Fouling Factor 646.1 1,064.5 100.0 190.0 0.001655 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.°F)Tube-Side hi (BTU/hr-ft 2-°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft-°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 (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 (Ibm/ft 3) Tube Temp Out (IF)Cp (BTU/Ibm-0 F) Tav Tube (IF)K (BTU/hr'ft'°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')Property Shell-Side Velocity (ft/s) 5.58 Reynold's Number 7.637E+04 Prandtl Number 2.15 Bulk Visc (brrm/ft-hr) 0.83 Skin Visc (lbm/ft-hr) 0.90 Density (lbmlft')

60.56 Cp (BTU/lbm.°F) 1.00 K (BTU/hr.ft.°F) 0.39 5.325E+5 3.232E+5 9.727E+6 65.6 468.2 Tube-Side 4.34 3.080E+04 3.83 1.41 1.20 61.79 1.00 0.37 Overall Fouling (hr ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2 -F)Tube-Side hi (BTU/hr-ft 2'°F)I/Wall Resis (BTU/hr.ft 2 F)LMTD Correction Factor U Overall (BTU/hr-ft 2-°F)Shell Temp In (OF)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (fF)Tube Temp Out (IF)Tav Tube (IF)Tube Skin rm A-ower Calc: 97-197

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D Rev: A Page 5 of 7 0.001655 1,879.8 1,376.2 15,431.0 0.9784 323.5 190.0 171.8 180.9 169.6 100.0 130.1 115.1 132.9** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 09:21:56 PROTO-IIX 3.02 by Proto-Power Corporation (SN#IIPX-0000)

Commonwealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.Tube--side Fouling = 0.00 15 06/26/98 Calculation Specitications II Constant Inlet Temperature Method Was Used Extrapolation Was to User Specified Conditions Fouling Was Input by User Test Data Extrapolation Data Data Date Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (IF)Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (IF)Input Fouling Factor 646.1 1,064.5 100.0 190.0 0.002233 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.'F)Tube-Side hi (BTU/hr-ft 2-.F)Heat Transferred (BTUihr) I/Wall Resis (BTU/lhr-ft 2-OF)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 (IF)Prandtl Number Tav Shell (OF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (OF)Skin Visc (Ibm/ft-hr)

Tube Temp In (OF)Density (lbm/ft')

Tube Temp Out (°F)Cp (BTU/Ibm.°F)

Tav Tube (OF)K (BTU/hrxft-°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')Property Shell-Side Velocity (ft/s) 5.58 Reynold's Number 7.692E+04 Prandtl Number 2.14 Bulk Visc (lbm/ft-hr) 0.82 Skin Visc (Ibm/ft-hr) 0.88 Density (Ibm/ft 3) 60.53 Cp (BTU/lbm.°F) 1.00 K (BTU/hr-ft 0'F) 0.39 5.325E+5 3.232E+5 8.59E+6 68.5 468.2 Overall Fouling (hr'ft 2."F/BTU)Shell-Side ho (BTU/hr'ft 2 1-F)Tube-Side hi (BTU/hr-ft 2.0 F)I[Wall Resis (BTU/hr ft 2-°F)LMTD Correction Factor 0.002233 1,887.1 1,360.6 15,431.0 0.9847 Tube-Side 4.33 3.027E+04 3.90 1.44 1.24 61.81 1.00 0.37 U Overall (BTU/hr.ft 2 0.F)Shell Temp In (IF)Shell Temp Out (IF)Tav Shell (°F)Shell Skin Temp (OF)Tube Temp In (°F)Tube Temp Out (IF)Tav Tube (IF)Tube roto-uower Calc: 97-197

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D Rev: A Page 6 of 7 272.0 190.0 173.9 182.0 172.1 100.0 126.6 113.3 129.2** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 09:22:56 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIX-0000)

Commonwealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.Tube--side Fouling = 0.001932 (LIMIT)06/26/98 Calculation Specifications II-I I I 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 (IF)Shell Inlet Temp (IF)Input Fouling Factor 646.1 1,064.5 100.0 190.0 0.002732 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr ft 2.°F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr'ft2 t'F)Tube-Side hi (BTU/hr-ft 2.OF)Heat Transferred (BTU/hr) l/Wall Resis (BTU/lhrft 2.°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 (IF)Prandtl Number Tav Shell (OF)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (IF)Skin Visc (Ibm/ft hr) Tube Temp In (IF)Density (lbm/ft 3) Tube Temp Out (°F)Cp (BTU/Ibm.°F)

Tav Tube (IF)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')Property Shell-Side Velocity (ft/s) 5.58 Reynold's Number 7.731 E+04 Prandtl Number 2.13 Bulk Visc (lbm/ft-hr) 0.82 Skin Visc (Ibm/ft-hr) 0.87 Density (Ibm/ft 3) 60.52 Cp (BTU/lbm-nF) 1.00 K (BTU/hr-ft.°F) 0.39 5.325E+5 3.232E+5 7.801 E+6 70.5 468.2 Tube-Side 4.33 2.991 E+04 3.95 1.45 1.27 61.83 1.00 0.37 Overall Fouling (hr-ft 2--F/BTU)Shell-Side ho (BTU/hr.ft 2-OF)Tube-Side hi (BTU/hr-ft 2-OF)I/Wall Resis (BTU/hr.ft2 -F)LMTD Correction Factor 0.002732 1,892.1 1,349.8 15,431.0 0.9881 U Overall (BTU/hr.ft 2.°F)Shell Temp In (°F)Shell Temp Out (IF)Tav Shell (IF)Shell Skin Temp (fF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin T _ff ower Cabc: 97-197

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D Rev: A Page 7 of 7 239.2 190.0 175.4 182.7 173.8 100.0 124.2 112.1 126.5** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Attachment E to Proto-Power Calculation 97-197 Revision A Proto-Power Calc: 97-197

Attachment:

E Rev: A Page 1 of 10 21:09:55 PROTO-HX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.LSCS Ref. Condition

-FINAL MODEL 06/26/98 Shell and Tube Heat Exchanger Input Parameters 11 1.Shell-Side Inlet Temperature OF 190.00 Outlet Temperature OF 175.00 Fouling Factor 0.00050 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.........

-79572-5 -100.00 121.00 0.00193 Fresh Water Fresh Water 8,505,000 241.70 0.633693000 0.00 TEMA-E 468.17 0.973212339 1 0.438000000 5.600 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-ft.'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 420 420 7.00 0.541 0.625 58.00 0.000 0.000 19.688 19.688 0.000 0.000 0.000 0.000 0.000 Proto-Power Calc: 97-197

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E Rev: A Page 2 of 10 22:25:58 PROTO-IHX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DG0IB -LSCS -HPCS DG Hx.CSCS=35 0 F 06/26/98 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)202.4 1,064.5 35.0 190.0 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.°F)Tube-Side hi (BTU/hr-ft 2-OF)Heat Transferred (BTU/hr) 1/Wall Resis (BTUJ/hr.ft 2.°F)LMTD LMTD Correction Factor Effective Area (ft 2)Overall Fouling (hr-Wf.°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 (IF)Skin Visc (lbm/ftrhr)

Tube Temp In (IF)Density (Ibm/ftr)

Tube Temp Out (°F)Cp (BTU/Ibm.°F)

Tav Tube (°F)K (BTU/hrlft-°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')Property Shell-Side Velocity (ft/s) 5.58 Reynold's Number 7.731 E+04 Prandtl Number 2.13 Bulk Visc (Ibm/ft-hr) 0.82 Skin Visc (lbmlft-hr) 0.87 Density (Ibm/fl 3) 60.52 Cp (BTU/Ibm-'F) 1.00 K (BTU/hr.ft.°F) 0.39 5.325E+5 1.0 12E+5 7.8E+6 106.1 468.2 Tube-Side 1.35 6.04 1E+03 6.41 2.25 1.29 62.27 1.00 0.35 Overall Fouling (hr-ft'-°F/BTU)

Shell-Side ho (BTU/hr-ft2-°F)

Tube-Side hi (BTU/hr.ft 2.°F)1/Wall Resis (BTU/hr-ft 2.°F)LMTD Correction Factor 0.002732 1,891.5 393.5 15,431.0 0.9829 U Overall (BTU/hr ft 2.°F)Shell Temp In (°F)Shell Temp Out (IF)Tav Shell (°F)Shell Skin Temp (°F)Tube Temp In (°F)Tube Temp Out (IF)Tav Tube (°F)Tube Skin Temp (°F)Proto-Power Calc: 97-197

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E Rev: A Page 3 of 10 159.7 190.0 175.4 182.7 173.5 35.0 112.0 73.5 124.7** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 22:22:16 PROTO-ntX 3.02 by Proto-Power Corporation (SNaPHX-s000)

Commonwealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.CSCS=40'F 06/26/98 I. .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 (°F)Shell Temp Out ('F)Tube Flow (gpm)Tube Temp In (fF)Tube Temp Out (°F)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (OF)Shell Inlet Temp (OF)209.1 1,064.5 40.0 190.0 Fouling Calculation Results Shell Mass Flow (lbmlhr) U Overall (BTU/hr ft 2.0 F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr ft 2.°F)Tube-Side hi (BTU/hr-ft 2'°F)Heat Transferred (BTU/hr) i/Wall Resis (BTUfhrft 2.°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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (°F)Bulk Visc (lbm/ft'hr)

Shell Skin Temp (OF)Skin Visc (lbm/ft-hr)

Tube Temp In (°F)Density (lbm/ft 3) Tube Temp Out (OF)Cp (BTU/lbm-°F)

Tav Tube (°F)K (BTU/hr'ft-°F)

Tube Skin Temp (°F)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 (lbm/ft-hr)

Skin Visc (Ibm/ft-hr)

Density (lbm/ft')Cp (BTU/Ibm.°F)

K (BTU/hr"ft-°F)

Shell-Side 5.58 7.73 1E+04 2.13 0.82 0.87 60.52 1.00 0.39 5.325E+5 1.046E+5 7.8E+6 102.5 468.2 Tube-Side 1.39 6.552E+03 6.08 2.15 1.29 62.24 1.00 0.35 U Overall (BTU/hr ft 2 -F)Shell Temp In (OF)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (7F)Tube Temp In (°F)Tube Temp Out (°F)Tav Tube (°F)Tube Skin Temp (°F)Proto-Power Calc: 97-197

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E Rev: A Page 4 of 10 165.5 190.0 175.4 182.7 173.5 40.0 114.6 77.3 124.7 Overall Fouling (hr-ft 2 1-F/BTU)Shell-Side ho (BTU/hr'ft 2-°F)Tube-Side hi (BTU/hr-ft 2.-F)I/Wall Resis (BTUfhr.ft 2-°F)LMTD Correction Factor 0.002732 1,891.5 425.1 15,431.0 0.9822** Reynolds Number Outside Range of Equation Applicability

\With Minimum Fouling The Test Heat Load Could Not Be Achie 22:05:05 PROTO-HX 3.02 by Proto-Power Corporation (SN#PRX-0000)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.CSCS=50°F 06/26/98 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 Shell Flow (gpm)Shell Temp In (°F)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (°F)Tube Temp Out (°F)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (°F)Shell Inlet Temp (OF)227.4 1,064.5 50.0 190.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr'ft 2.°F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr-ft 2.-F)Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ftt-OF)

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 Vise (lbm/ft-hr)

Shell Skin Temp (IF)Skin Vise (lbrn/ft-hr)

Tube Temp In (°F)Density (Ibm/ft 3) Tube Temp Out (°F)Cp (BTU/Ibm'°F)

Tav Tube (OF)K (BTU/hr'ft'°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 Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (Ibm/ft 3)Cp (BTU/Ibm-0 F)K (BTU/hr'ft°F)

Shell-Side 5.58 7.73 1E+04 2.13 0.82 0.87 60.52 1.00 0.39 5.325E+5 1. 138E+5 7.8E+6 95.9 468.2 Tube-Side 1.52 7.772E+03 5.52 1.97 1.29 62.17 1.00 0.36 U Overall (BTU/hr-ft 2.°F)Shell Temp In (0 F)Shell Temp Out (fF)Tav Shell (°F)Shell Skin Temp (°F)Tube Temp In (°F)Tube Temp Out (°F)Tav Tube (°F)Tube Skin Temp (°F)Proto-Power Calc: 97-197

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E Rev: A Page 5 of 10 177.1 190.0 175.4 182.7 173.5 50.0 118.6 84.3 124.8 Overall Fouling (hr-ft 2-°F/BTU)Shell-Side ho (BTU/hr-ft 2-°F)Tube-Side hi (BTU/hr-ft 2-IF)1/Wall Resis (BTU/hr ft 2--F)LMTD Correction Factor 0.002732 1,891.5 497.6 15,431.0 0.9813** Reynolds Number Outside Range of Equation Applicability 1! With Minimum Fouling The Test Heat Load Could Not Be Achie 22:01:26 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIX-0000)

Commonwealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.CSCS=60 0 F 06/26/98 Calculation Specitications 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 (OF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (OF)Shell Inlet Temp (fF)255.0 1,064.5 60.0 190.0 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.°F)Tube-Side hi (BTU/hr-ft 2.0 F)Heat Transferred (BTU/hr) 1/Wall Resis (BTU/hr-ft 2.OF)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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell (OF)Bulk Visc (Ibm/ft hr) Shell Skin Temp (OF)Skin Visc (Ibm/ft-hr)

Tube Temp In (OF)Density (Ibrn/ft 3) Tube Temp Out (OF)Cp (BTU/lbm 0'F) Tav Tube (OF)K (BTU/hr-ft-°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)Property Shell-Side Velocity (ft/s) 5.58 Reynold's Number 7.731 E+04 Prandtl Number 2.13 Bulk Visc (lbm/ft-hr) 0.82 Skin Visc (lbm/ft-hr) 0.87 Density (Ibm/ft')

60.52 Cp (BTU/lbm-°F) 1.00 K (BTU/hr-ft'°F) 0.39 5.325E+5 1.276E+5 7.8E+6 90.1 468.2 Tube-Side 1.70 9.385E+03 5.09 1.83 1.29 62.11 1.00 0.36 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr-ft 2.-F)Tube-Side hi (BTUhr-ft 2-0 F)I/Wall Resis (BTU/hr-ft 2 z.F)LMTD Correction Factor 0.002732 1,891.6 583.3 15,431.0 0.9812 U Overall (BTU/hr-ft 2.°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (fF)Tube Temp In (OF)Tube Temp Out (°F)Tav Tube (OF)Tube Skin Temp (OF)Proto-Power Calc: 97-197

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E Rev: A Page 6 of 10 188.5 190.0 175.4 182.7 173.5 60.0 121.2 90.6 125.0** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 21:59:26 PROTO-HX 3.02 by Proto-Power Corporation (SN#IIPHX-0000)

Commonwealth Edison Calculation Report for DGO1B -LSCS -HPCS DG Hx.CSCS=70OF 06/26/98 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 (IF)Shell Temp Out (IF)Tube Flow (gpm)Tube Temp In (°F)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (°F)Shell Inlet Temp (IF)298.7 1,064.5 70.0 190.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr.ft 2.°F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hr.ft 2-OF)Tube-Side hi (BTU/hr-ft 2.°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.°F/BTU)Property Shell-Side Tube-Side Velocity (ft/s) Shell Temp In (OF)Reynold's Number Shell Temp Out (IF)Prandtl Number Tav Shell (IF)Bulk Visc (lbmr/ft-hr)

Shell Skin Temp (OF)Skin Visc (lbm/ft-hr)

Tube Temp In (IF)Density (lbm/ft) Tube Temp Out (IF)Cp (BTU/lbm.°F)

Tav Tube (IF)K (BTU/hr-ft.-F)

Tube Skin Temp (IF)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (Ibnmlhr)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 3)Cp (BTU/Ibm-°F)

K (BTU/hr-ft.°F)

Shell-Side 5.58 7.73 1E+04 2.13 0.82 0.87 60.52 1.00 0.39 5.325E+5 1.494E+5 7.8E+6 85.2 468.2 Tube-Side 2.00 I. 170E+04 4.75 1.72 1.28 62.04 1.00 0.36 U Overall (BTU/hr-ft 2-°F)Shell Temp In (IF)Shell Temp Out (°F)Tav Shell (IF)Shell Skin Temp (IF)Tube Temp In (°F)Tube Temp Out (IF)Tav Tube (IF)Tube Skin Temp (IF)Proto-Power Calc: 97-197

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E Rev: A Page 7 of 10 199.1 190.0 175.4 182.7 173.6 70.0 122.2 96.1 125.4 Overall Fouling (hr'ft 2 0-F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr-ft 2.°F)I/Wall Resis (BTU/hr-ft 2-°F)LMTD Correction Factor 0.002732 1,891.7 680.9 15,431.0 0.9821** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 21:55:33 PROTO-IIX 3.02 by Proto-Power Corporation (SN#PHX-0000)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.CSCS=80°F 06/26/98 Calculation Specifications 1I[I i 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 (OF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (fF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (°F)Shell Inlet Temp (°F)362.9 1,064.5 80.0 190.0 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-ft 2 0-F)Tube-Side hi (BTU/hr-ft 2.0 F)Heat Transferred (BTU/hr) l/Wall Resis (BTU/hr ft 2.°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 (OF)Reynold's Number Shell Temp Out (°F)Prandtl Number Tav Shell (°F)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (OF)Skin Visc (lbm/ft-hr)

Tube Temp In (°F)Density (lbm/ft 3) Tube Temp Out (°F)Cp (BTU/Ibm-°F)

Tav Tube (OF)K (BTU/hr-ft.°F)

Tube Skin Temp (°F)Extrapolation Calculation Results Shell Mass Flow (lbm/hr)Tube Mass Flow (Ibm/hr)Heat Transferred (BTU/hr)LMTD Effective Area (ft 2)Property Shell-Side Velocity (ft/s) 5.58 Reynold's Number 7.731 E+04 Prandtl Number 2.13 Bulk Visc (lbm/ft-hr) 0.82 Skin Visc (Ibm/ft-hr) 0.87 Density (lbmift')

60.52 Cp (BTU/lbm-°F) 1.00 K (BTU/hr.ft.°F) 0.39 5.325E+5 1.815E+5 7.8E+6 80.4 468.2 Tube-Side 2.43 1.507E+04 4.45 1.62 1.28 61.98 1.00 0.36 Overall Fouling (hr-ft 2.°F/BTU)Shell-Side ho (BTU/hr ft 2-OF)Tube-Side hi (BTU/hr-ft 2.°F)I/Wall Resis (BTU/hr-ft 2-°F)LMTD Correction Factor 0.002732 1,891.8 814.6 15,431.0 0.9835 U Overall (BTU/hr-ft 2'°F)Shell Temp In (7F)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (`F)Tube Temp In (°F)Tube Temp Out (OF)Tav Tube (°F)Tube Skin Temp ('F)Proto-Power Calc: 97-197

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E Rev: A Page 8 of 10 210.8 190.0 175.4 182.7 173.6 80.0 123.0 101.5 125.8** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 21:48:46 PROTO-HX 3.02 by Proto-Power Corporation (SN#PIX-0000)

Commonwealth Edison Calculation Report for DGOIB -LSCS -HPCS DG Hx.CSCS=90OF 06/26/98 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 Shell Flow (gpm)Shell Temp In (IF)Shell Temp Out (°F)Tube Flow (gpm)Tube Temp In (°F)Tube Temp Out (IF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (IF)Shell Inlet Temp (°F)464.2 1,064.5 90.0 190.0 Fouling Calculation Results Shell Mass Flow (Ibm/hr) U Overall (BTU/hr-ft 2.°F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hrbft 2-°F)Tube-Side hi (BTU/hr-ft 2.°F)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr.ft 2-OF)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 (OF)Prandtl Number Tav Shell (°F)Bulk Visc (lbm/ft-hr)

Shell Skin Temp (OF)Skin Visc (Ibm/ft-hr)

Tube Temp In (°F)Density (lbm/ft3)

Tube Temp Out (OF)Cp (BTU/lbm.°F)

Tav Tube (OF)K (BTU/hr'ft-°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)5.325E+5 2.322E+5 Overall Fouling (hr-ft 2 0.F/BTU)Shell-Side ho (BTU/hr-ft 2.°F)Tube-Side hi (BTU/hr.ft 2.°F)I/Wall Resis (BTU/hr.ft 2.°F)LMTD Correction Factor 0.002732 1,892.0 1,014.2 15,431.0 0.9855 7.8E+6 75.5 468.2 Property Velocity (ft/s)Reynold's Number Prandtl Number Bulk Visc (lbm/fthr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm.°F)

K (BTU/hr.ft.°F)

Shell-Side 5.58 7.73 1E+04 2.13 0.82 0.87 60.52 1.00 0.39 Tube-Side 3.11 2.037E+04 4.19 1.53 1.27 61.90 1.00 0.37 U Overall (BTU/hr-ft 2-°F)Shell Temp In (IF)Shell Temp Out (°F)Tav Shell (°F)Shell Skin Temp (OF)Tube Temp In (IF)Tube Temp Out (OF)Tav Tube (IF)Tube Skin Temp (°F)Proto-Power Calc: 97-197

Attachment:

E Rev: A Page 9 of 10 224.0 190.0 175.4 182.7 173.7 90.0 123.6 106.8 126.2** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie 21:40:56 PROTO-HX 3.02 by Proto-Power Corporation (SNIPHX-0000)

Commonwealth Edison Calculation Report for DG01B -LSCS -HPCS DG Hx.CSCS= I 00°F 06/26/98 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 (fF)Shell Temp Out (OF)Tube Flow (gpm)Tube Temp In (OF)Tube Temp Out (OF)Extrapolation Data Tube Flow (gpm)Shell Flow (gpm)Tube Inlet Temp (OF)Shell Inlet Temp (OF)646.1 1,064.5 100.0 190.0 Fouling Calculation Results Shell Mass Flow (lbm/hr) U Overall (BTU/hr-ft 2-°F)Tube Mass Flow (lbm/hr) Shell-Side ho (BTU/hrtft 2.°F)Tube-Side hi (BTU/hr'ft 2-OF)Heat Transferred (BTU/hr) I/Wall Resis (BTU/hr-f 2-0 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 (OF)Reynold's Number Shell Temp Out (OF)Prandtl Number Tav Shell ('F)Bulk Vise (lbm/ft-hr)

Shell Skin Temp ('F)Skin Visc (lbm/ft.hr)

Tube Temp In (OF)Density (lbm/ft 3) Tube Temp Out (OF)Cp (BTU/Ibm'°F)

Tav Tube (OF)K (BTU/hr-ft-0 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)Property Shell-Side Velocity (ft/s) 5.58 Reynold's Number 7.731 E+04 Prandtl Number 2.13 Bulk Visc (lbm/ft-hr) 0.82 Skin Vise (lbm/ft hr) 0.87 Density (Ibm/ft 3) 60.52 Cp (BTU/Ibm.°F) 1.00 K (BTU/hr-ft-°F) 0.39 5.325E+5 3.232E+5 7.80 1E+6 70.5 468.2 Overall Fouling (hr'fta'F/BTU)

Shell-Side ho (BTU/hr-ft 2-°F)Tube-Side hi (BTU/hr-ft 2-°F)I/Wall Resis (BTU/hr-ft 2..F)LMTD Correction Factor 0.002732 1,892.1 1,349.8 15,431.0 0.9881 Tube-Side 4.33 2.991 E+04 3.95 1.45 1.27 61.83 1.00 0.37 U Overall (BTU/hr-ft 2.°F)Shell Temp In (OF)Shell Temp Out (OF)Tav Shell (OF)Shell Skin Temp (fF)Tube Temp In (OF)Tube Temp Out (°F)Tav Tube (OF)Tube Skin Temp (OF)Proto-Power Calc: 97-197

Attachment:

E Rev: A Page 10 of 10 239.2 190.0 175.4 182.7 173.8 100.0 124.2 112.1 126.5** Reynolds Number Outside Range of Equation Applicability With Minimum Fouling The Test Heat Load Could Not Be Achie Attachment F to Proto-Power Calculation 97-197 Revision A Proto-Power Calc: 97-197

Attachment:

F Rev: A Page 1 of 2 PROTO-HX T M Version 3.02 MODEL LASALLE STATION HPCS DIESEL GENERATOR HEAT EXCHANGER.

FILE NAME: DGO1B.PHX DATE LAST MODIFIED:

6/26/98 TIME LAST MODIFIED:

11:25:36 AM FILE SIZE: 864 KB Proto-Power Calc: 97-197

Attachment:

F Rev: A Page 2 of 2 CC-AA-309-1 001 Revision 6 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page 1 Design Analysis (Minor Revision)

Last Page No. ' Attachment C, C8 Analysis No.: 1 97-200 Revision:

2 A05 Title: I VY Cooler Thermal Performance Model -1 (2)VY01 A and 1(2)VY02A EClEGR No.: ' 388666 Revision:'

000 Station(s):

LaSalle Unit No.: 8 01 & 02 Safety/OA Class: ' SR System Code(s): ,0 VY is this Design Analysis Safeguards Information? " Yes [] No Z If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?

'2 Yes [] No Z If yes, ATI/AR#: N/A This Design Analysis SUPERCEDES:

,3 N/A in its entirety.Description of Changes (list affected pages): " This revision evaluates a maximum cooling water inlet temperature of 107 OF. The previous temperature that was evaluated was 104 OF. This revision also raises the maximum room temperature of the Southwest corner room to 153 °F. Affected pages are Pages 1 -3 and Attachment A, Pages Al-A8, Attachment B, Pages B1-B8, and Attachment C, Pages Cl-C8.Disposition of Changes: " See attached pages. The changes made are acceptable.

Preparer:" Ge4-nu 3&A ýz~Print Name Sign Name 0 te Method of Review: '1 Detailed Review t] Alternate Calculations E] Testing El Reviewer:" 6eV. C e _________-,._-___

-7//2-Print Name Sign Name Date Review Independent review EJ Peer review El Notes:" (For External Analyses Only)External Approver:

-/A Print Narme Sign Name Date Exelon Reviewer 2' AM Print Name Sion Name Date Exelon Approver:

22 IVA/ Si_/_r_ 7-___ .51_F_ /i Print Name 1V Sign Name I ate 97-200 Rev. A05 Page 2 of 3 Purpose: The purpose of this revision is to verify that the 1(2)VY01A and 1(2)VY02A coolers can remove the design heat load of 517,239 and 646,235 BTU/hr, respectively with a revised maximum cooling water temperature of 107 °F.Assumptions:

There are no assumptions for this revision.Inputs:* Cooling water temperature

= 107 OF (Reference 2)* Air temperature for 1(2)VY01A

= 148 OF (Reference 1)* Air temperature for 1(2)VY02A

= 153 OF** Water flow rate for 1(2)VY01 A = 75 gpm (Reference 1)* Water flow rate for 1(2)VY02A

= 108 gpm (References 1, 3, and 4)*** Air Flow rate for 1(2)VYO1A

= 17,100 cfm (Reference 1)* Air Flow rate for 1(2)VY02A

= 18,000 cfm (Reference 1)* Fouling factor for both coolers = 0.02832467 hrtft 2.°F/BTU (design fouling factor) (Reference 1)* 1 tube plugged for both coolers (5% tube plugging) (Reference 1)*153 OF was chosen to achieve the desired heat transfer rate for the VY02 room cooler. As long as the heat transfer rate of at least 646,235 BTU/hr is achieved, the room will stay < 153 OF. This temperature will be reflected in the EQ binders associated with the components in this room."*Note that an additional 50 gpm was allocated to the 1 (2)VY02A coolers per ECs 370853 and 384525. The results of the run with a 158 gpm flow rate on the water side is shown in Attachment C.S

References:

1. Design analysis97-200, Rev. A, up to and including Revs AO0 through A04 2. EC 388666, Rev. 000 3. EC 370853, Rev. 000 4. EC 384525, 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 EX00001 03.Method of Analysis I Numeric Analysis: The existing heat exchanger model will be revised by changing the input of the Tube Inlet Temp" from 104 OF to 107 °F. Because the fan for the 1(2)VY01A and 1(2)VY02A 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 17,100 cfm for the 1(2)VY01A cooler and 18,000 cfm for the 1(2)VY02A cooler. The iteration process is detailed in section 6.7 of revision A. The air flow values can be found on pages A8, B8, and C8 for each of the three cases considered.

Results I

Conclusions:

The 1(2)VY01A coolers can remove the design heat load of 517,239 BTU/hr with the following conditions:

0 107 OF cooling water temperature

148 OF air temperature

design fouling factor of 0.02832467 hrft 2.°F/BTU* 1 tube plugged* air flow rate of 17,100 cfm* water flow rate of 75 gpm 13 The total heat removed at these conditions is 560,505 BTU/hr, which provides 8.4% thermal margin over the design heat load. This thermal margin is enough to account for the 4.9% 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 97-200 Rev. A05 Page 3 of 3 4 for these heat exchangers.

The bounding fouling factor is the design fouling factor of 0.02832467 hr-ft 2.°F/BTU.This case is shown in Attachment A.The 1(2)VY02A coolers can remove the design heat load of 646,235 BTU/hr with the following conditions:

107 OF cooling water temperature

153 OF air temperature

design fouling factor of 0.02832467 hrft 2.OF/BTU* 1 tube plugged* air flow rate of 18,000 cfm* water flow rate of 108 gpm The total heat removed at these conditions is 681,320 BTU/hr, which provides 5.4% thermal margin over the design heat load. This thermal margin is enough to account for the 4.9% 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 0.02832467 hr-ft 2.-F/BTU.This case is shown in Attachment B.Additionally, a case was run for the 1(2)VY02A coolers with a water flow rate of 158 gpm. All other input parameters listed above remained the same. The total heat removed at these conditions is 701,741 BTU/hr, which provides 8.6% thermal margin over the design heat load. This case is shown in Attachment C. As stated above, this cooling water flow is to be implemented with ECs 370853 and 384525 for Units 1 & 2, respectively.

If this flow is to be used as the minimum equipment cooling water flow, an update to the UFSAR is required.The above 2 cases used a Southwest corner room (1(2)VY02A coolers) maximum temperature of 153 OF. The previously analyzed temperature was 150 OF. As stated above, 153 OF was chosen to achieve the desired heat transfer rate for the VY02 room cooler. As long as the heat transfer rate of at least 646,235 BTU/hr is achieved, the room temperature will stay < 153 OF. The EQ binders associated with the components in this room will be updated to qualify the components for this temperature.

Attachments:

A. Data Report for 1(2)VY01A (8 pgs)B. Data Report for 1(2)VY02A (8 pgs)C. Data Report for 1(2)VY02A w/ 158 gpm (8 pgs) 04-25-2012 14:13:19 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

ComEd -- LaSalle Data Report for 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYO1 -148 'F air side, 17,100 cfin, 107 'F water side, 75 gpm, Design FF, I tube plugged Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Flow 21,179.00 acfrn 150.00 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) 109.40 OF 115.30 OF Outlet Wet Bulb Temperature 84.10 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°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)

Fresh Water 0.001500 0.000000 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 19.00 0.5270 0.6250 1.500 1.452 97-200 1.000 Rev. A05 225.00 Attachment A Page Al of A8 04-25-2012 14:13:19 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

CornEd -- LaSalle Calculation Report for 1(2)VYOI A & 02A -CSCS Equipment Area Cooling Coils VY01 -148 0 F air side, 17,100 cfm, 107 0 F water side, 75 gpm, Design FF. I 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 tl Data Date Air Flow (acfm)Air Dry Bulb Temp In (0 F)Air Dry Bulb Temp Out (0 F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (0 F)Wet Bulb Temp Out ('F)Atmospheric Pressure (psia)Tube Flow (gpm)Tube Temp In (0 F)Tube Temp Out (0 F)Condensate Temperature (0 F)Extrapolation Data Tube Flow (gprn)Air Flow (acfm)Tube Inlet Temp (0 F)Air Inlet Temp (0 F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (0 F)Atmospheric Pressure (psia)75.00 18,098.00 107.00 148.00 12.76 0.00 14.315 97-200 Rev. A05 Attachment A Page A2 of A8 SAir Mass Velocity (Lbm/hr-ftZ), Tube Fluid Velocity (fl/see);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 14:13:19 PROTO--X 4.01 by Proto-Power Corporation (SN#PILX-1002)

Page 2 CornEd -- LaSalle Calculation Report for 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VYO1 -148 'F air side, 17,100 cfmi, 107 'F water side, 75 gpm, Design FF, I tube plugged Extrapolation Calculation Summary II Mass Flow (lbnm/hr)Inlet Temperature (IF)Outlet Temperature

(°F)Inlet Specific Humidity Outlet Specific Humidity Air-Side 66,878.21 148.00 114.50 Tube-Side 37,240.41 107.00 122.05 Tube-Side hi (BTU/hr.ft2-°F) 0.00 j Factor 0.0000 Air-Side ho (BTU/hr.ft 2.°F) 0.00 Tube Wall Resistance (hr.ft 2-°F/BTU) 0.00031430 Overall Fouling (hr- ft 2.°F/BTU) 0.02832467 U Overall (BTU/hr-ft 2-°F)Effective Area (t2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6,880.52 0.00 560,505 0.0000 560,505 11 Extrapolation Calculation for Row 1(Dry) I Air-Side Mass Flow (lbm/hr) 66,878.21 Inlet Temperature (IF) 148.00 Outlet Temperature (IF) 141.17 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 144.58 Skin Temperature (IF) 126.85 Velocity *** 3,364.26 Reynold's Number 793*Prandtl Number 0.7254 Bulk Visc (lbm/ft-hr) 0.0490 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0623 Cp (BTU/Ibm.°F) 0.2402 K (BTU/hr-ft.°F) 0.0162 Relative Humidity In (%) 12.76 Relative Humidity Out (%) 15.16 Tube-Side 37,240.41 118.98 122.05 120.5178 123.0132 2.9125 21,205 3.6151 1.3399 1.3091 61.7036 0.9988 0.3702 Tube-Side hi (BTU/hr. ft 2-F) 1,013.40 j Factor 0.0082 Air-Side ho (BTU/hr.ft 2.0 F) 8.22 Tube Wall Resistance (hr.ft 2-°F/BTU) 0.00031430 Overall Fouling (hr-ft2-°F/BTU)

0.0 2832467

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)5.56 860.06 23.88 114,284 0.9188 114,284 I-6 4* Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment A Page A3 of A8*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 14:13:19 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 3 CornEd -- LaSalle Calculation Report for 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYOI -148 'F air side, 17,100 cfm, 107 'F water side. 75 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 2(Dry)II Air-Side Mass Flow (ibm/hr) 66,878.21 Inlet Temperature (OF) 141.17 Outlet Temperature (OF) 135.35 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (OF) 138.26 Skin Temperature (IF) 123.10 Velocity *** 3,364.26 Reynold's Number 799**Prandtl Number 0.7260 Bulk Visc (lbm/ftRhr) 0.0486 Skin Visc (Ibm/Rf hr) 0.0000 Density (lbm/ft 3) 0.0629 Cp (BTU/lbm-°F) 0.2402 K (BTU/hr.ft.F) 0.0161 Relative Humidity In (%) 15.16 Relative Humidity Out (%) 17.62 Tube-Side 37,240.41 116.36 118.98 117.6724 119.8303 2.9105 20,641 3.7235 1.3765 1.3486 61.7474 0.9988 0.3692 Tube-Side hi (BTU/hr.ft 2-°F) 998.60 j Factor 0.0082 Air-Side ho (BTU/hr.ft 2.°F) 8.19 Tube Wall Resistance (hr-ft 2-°F/BTU) 0.00031430 Overall Fouling (hr-ft 2°F/BTU) 0.02832467 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)5.54 860.06 20.43 97,394 0.9190 97,394** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)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 (Ibm/itfhr)

Skin Visc (lbm/ftrhr)

Density (lbm/ft 3)Cp (BTU/Ibm.°F)

K (BTU/hr-ft.°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 66,878.21 135.35 130.38 0.020268 0.020268 132.86 119.90 3,364.26 805*4 0.7264 0.0483 0.0000 0.0634 0.2402 0.0160 17.62 20.10 Tube-Side 37,240.41 114.13 116.36 115.2463 117.1108 2.9087 20,164 3.8202 1.4091 1.3839 61.7839 0.9988 0.3684 Tube-Side hi (BTU/hr-ft 2.-F) 985.92 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2.°F) 8.17 Tube Wall Resistance (hr-ft 2.°F/BTU) 0.00031430 Overall Fouling (hr.ft 2.°F/BTU) 0.02832467 U Overall (BTU/hr-ft2.1F)

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)5.53 860.06 17.48 83,087 0.9192 83,087** Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment A Page A4 of A8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T. Other Properties at Average T 04-25-2012 14:13:19 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 4 ComEd -- LaSalle Calculation Report for 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYO0 -148 'F air side, 17,100 cfm, 107 'F water side, 75 gpm, Design FF, 1 tube plugged Extrapolation Calculation for Row 4(Dry)II i. _ _ _ _Air-Side Mass Flow (lbm/hr) 66,878.21 Inlet Temperature (OF) 130.38 Outlet Temperature (IF) 126.14 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 128.26 Skin Temperature (IF) 117.17 Velocity *** 3,364.26 Reynold's Number 810**Prandtl Number 0.7268 Bulk Visc (Ibm/f hr) 0.0480 Skin Vise (Ibm/ft hr) 0.0000 Density (lbm/ft 3) 0.0639 Cp (BTU/Ibm.°F) 0.2402 K (BTU/hr-ti.°F) 0.0159 Relative Humidity In (%) 20.10 Relative Humidity Out (%) 22.52 Tube-Side 37,240.41 112.22 114.13 113.1757 114.7854 2.9073 19,760 3.9061 1.4379 1.4154 61.8144 0.9988 0.3677 Tube-Side hi (BTU/hr-ft 2-°F) 975.07 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2-°F) 8.15 Tube Wall Resistance (hr.ft 2-°F/BTU) 0.00031430 Overall Fouling (hr.ft 2-°F/BTU) 0.02832467 U Overall (BTU/hr-ft 2.°F)Effective Area (ftR)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.51 860.06 14.97 70,945 0.9194 70,945** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(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 (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm.0 F)K (BTU/hr-ft-°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 66,878.21 126.14 122.52 0.020268 0.020268 124.33 114.83 3,364.26 814**0.7271 0.0478 0.0000 0.0643 0.2402 0.0158 22.52 24.87 Tube-Side 37,240.41 110.59 112.22 111.4071 112.7959 2.9061 19,417 3.9819 1.4633 1.4433 61.8400 0.9988 0.3670 Tube-Side hi (BTU/hr-ft 2-°F) 965.76 j Factor 0.0081 Air-Side ho (BTU/hr.ft 2-°F) 8.13 Tube Wall Resistance (hr-ft 2.°F/BTU) 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 U Overall (BTU/hrft 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)5.50 860.06 12.82 60,626 0.9196 60,626** Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment A Page A5 of A8*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ftlsec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 14:13:19 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 5 ComEd -- LaSalle Calculation Report for I(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VYOI -148 IF air side, 17,100 cfm, 107 IF water side, 75 gpm, Design FF, 1 tube plugged Extrapolation Calculation for Row 6(Dry)II I -- _Air-Side Mass Flow (lbm/hr) 66,878.21 Inlet Temperature

(°F) 122.52 Outlet Temperature (OF) 119.42 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 120.97 Skin Temperature (OF) 112.83 Velocity *** 3,364.26 Reynold's Number 818**Prandtl Number 0.7273 Bulk Visc (lbm/fthr) 0.0475 Skin Visc (lbm/fthr) 0.0000 Density (lbm/ft 3) 0.0646 Cp (BTU/Ibm 0'F) 0.2402 K (BTU/hr-ft 0'F) 0.0 157 Relative Humidity In (%) 24.87 Relative Humidity Out (%) 27.10 Tube-Side 37,240.41 109.20 110.59 109.8952 111.0927 2.9051 19,126 4.0486 1.4856 1.4679 61.8615 0.9988 0.3665 Tube-Side hi (BTU/hr-ft 2.°F) 957.79 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.°F) 8.12 Tube Wall Resistance (hr-ft 2.°F/BTU) 0.00031430 Overall Fouling (hr-ft 2"°F/BTU) 0.02832467 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)5.49 860.06 10.99 51,842 0.9197 51,842** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)Mass Flow (Ibm/hr)Inlet Temperature (IF)Outlet Temperature

(°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 (Ibmr/t.hr)

Density (lbm/ft 3)Cp (BTU/Ibm.0 F)K (BTU/hrift.°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 66,878.21 119.42 116.77 0.020268 0.020268 118.09 111.12 3,364.26 821**0.7275 0.0474 0.0000 0.0649 0.2402 0.0156 27.10 29.18 Tube-Side 37,240.41 108.01 109.20 108.6021 109.6340 2.9042 18,878 4.1072 1.5051 1.4895 61.8797 0.9988 0.3660 Tube-Side hi (BTU/hr-ft 2-°F) 950.95 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2-IF) 8.11 Tube Wall Resistance (hr-ft 2.°F/BTU) 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.48 860.06 9.42 44,357 0.9198 44,357* Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment A Page A6 of A8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ftlsec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 14:13:19 PROTO-HX 4.01 by Proto-Power Corporation (SN#PILX-1002)

Page 6 ComEd -- LaSalle Calculation Report for 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYOI -148 'F air side, 17,100 cfm, 107 'F water side, 75 gpm, Design FF, 1 tube plugged., Extrapolation Calculation for Row 8(Dry)II Air-Side Mass Flow (lbm/hr) 66,878.21 Inlet Temperature (0 F) 116.77 Outlet Temperature

('F) 114.50 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (0 F) 115.63 Skin Temperature

('F) 109.66 Velocity *** 3,364.26 Reynold's Number 824**Prandtl Number 0.7277 Bulk Visc (lbm/ft-hr) 0.0472 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0652 Cp (BTU/Ibm.°F) 0.2402 K (BTU/hr'ft-°F) 0.0156 Relative Humidity In (%) 29.18 Relative Humidity Out (%) 31.12 Tube-Side 37,240.41 106.99 108.01 107.4955 108.3843 2.9035 18,666 4.1584 1.5221 1.5084 61.8950 0.9989 0.3656 Tube-Side hi (BTU/hr-ft 2.°F)j Factor Air-Side ho (BTU/hr-ft 2 1-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 (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)945.09 0.0081 8.09 0.00031430

0.0 2832467

5.47 860.06 8.08 37,971 0.9199 37,971** Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment A Page A7 of A8* Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (fi/sec);

Air Density at Inlet T, Other Properties at Average T Formuilas~

from Section 6.7 for iteration orocess to determine inlet airflow for extranolation conditions Total.......

................

...."r. ..

--...- --.......

..... ........._Total P: P = 14.3151psia Dry Bulb T OUT: T1 114.51 F Specific Hum.: w = 0.0202 H20 Vap. P: Pv = (W*Rv*P)/(Ra+(W*Rv))

= 0.450285048 psia iRv = 8 5.7 7 8 1 (ft-lbf)/(Ibm-R)

__II Ra = 53.3521 (ft-lbf)/(Ibm-R)

Dry Air P: Pa = P -Pv =1 _ 13.8647151 psia Dry Air rho OUT: rho.out = (144/Ra)*(Pa/(459.67+T1))

=__ 0.065175 Ibm/ftA3 Dry Air rho IN: rho.in = (144/Ra)*(Pa/(459.67+T2))

= I 0.061582 Ibm/ftA3 Dry Bulb T IN: T2I 148 F Outlet Air Flow: V = 17100] cfrn cfm.in cfm.in = V*(rho.out/rho.in

= 1 18097.70 acfm 97-200 Rev. A05 Attachment A Page A8 of A8 04-25-2012 13:51:45 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

ComEd -- LaSalle Data Report for 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cfm, 107 TF water side, 108 gpm, Design FF, 1 tube plugged Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Flow 21,179.00 acfm 150.00 gpm Mass Flow 0.00 Ibm/hr 0.00 Ibm/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) 109.40 OF 115.30 OF Outlet Wet Bulb Temperature 84.10 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-°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)

Fresh Water 0.001500 0.000000 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 19.00 0.5270 0.6250 1.500 1.452 1.000 225.00 97-200 Rev. A05 Attachment B Page B1 of B8 04-25-2012 13:51:45 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

ComEd -- LaSalle Calculation Report for l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cfm, 107 'F water side, 108 gpm, Design FF, I tube plugged Page 1~1.11 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 (acfin)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 ('F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp ('F)Atmospheric Pressure (psia)108.00 19,212.00 107.00 153.00 12.76 0.00 14.315 97-200 Rev. A05 Attachment B Page B2 of B8 Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 13:51:45 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 2 ComEd -- LaSalle Calculation Report for l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cfrm, 107 'F water side, 108 gpm, Design FF, 1 tube plugged Extrapolation Calculation Summary 11 I.Air-Side Mass Flow (Ibm/hr) 70,113.67 Inlet Temperature (0 F) 153.00 Outlet Temperature (0 F) 114.36 Inlet Specific Humidity Outlet Specific Humidity Tube-Side 53,626.19 107.00 119.71 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-.F/BTU) 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 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)6,880.52 0.00 681,320 0.0000 681,320 Extrapolation Calculation for Row l(Dry)Mass Flow (lbm/hr)Inlet Temperature (fF)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/frhr)

Density (lbm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr-ft.°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,113.67 153.00 144.40 0.023032 0.023032 148.70 125.88 3,527.02 827**0.7250 0.0493 0.0000 0.0617 0.2402 0.0163 12.76 15.80 Tube-Side 53,626.19 116.88 119.71 118.2967 120.7965 4.1917 29,901 3.6993 1.3683 1.3364 61.7379 0.9988 0.3695 Tube-Side hi (BTU/hr ft 2.°F) 1,341.67 j Factor 0.0081 Air-Side ho (BTU/hr.ft 2-°F) 8.49 Tube Wall Resistance (hr.ft 2-°F/BTU) 0.00031430 Overall Fouling (hr.ft 2-°F/BTU) 0.02832467 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)5.84 860.06 30.19 151,661 0.9164 151,661** Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment B Page B3 of B8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (fl/sec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 13:51:45 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 3 ComEd -- LaSalle Calculation Report for I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cfm, 107 'F water side, 108 gpm, Design FF, 1 tube plugged Extrapolation Calculation for Row 2(Dry)11 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/f hr)Skin Visc (Ibm/f-ihr)

Density (lbm/ft 3)Cp (BTU/Ibm.0 F)K (BTU/hr-ft.°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,113.67 144.40 137.31 0.023032 0.023032 140.86 121.99 3,527.02 835**0.7258 0.0488 0.0000 0.0624 0.2402 0.0162 15.80 18.94 Tube-Side 53,626.19 114.55 116.88 115.7147 117.8022 4.1891 29,168 3.8012 1.4027 1.3748 61.7769 0.9988 0.3686 Tube-Side hi (BTU/hr.ft 2.°F) 1,323.45 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.°F) 8.46 Tube Wall Resistance (hr-ft 2-°F/BTU) 0.00031430 Overall Fouling (hr-ft2-'F/BTU)

0.0 2832467

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)5.82 860.06 24.96 124,935 0.9167 124,935 Reynolds Number Outside Range of Equation Applicability I1 Extrapolation Calculation for Row 3(Dry)Air-Side Mass Flow (Ibm/hr) 70,113.67 Inlet Temperature (IF) 137.31 Outlet Temperature (IF) 131.47 Inlet Specific Humidity 0.023032 Outlet Specific Humidity 0.023032 Average Temp (IF) 134.39 Skin Temperature (IF) 118.78 Velocity *** 3,527.02 Reynold's Number 842**Prandtl Number 0.7263 Bulk Visc (lbm/ft-hr) 0.0484 Skin Visc (lbm/ftihr) 0.0000 Density (lbm/ft 3) 0.0630 Cp (BTU/Ibm-°F) 0.2402 K (BTU/hr.ft-.F) 0.0160 Relative Humidity In (%) 18.94 Relative Humidity Out (%) 22.09 Tube-Side 53,626.19 112.62 114.55 113.5865 115.3281 4.1869 28,569 3.8888 1.4321 1.4080 61.8084 0.9988 0.3678 Tube-Side hi (BTU/hr ft 2-°F) 1,308.37 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2-°F) 8.43 Tube Wall Resistance (hr-ft 2'.F/BTU) 0.00031430 Overall Fouling (hr.ft2-°F/BTU)

0.0 2832467

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)5.80 860.06 20.66 103,055 0.9169 103,055 61"** Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment B Page B4 of B8*** Air Mass Velocity (Lbm/hr-ft'), Tube Fluid Velocity (ftlsec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 13:51:45 PROTO-ILX 4.01 by Proto-Power Corporation (SN#P-LX-1002)

Page 4 CornEd -- LaSalle Calculation Report for I(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 *F air side, 18,000 cfm, 107 'F water side, 108 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 4(Dry)11 L 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/ffthr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm-'F)

K (BTU/hr-ftf'F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,113.67 131.47 126.64 0.023032 0.023032 129.06 116.14 3,527.02 848*" 0.7268 0.0481 0.0000 0.0636 0.2402 0.0159 22.09 25.14 Tube-Side 53,626.19 111.04 112.62 111.8301 113.2821 4.1852 28,078 3.9635 1.4571 1.4364 61.8339 0.9988 0.3672 Tube-Side hi (BTU/hr-ft 2-°F) 1,295.89 j Factor 0.0080 Air-Side ho (BTU/hr-ftf 2.F) 8.41 Tube Wall Resistance (hr-ft 2.°F/BTU) 0.00031430 Overall Fouling (hr-ft2-°F/BTU)

0.0 2832467

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)5.78 860.06 17.11 85,102 0.9171 85,102** Reynolds Number Outside Range of Equation Applicability 11 Extrapolation Calculation for Row 5(Dry) 1 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 (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm-°F)

K (BTU/hr--.fF)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,113.67 126.64 122.66 0.023032 0.023032 124.65 113.95 3,527.02 853**0.7271 0.0478 0.0000 0.0640 0.2402 0.0158 25.14 28.03 Tube-Side 53,626.19 109.72 111.04 110.3790 111.5888 4.1838 27,675 4.0271 1.4784 1.4606 61.8546 0.9988 0.3667 Tube-Side hi (BTU/hr-ft 2.°F) 1,285.54 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2 l-F) 8.39 Tube Wall Resistance (hr-ft 2.°F/BTU) 0.00031430 Overall Fouling (hr.ft 2.0 F/BTU) 0.02832467 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)5.77 860.06 14.17 70,341 0.9173 70,341-** Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment B Page B5 of B8*** Air Mass Velocity (Lbm/hr-ft), Tube Fluid Velocity (fi/sec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 13:51:45 PROTO-H-X 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 5 ComEd -- LaSalle Calculation Report for 1(2)VYO0A

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cftm, 107 'F water side, 108 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 6(Dry)I'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/tt-hr)

Skin Visc (lbm/ft-hr)

Density (Ibm/ft)Cp (BTU/Ibm."F)

K (BTU/hr-ft-°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,113.67 122.66 119.36 0.023032 0.023032 121.01 112.14 3,527.02 857**0.7273 0.0475 0.0000 0.0644 0.2402 0.0157 28.03 30.71 Tube-Side 53,626.19 108.64 109.72 109.1793 110.1867 4.1826 27,343 4.0809 1.4963 1.4812 61.8716 0.9988 0.3662 Tube-Side hi (BTU/hr.ft 2.F) 1,276.97 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.F) 8.37 Tube Wall Resistance (hr-ft 2-°F/BTU) 0.00031430 Overall Fouling (hr-ft2-°F/BTU)

0.0 2832467

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)5.76 860.06 11.74 58,184 0.9174 58,184*Reynolds Number Outside Range of Equation Applicability II Extrapolation Calculation for Row 7(Dry) 1 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 (1bm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr-ft.°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,113.67 119.36 116.63 0.023032 0.023032 117.99 110.64 3,527.02 861*0.7275 0.0474 0.0000 0.0647 0.2402 0.0156 30.71 33.15 Tube-Side 53,626.19 107.74 108.64 108.1866 109.0251 4.1817 27,069 4.1263 1.5115 1.4987 61.8854 0.9988 0.3659 Tube-Side hi (BTU/hr-ft 2.°F) 1,269.86 j Factor 0.0080 Air-Side ho (BTU/hr-ft2-°F) 8.36 Tube Wall Resistance (hr-ft 2.°F/BTU) 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.75 860.06 9.74 48,159 0.9175 48,159 I

Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment B Page B6 of B8*** Air Mass Velocity (Lbrr/hr-fi 2), Tube Fluid Velocity (f/sec); Air Density at Inlet T, Other Properties at Average T 04-25-2012 13:51:45 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 6 ComEd -- LaSalle Calculation Report for l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 OF air side, 18,000 cfm, 107 OF water side, 108 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 8(Dry)II 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 (Ibm/f hr)Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm.°F)

K (BTU/hr-ftf-F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,113.67 116.63 114.36 0.023032 0.023032 115.49 109.40 3,527.02 864**0.7277 0.0472 0.0000 0.0649 0.2402 0.0156 33.15 35.34 Tube-Side 53,626.19 106.99 107.74 107.3648 108.0624 4.1809 26,843 4.1645 1.5242 1.5134 61.8968 0.9989 0.3656 Tube-Side hi (BTU/hr-ft 2 -F) 1,263.97 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.0 F) 8.35 Tube Wall Resistance (hr ft 2.°F/BTU) 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.74 860.06 8.07 39,883 0.9176 39,883** Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment B Page B7 of B8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (fi/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: P = 14.3151psia Dry Bulb T OUT: T1 = 114.36 F Specific Hum.: W = 0.023 H20 Vap. P: Pv = (W*Rv*P)/(Ra+(W*Rv))

= 0.5104750421psia

_IRv = 85.7781 (ft-lbf)/(Ibm-R)

_Ra = 53.3521 (ft-lbf)/(Ibm-R)

Dry Air P: Pa = P -Pv = 13.804521 psia Dry Air rho OUT: rho.out = (144/Ra)*(Pa/(459.67+T1))

= 0.064908 libmIftA3 Dry Air rho IN: rho.in = (144/Ra)*(Pa/(459.67+T2))

= 0.060814 libm/ftA3 Dry Bulb T IN: T2 = 153F Outlet Air Flow: V = 18000cm cfm.in cfm.in = V*(rho.out/rho.in)

= 19211.64 acfm 97-200 Rev. A05 Attachment B Page B8 of B8 04-25-2012 14:00:59 PROTO-ILX 4.01 by Proto-Power Corporation (SN#PHX-1002)

ComEd -- LaSalle Data Report for l(2)VYOlA

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 TF air side, 18,000 cfm, 107 TF water side, 158 gpm, Design FF, I tube plugged I] Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Flow 21,179.00 acfrn 150.00 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) 109.40 OF 115.30 OF Outlet Wet Bulb Temperature 84.10 OF Outlet Relative Humidity 0.00 %Tube Fluid Name Tube-Side Fouling Air-Side Fouling Fresh Water 0.001500 0.000000 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-°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) 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 19.00 0.5270 0.6250 1.500 1.452 97-200 1.000 Rev. A05 225.00 Attachment C Page C1 of C8 04-25-2012 14:00:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

CornEd -- LaSalle Calculation Report for l(2)VYO0A

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cfm, 107 'F water side, 158 gpm, Design FF, I tube plugged Page 1 1~~II 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 (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 ('F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp ('F)Atmospheric Pressure (psia)158.00 19,248.00 107.00 153.00 12.76 0.00 14.315 97-200 Rev. A05 Attachment C Page C2 of C8* Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 14:00:59 PROTO-HLX 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 2 ComEd -- LaSalle Calculation Report for I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cfrn, 107 'F water side, 158 gpMr Design FF. I tube plugged ,,I II Extrapolation Calculation Summary 11 Mass Flow (Ibm/hr)Inlet Temperature (fF)Outlet Temperature

(°F)Inlet Specific Humidity Outlet Specific Humidity Air-Side 70,245.05 153.00 113.28 Tube-Side 78,453.13 107.00 115.98 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 2.0 F/BTU) 0.00031430 Overall Fouling (hr.ft 2.F/BTU) 0.02832467 U Overall (BTU/hr.ft 2"F)Effective Area (it 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6,880.52 0.00 701,741 0.0000 701,741 Extrapolation Calculation for Row l(Dry)Air-Side Mass Flow (lbm/hr) 70,245.05 Inlet Temperature (0 F) 153.00 Outlet Temperature (0 F) 143.40 Inlet Specific Humidity 0.023032 Outlet Specific Humidity 0.023032 Average Temp (0 F) 148.20 Skin Temperature (0 F) 122.69 Velocity *** 3,533.63 Reynold's Number 829*1 Prandtl Number 0.7251 Bulk Visc (Ibm/ft hr) 0.0492 Skin Visc (Ibm/ft hr) 0.0000 Density (lbm/ft 3) 0.0618 Cp (BTU/Ibm.0 F) 0.2402 K (BTU/hr-ift-F) 0.0163 Relative Humidity In (%) 12.76 Relative Humidity Out (%) 16.21 Tube-Side 78,453.13 113.82 115.98 114.9014 117.0014 6.1272 42,337 3.8343 1.4138 1.3854 61.7890 0.9988 0.3683 Tube-Side hi (BTU/hr-ft2-°F) 1,786.84 j Factor 0.0081 Air-Side ho (BTU/hr.ft 2-°F) 8.50 Tube Wall Resistance (hr-ft 2-°F/BTU) 0.00031430 Overall Fouling (hr-ft2-°F/BTU)

0.0 2832467

U Overall (BTU/hrift2"°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)5.97 860.06 33.06 169,688 0.9163 169,688*

Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment C Page C3 of C8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 14:00:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 3 CornEd -- LaSalle Calculation Report for 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cfm, 107 'F water side, 158 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 2(Dry)II I.Air-Side Mass Flow (Ibm/hr) 70,245.05 Inlet Temperature (IF) 143.40 Outlet Temperature (IF) 135.75 Inlet Specific Humidity 0.023032 Outlet Specific Humidity 0.023032 Average Temp (IF) 139.57 Skin Temperature (IF) 119.18 Velocity *** 3,533.63 Reynold's Number 838**Prandtl Number 0.7259 Bulk Visc (lbm/ft-hr) 0.0487 Skin Visc (Ibm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0626 Cp (BTU/Ibm.0 F) 0.2402 K (BTU/hr.ft-°F) 0.0161 Relative Humidity In (%) 16.21 Relative Humidity Out (%) 19.73 Tube-Side 78,453.13 112.09 113.82 112.9565 114.6465 6.1244 41,538 3.9153 1.4410 1.4173 61.8176 0.9988 0.3676 Tube-Side hi (BTU/hr-ft 2.°F) 1,767.91 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.°F) 8.46 Tube Wall Resistance (hr-ft 2.°F/BTU) 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 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)5.95 860.06 26.43 135,127 0.9166 135,127** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry) I1 Mass Flow (lbm/hr)Inlet Temperature

(°F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (°F)Skin Temperature

(°F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftfhr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr-ft-°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,245.05 135.75 129.65 0.023032 0.023032 132.70 116.38 3,533.63 846**0.7265 0.0483 0.0000 0.0632 0.2402 0.0160 19.73 23.19 Tube-Side 78,453.13 110.72 112.09 111.4066 112.7661 6.1222 40,905 3.9819 1.4633 1.4437 61.8400 0.9988 0.3670 Tube-Side hi (BTU/hr-ft 2-°F) 1,752.78 j Factor 0.0080 Air-Side ho (BTU/hr ft 2-°F) 8.43 Tube Wall Resistance (hr-ft 2.°F/BTU) 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 U Overall (BTU/hr-tt2.°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)5.93 860.06 21.14 107,769 0.9169 107,769** Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment C Page C4 of C8*** Air Mass Velocity (Lbm/hr-ftV), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 14:00:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PILX-1002)

Page 4 ComEd -- LaSalle Calculation Report for 1(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cfm, 107 'F water side, 158 gpm, Design FF, 1 tube plugged Extrapolation Calculation for Row 4(Dry)II Air-Side Mass Flow (lbm/hr) 70,245.05 Inlet Temperature

("F) 129.65 Outlet Temperature

("F) 124.78 Inlet Specific Humidity 0.023032 Outlet Specific Humidity 0.023032 Average Temp ("F) 127.21 Skin Temperature

("F) 114.15 Velocity *** 3,533.63 Reynold's Number 852**Prandtl Number 0.7269 Bulk Vise (lbm/frhr) 0.0479 Skin Visc (Ibm/ft-hr) 0.0000 Density (Ibm/ft 3) 0.0638 Cp (BTU/Ibm'°F) 0.2402 K (BTU/hr.ft-°F) 0.0158 Relative Humidity In (%) 23.19 Relative Humidity Out (%) 26.45 Tube-Side 78,453.13 109.62 110.72 110.1699 111.2629 6.1204 40,403 4.0364 1.4815 1.4654 61.8576 0.9988 0.3666 Tube-Side hi (BTU/hr-ft 2-°F) 1,740.68 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2-"F) 8.41 Tube Wall Resistance (hr-ft 2-"F/BTU) 0.00031430 Overall Fouling (hr.ft2-'F/BTU)

0.0 2832467

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)5.91 860.06 16.92 86,054 0.9171 86,054** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)Air-Side Mass Flow (lbm/hr) 70,245.05 Inlet Temperature

("F) 124.78 Outlet Temperature

("F) 120.88 Inlet Specific Humidity 0.023032 Outlet Specific Humidity 0.023032 Average Temp ("F) 122.83 Skin Temperature

("F) 112.37 Velocity *** 3,533.63 Reynold's Number 857**Prandtl Number 0.7272 Bulk Visc (lbm/ft-hr) 0.0477 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0642 Cp (BTU/Ibm.°F) 0.2402 K (BTU/hr-ft.°F) 0.0157 Relative Humidity In (%) 26.45 Relative Humidity Out (%) 29.44 Tube-Side 78,453.13 108.74 109.62 109.1819 110.0604 6.1191 40,003 4.0807 1.4963 1.4831 61.8715 0.9988 0.3662 Tube-Side hi (BTU/hr-ft 2-'F) 1,730.99 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2 -F) 8.39 Tube Wall Resistance (hr.ft 2."F/BTU) 0.00031430 Overall Fouling (hr.ft2-.F/BTU)

0.0 2832467

U Overall (BTU/hr.ft2-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)5.90 860.06 13.55 68,781 0.9173 68,781 Q3, ** Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment C Page C5 of C8*** Air Mass Velocity (Lbm/hr'ft2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 14:00:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 5 CornEd -- LaSalle Calculation Report for 1(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cfmi, 107 'F water side, 158 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 6(Dry)II I.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/frhr)

Skin Visc (Ibm/ft hr)Density (lbm/ft 3)Cp (BTU/Ibm-'F)

K (BTU/hr-ft-°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,245.05 120.88 117.77 0.023032 0.023032 119.33 110.94 3,533.63 861**0.7275 0.0474 0.0000 0.0645 0.2402 0.0157 29.44 32.10 Tube-Side 78,453.13 108.04 108.74 108.3920 109.0979 6.1180 39,684 4.1168 1.5083 1.4976 61.8826 0.9988 0.3660 Tube-Side hi (BTU/hr-ft 2.°F) 1,723.23 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2-°F) 8.38 Tube Wall Resistance (hr-ft2-0 F/BTU) 0.00031430 Overall Fouling (hr.ft 2 l.F/BTU) 0.02832467 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)5.89 860.06 10.86 55,019 0.9174 55,019 (a ** Reynolds Number Outside Range of Equation Applicability I Extrapolation Calculation for Row 7(Dry) I 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/ft.hr)

Skin Visc (lbm/ft-hr)

Density (Ibm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr-f:-'F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,245.05 117.77 115.28 0.023032 0.023032 116.52 109.80 3,533.63 864**0.7276 0.0473 0.0000 0.0648 0.2402 0.0156 32.10 34.44 Tube-Side 78,453.13 107.48 108.04 107.7600 108.3270 6.1171 39,430 4.1460 1.5180 1.5093 61.8914 0.9989 0.3657 Tube-Side hi (BTU/hr.ft 2.°F) 1,717.01 j Factor 0.0080 Air-Side ho (BTU/hr'ft 2.°F) 8.36 Tube Wall Resistance (hr-ff 2.°F/BTU) 0.00031430 Overall Fouling (hrjft 2-°F/BTU) 0.02832467 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)5.88 860.06 8.70 44,037 0.9175 44,037*

Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment C Page C6 of C8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 04-25-2012 14:00:59 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-1002)

Page 6 ComEd -- LaSalle Calculation Report for 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY02 -153 'F air side, 18,000 cfm, 107 'F water side, 158 gpm, Design FF, I tube plugged Extrapolation Calculation for Row 8(Dry)'I I. 'I 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 (Ibm/ftihr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm.°F)

K (BTU/hr-ft-°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 70,245.05 115.28 113.28 0.023032 0.023032 114.28 108.89 3,533.63 867**0.7278 0.0471 0.0000 0.0650 0.2402 0.0156 34.44 36.45 Tube-Side 78,453.13 107.03 107.48 107.2540 107.7094 6.1164 39,226 4.1697 1.5259 1.5188 61.8983 0.9989 0.3655 Tube-Side hi (BTU/hr.ft 2.'F) 1,712.02 j Factor 0.0080 Air-Side ho (BTU/hr.ft 2.0 F) 8.35 Tube Wall Resistance (hr-ft 2.°F/BTU) 0.00031430 Overall Fouling (hr-ft 2.0 F/BTU) 0.02832467 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)5.88 860.06 6.98 35,265 0.9176 35,265** Reynolds Number Outside Range of Equation Applicability 97-200 Rev. A05 Attachment C Page C7 of C8*** Air Mass Velocity (Lbri/hr.ft2), Tube Fluid Velocity (fi/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: p = __ 14.315 psia Dry Bulb T OUT: T1 _ _ 113.28 F Specific Hum.: W = _ 0.023 H20 Vap. P: Pv (W*Rv*P)/(Ra+(W*Rv))

= _ 0.510475042 psia!Rv = 85.778 (ft-lbf)/(Ibm-R)

IRa = 53.352 (ft-lbf)/(Ibm-R)

Dry Air P: Pa = P -Pv1 13.80452 psia Dry Air rho OUT: rho.out = (144/Ra)*(Pa/(459.67+T1))

=_ 0.065030 lbm/ftA3 Dry Air rho IN: rho.in = (144/Ra)*(Pa/(459.67+T2))

= _ 0.060814 Ibm/ftA3 Dry Bulb T IN: T2 1 153 F Outlet Air Flow: V I 18000dcfm cfm.in cfm.in = V*(rho.out/rho.in)

= 19247.86 acfm 97-200 Rev. A05 Attachment C Page C8 of C8 CC-AA-309-1 001 Revision 6 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page 1 Design Analysis (Minor Revision)

Last Page No. 1 Analysis No.:'97-200 Revision:

I A04 Title: 3 VY Cooler Thermal Performance Model -1(2)VY01 A and 1(2)VY02A EC/ECR No.:' 384525 Revision:

5 000 Station(s):

' LaSalle Unit No.:; 02 Safety/QA Class: 9 SR System Code(s): '° HP, E22, DG, VY Is this Design Analysis Safeguards Information?" Yes [] No 0 If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?

'2 Yes [1 No 0 If yes, ATI/AR#: N/A This Design Analysis SUPERCEDES:

'3 N/A in its entirety.Description of Changes (list affected pages): " EC 384525 revised the flows in Division 3 of the Unit 2 CSCS. This revision makes the changes made in Revision A03 applicable to both Units.Disposition of Changes: I As shown in Attachment A of Revision A03, the changes made are acceptable.

The additional 50 gpm is acceptable.

No formal heat transfer analysis will be performed.

Preparer:" Sean Tanton L 3 2o/Print Name Sign Name De Method of Review: '7 Detailed Review 0 Alternate Calculations E] Testing E]Reviewer:"I Matthew Cosenza Name -.3t/7 1 Print Name 5gn PNaxeat Review Independent review 0 Peer review E]Notes: 89 (For External Analyses Only)External Approver:

20 N/A N/A N/A Print Name Sign Name Date Exelon Reviewer' N/A N/A N/A Print Name Sigln Name Date Exelon Approver:

22 Dan Schmit .2-Print Name I Sign Name Date CC-AA-309-1001 Revision 6 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page 1 Design Analysis (Minor Revision)

Last Page No.' 1 Analysis No.:'97-200 Revision:

' A03 Title: ' VY Cooler Thermal Performance Model -1(2)VYO1 A and 1 (2)VY02A EC/ECR No.:, 370853 Revision:

S 000 Station(s):'

LaSalle Unit No.: 01 SafetylOA Class:' SR System Code(s): " HP. E22, DG Is this Design Analysis Safeguards Information?" Yes O No 0 If yes, see SY-AA-101-106 Does this Design Analysis contain Unverified Assumptions?

' Yes r No 0 If yes, ATI/AR#: N/A This Design Analysis SUPERCEDES: " N/A in Its entirety.Description of Changes (list affected pages): " To recover available margin in Division III of the CSCS. EC 370853 revises the flows of the 1 VY02A cooler. To recover margin. 100 gpm will be diverted from the 1E22-SOO1 cooler. Of this 100 gpm. 50 gpm will be returned to the 1 E22-CO01 pump. while the other 50 gpm will be given to the 1 VY02A cooler. This minor revision documents the change in flow.Note that this analysis covers the 1(2)VY02A and the 1(2)VYOIA coolers. This revision only applies to Div. 3.Unit 1 (1VY02A cooler). The flows shown for the remaining coolers are not impacted by this revision.Disposition of Changes: The minimum flow required to remove the design heat load of 646.235 Btu/hr has not changed. Because the flow through the coolers is increasing by 50 gpm. the heat transfer will be greater and the previous scenarios that have been run in this calculation will remain bounding.

The increase in flow will not increase the velocity of the water through the tubes to a point that would exceed the limits established in ER-AA-340-2000.

Therefore.

the additional 50 gpm is acceptable., ~pt" ma" .... io Method of Review: " Detailed Review [] Alternate Calculation-r-1 Testing E]Reviewer." Matthew

":j_!l .Review Independent review 0 Peer review Notes: ý'(;:Cf External Approver:, N/A N/A WA Exelo NRwN N/A "WbcA Exelon Reviewer, NIA N/ANI Exelon Approver.

71 Dan Schmvit I CC-AA-309-1001 Revision 1 ATTACHMENT 2 Design Analysis Minor Revision Cover Sheet Page 1 of,0"~-f/ 4#- A Last Page No.Analysis No.97-200 Revision A02 EC/ECR No. 356225 a I- Revision 0 Title: VY Cooler Thermal Performance Model -1(2)VY01A and 1(2)VY02A Station(s)

LaSalle Is this Design Analysis Safeguards?

Yes [] No [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)VY01A coolers by 5%, and determines a new maximum fouling factor at this reduced air flow.The 1(2)VY02A coolers were not changed.Disposition of Changes (include additional pages as required)See attached sheets. The change is acceptable.

Preparer Terry Martin 7/6/05 Print Name Sign Name Date Reviewer Of Name Sign e Method of Review tled Review E- Alternate Calculati n E] Testing Review Notes:,. , Approver -7 C ___ _Print Name ign Name Date (For External Analyses Only)Exelon Reviewer Print Name Sign Name Date Approver Print Name Sign Name Date Purpose: The purpose of this minor revision is to revise the thermal model of the I(2)VYOIA 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 0.02832467 hr*ft 2*°F/BTU, 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 1 are still valid.

References:

1. Calculation No.97-200, Rev. A, "VY Cooler Thermal Performance Model -1(2)VYO1A and 1(2)VY02A." 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. The 5% reduction is calculated on the exit of the cooler. 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 517,239 BTU/hr for 1(2)VYO I A 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.

The current analyzed exit flow rate is taken from the 8 th row of the cooler (see Reference 1 Rev AOO Attachment B, page B8), which is 70,628.98 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 18,000 CFM. Reducing this number by 5% results in an exit flow rate of 17,100 CFM. Manipulation of the inlet flow rate was used until the exit flow rate is 17,100 CFM.When the Service Water inlet temperature is 104'F for the limiting flow rate of 75gpm, a design fouling factor of 0.02832467 hr*ft 2*OF/BTU, and a 5% tube plugging allowance, the new total heat transfer is 603,150 BTU/hr. The thermal margin is calculated as Apqo Qcalculated

-Qrequired, which is 603,150 -517,239 BTU/hr = 85,911 or 16.6% Gross Thermal Margin. Allowing for 5% model uncertainty, the net margin is 603,150(0.95)

-517,239 BTU/hr = 55,754 or 10.8% net Thermal Margin.The maximum fouling factor with the same assumptions as above and a 5% model uncertainty is 0.07593245 hr*ft 2*°F/BTU.Results /

Conclusion:

The 1 (2)VYO 1 A coolers were found to have adequate thermal margin for a maximum lake temperature of 104'F when operated at design fouling conditions (0.02832467 hr*ft 2*°F/BTU), a 5% tube plugging allowance, and a 5% reduction in air flow rate. The maximum fouling factor is 0.07593245 hr*ft 2*OF/BTU. A reduced air flow rate of 17,100 ACFM (95% of 18,000) 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)VYO1A (CSCS=I04'F

@ design fouling, 5% tube plugged, 5% reduction in flow)Attachment "B" -Proto-Hx Calc. Report for l(2)VYOIA (CSCS=104'F Max FF, 5% tube plugged, 5% reduction in flow)1 a *1 Is 06-09-2005 14:41:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Data Report for 1(2)VYOI A & 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, Design FF, 5% Plug, 5% Reduction in Flow 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.°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) 21,179.00 0.00 150.00 92.00 0.00 109.40 84.10 0.00 acfm Ibm/hr OF OF OF OF Tube-Side 150.00 0.00 105.00 gpm Ibm/hr OF 115.30 OF Fresh Water 0.001500 0.000000 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers O1A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 19.00 0.5270 0.6250 1.500 1.452 1.000 225.00 VA-KAb 06-09-2005 14:41:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY0I @ 104 F, Design FF, 5% Plug, 5% Reduction in Flow Page I-V 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 (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 (IF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm)Air Flow (acfm)Tube Inlet Temp (OF)Air Inlet Temp (IF)Inlet Relative Humidity (%)Inlet Wet Bulb Temp (IF)Atmospheric Pressure (psia)75.00 18,186.00 104.00 148.00 12.76 0.00 14.315 6f7-60 AC/o A (44 0*** Air Mass Velocity (Lbm/hr-l), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 06-09-2005 14:41:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

Page 2 ComEd -- LaSalle Calculation Report for l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY0 @ 104 F, Design FF, 5% Plug, 5% Reduction in Flow Extrapolation Calculation Summary II Mass Flow (lbm/hr)Inlet Temperature

(°F)Outlet Temperature

(°F)Inlet Specific Humidity Outlet Specific Humidity Air-Side 67,203.40 148.00 112.12 Tube-Side 37,264.79 104.00 120.20 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.°F/BTU,'

0.0 0031430

Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)6,880.52 0.00 603,150 0.0000 603,150 Extrapolation Calculation for Row l(Dry)Air-Side Mass Flow (lbm/hr) 67,203.40 Inlet Temperature (OF) 148.00 Outlet Temperature (OF) 140.70 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 144.35 Skin Temperature (OF) 125.37 Velocity *** 3.380.62 Reynold's Number 797**Prandtl Number 0.7255 Bulk Visc (lbm/ft-hr) 0.0490 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0623 Cp (BTU/Ibm.°F) 0.2402 K (BTU/hr-ff.°F) 0.0 162 Relative Humidity In (%) 12.76 Relative Humidity Out (%) 15.34 Tube-Side 37,264.79 116.90 120.20 118.5507 121.2532 2.9130 20,828 3.6895 1.3650 1.3307 61.7340 0.9988 0.3695 Tube-Side hi (BTU/hr-fti 2.F) 1,004.28 j Factor 0.0082 Air-Side ho (BTU/hr ft2. F) 8.24 Tube Wall Resistance (hr-ft 20.00031430 Overall Fouling (hr-ft 2-F/BTU) 0.02832467 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)5.57 860.06 25.60 122,664 0.9186 122,664 4 ** Reynolds Number Outside Range of Equation Applicability V-dot)4 Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (fi/sec);

Air Density at Inlet T, Other Properties at Average T 06-09-2005 14:41:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

Page 3 CornEd -- LaSalle Calculation Report for I(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VYOl @ 104 F. Design FF, 5% Plug, 5% Reduction in Flow Extrapolation Calculation for Row 2(Dry)Air-Side Tube-Side Mass Flow (lbm/hr) 67,203.40 37,264.79 Tube-Side hi (BTU/hr-ft 2.°F) 988.35 Inlet Temperature (0 F) 140.70 114.09 j Factor 0.0082 Outlet Temperature (0 F) 134.48 116.90 Air-Side ho (BTU/hr-ft 2.°F) 8.21 Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2'°F/BTU', 0.00031430 Outlet Specific Humidity 0.020268 Overall Fouling (hr-fl 2.°F/BTU) 0.02832467 Average Temp (°F) 137.59 115.4974 Skin Temperature

(°F) 121.35 117.8395 U Overall (BTU/hr'ft 2-0 F) 5.55 Velocity *** 3.380.62 2.9108 Effective Area (ft 2) 860.06 Reynold's Number 804** 20,226 LMTD 21.93 Prandtl Number 0.7261 3.8100 Total Heat Transferred (BTU/hr) 104,623 Bulk Visc (lbm/ft-hr) 0.0486 1.4056 Skin Visc (lbm/ftdhr) 0.0000 1.3743 Surface Effectiveness (Eta) 0.9188 Density (Ibm/fl 3) 0.0630 61.7801 Sensible Heat Transferred (BTU/hr) 104,623 Cp (BTU/1bm'°F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr'fr'°F) 0.0161 0.3685 Heat to Condensate (BTU/hr)Relative Humidity In (%) 15.34 Relative Humidity Out (%) 18.03** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)Air-Side Mass Flow (Ibm/hr) 67,203.40 Inlet Temperature (0 F) 134.48 Outlet Temperature

(°F) 129.17 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (7F) 131.82 Skin Temperature (7F) 117.92 Velocity *** 3.380.62 Reynold's Number 810**Prandtl Number 0.7265 Bulk Visc (lbm/ft-hr) 0.0482 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0636 Cp (BTU/Ibm'°F) 0.2402 K (BTU/hr'ft.

0 F) 0.0159 Relative Humidity In (%) 18.03 Relative Humidity Out (%) 20.76 Tube-Side 37,264.79 111.69 114.09 112.8918 114.9196 2.9090 19,718 3.9181 1.4419 1.4136 61.8185 0.9988 0.3676 Tube-Side hi (BTU/hr'ft 2-°F) 974.69 j Factor 0.0081 Air-Side ho (BTU/hrft2.°F) 8.19 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.53 860.06 18.79 89,336 0.9191 89,336*

Reynolds Number Outside Range of Equation Applicability q~-?ooIAv 4 Adl-14~,P4,_*** Air Mass Velocity (Lbrn/hrfi 2), Tube Fluid Velocity (ft/sec), Air Density at Inlet T, Other Properties at Average T 06-09-2005 14:41:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

Page 4 CornEd -- LaSalle Calculation Report for I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY01 @ 104 F, Design FF, 5% Plug, 5% Reduction in Flow Extrapolation Calculation for Row 4(Dry)Air-Side Tube-Side Mass Flow (lbm/hr) 67,203.40 37,264.79 Tube-Side hi (BTU/hr ft 2-°F) 962.97 Inlet Temperature (IF) 129.17 109.64 j Factor 0.0081 Outlet Temperature (IF) 124.62 111.69 Air-Side ho (BTU/hr-ft 2.°F) 8.17 Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-fi2-°F/BTU'

0.0 0031430

Outlet Specific Humidity 0.020268 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 Average Temp (IF) 126.90 110.6660 Skin Temperature

(°F) 114.98 112.4202 U Overall (BTU/hr ft2.°F) 5.51 Velocity *** 3.380.62 2.9075 Effective Area (ft 2) 860.06 Reynold's Number 815** 19,287 LMTD 16.11 Prandtl Number 0.7269 4.0144 Total Heat Transferred (BTU/hr) 76,356 Bulk Visc (lbm./fthr) 0.0479 1.4741 Skin Visc (lbm/ft-hr) 0.0000 1.4486 Surface Effectiveness (Eta) 0.9192 Density (Ibm/ft 3) 0.0641 61.8506 Sensible Heat Transferred (BTU/hr) 76,356 Cp (BTU/Ibm-°F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft'°F) 0.0158 0.3668 Heat to Condensate (BTU/hr)Relative Humidity In (%) 20.76 Relative Humidity Out (%) 23.47** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry) 7 1 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (0 F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibmr/ft-hr)

Skin Visc (lbm/ftihr)

Density (lbm/ft 3)Cp (BTU/lbm.°F)

K (BTU/hr-fti.F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 67,203.40 124.62 120.74 0.020268 0.020268 122.68 112.47 3.380.62 820**0.7272 0.0477 0.0000 0.0645 0.2402 0.0157 23.47 26.12 Tube-Side 37,264.79 107.89 109.64 108.7629 110.2792 2.9062 18,921 4.0998 1.5026 1.4799 61.8774 0.9988 0.3661 Tube-Side hi (BTU/hr f12.°F) 952.92 j Factor 0.0081 Air-Side ho (BTU/hr-ft2-°F) 8.15 Tube Wall Resistance (hr ft 2-°F/BTU' 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.50 860.06 13.81 65,316 0.9194 65,316 N .** Reynolds Number Outside Range of Equation Applicability 4?_ý 0 vi&*** Air Mass Velocity (Lbm/hr'ft 2). Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 06-09-2005 14:41:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

Page 5 ComEd -- LaSalle Calculation Report for I(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VYO1 @ 104 F, Design FF, 5% Plug, 5% Reduction in Flow Extrapolation Calculation for Row 6(Dry)Air-Side Tube-Side Mass Flow (lbm/hr) 67,203.40 37,264.79 Tube-Side hi (BTU/hrft 2"°F) 944.29 Inlet Temperature (OF) 120.74 106.38 j Factor 0.0081 Outlet Temperature (OF) 117.41 107.89 Air-Side ho (BTU/hr'ftl 2.F) 8.14 Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Outlet Specific Humidity 0.020268 Overall Fouling (hrft 2-°F/BTU) 0.02832467 Average Temp (°F) 119.08 107.1344 Skin Temperature (OF) 110.32 108.4442 U Overall (BTU/hr ft 2.°F) 5.48 Velocity *** 3.380.62 2.9052 Effective Area (fI) 860.06 Reynold's Number 824** 18,610 LMTD 11.85 Prandtl Number 0.7275 4.1753 Total Heat Transferred (BTU/hr) 55,913 Bulk Visc (lbm/ft-hr) 0.0474 1.5278 Skin Visc (lbm/ft'hr) 0.0000 1.5075 Surface Effectiveness (Eta) 0.9195 Density (Ibm/fl 3) 0.0649 61.9000 Sensible Heat Transferred (BTU/hr) 55,913 Cp (BTU/lbm-°F) 0.2402 0.9989 Latent Heat Transferred (BTU/hr)K (BTU/hr'ft'°F) 0.0157 0.3655 Heat to Condensate (BTU/hr)Relative Humidity In (%) 26.12 Relative Humidity Out (%) 28.66** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)Air-Side Mass Flow (lbm/hr) 67,203.40 Inlet Temperature (OF) 117.41 Outlet Temperature (OF) 114.56 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (°F) 115.99 Skin Temperature (OF) 108.48 Velocity *** 3.380.62 Reynold's Number 827**Prandtl Number 0.7277 Bulk Visc (Ibm/fl'hr) 0.0472 Skin Visc (lbm/ftrhr) 0.0000 Density (Ibm/fl 3) 0.0652 Cp (BTU/lbm-'F) 0.2402 K (BTU/hr-ft.°F) 0.0156 Relative Humidity In (%) 28.66 Relative Humidity Out (%) 31.06 Tube-Side 37,264.79 105.10 106.38 105.7400 106.8708 2.9043 18,345 4.2417 1.5498 1.5319 61.9190 0.9989 0.3650 Tube-Side hi (BTU/hr'fl 2"°F) 936.89 j Factor 0.0081 Air-Side ho (BTU/hr-ft2.°F) 8.12 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.47 860.06 10.17 47,894 0.9197 47,894 Reynolds Number Outside Range of Equation Applicability A~9L A~*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ftisec);

Air Density at Inlet T, Other Properties at Average T 06-09-2005 14:41:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

Page 6 ComEd -- LaSalle Calculation Report for 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, Design FF, 5% Plug, 5% Reduction in Flow Extrapolation Calculation for Row 8(Dry)II I, Air-Side Mass Flow (lbm/hr) 67,203.40 Inlet Temperature (0 F) 114.56 Outlet Temperature (7F) 112.12 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (7F) 113.34 Skin Temperature (0 F) 106.90 Velocity *** 3.380.62 Reynold's Number 830**Prandtl Number 0.7278 Bulk Visc (lbmr/fthr) 0.0471 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0655 Cp (BTU/Ibm'°F) 0.2402 K (BTU/hr'fV'F) 0.0155 Relative Humidity In (%) 31.06 Relative Humidity Out (%) 33.30 Tube-Side 37,264.79 103.99 105.10 104.5452 105.5210 2.9035 18,119 4.3000 1.5692 1.5534 61.9351 0.9989 0.3645 Tube-Side hi (BTU/hr-ft 2.°F) 930.53 j Factor 0.0081 Air-Side ho (BTU/hr'ft 2"°F) 8.11 Tube Wall Resistance (hr-fi 2"°F/BTU' 0.00031430 Overall Fouling (hr-fi 2"°F/BTU) 0.02832467 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)5.47 860.06 8.73 41,047 0.9198 41,047** Reynolds Number Outside Range of Equation Applicability jo,42_ '4 7 P(14(Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07-06-2005 12:28:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Data Report for I(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, Max FF, 5% Plug, reduction in air flow 7/6/05 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-°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.f.°F) 21,179.00 acfm 0.00 Ibm/hr 150.00 OF 92.00 OF 0.00 %109.40 OF 84.10 OF 0.00 %150.00 0.00 105.00 gpm lbm/hr OF 115.30 OF Fresh Water 0.004000 0.000400 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01 A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 19.00 0.5270 0.6250 1.500 1.452 q?-ýao o 1.000 4 225.00 07-06-2005 12:28:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for 1(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, Max FF, 5% Plug, reduction in air flow 7/6/05 Page I 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 (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 (acfrn)Tube Inlet Temp ('F)Air Inlet Temp ('F)Inlet Relative Humidity (%)Inlet Wet Bulb Temp ('F)Atmospheric Pressure (psia)75.00 18,075.00 104.00 148.00 12.76 0.00 14.315 T97-Iývo & '1oý*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average T 07-06-2005 12:28:20 PROTO-HX.4.01 by Proto-Power Corporation (SN#PHX-0000)

Page 2 CornEd -- LaSalle Calculation Report for I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY0I @) 104 F. Max FF, 5% Plug, reduction in air flow 7/6/05 Extrapolation Calculation Summary II Air-Side Mass Flow (lbm/hr) 66,793.22 Inlet Temperature (IF) 148.00 Outlet Temperature

(°F) 114.87 Inlet Specific Humidity Outlet Specific Humidity Tube-Side 37,264.79 104.00 118.87 Tube-Side hi (BTU/hr ft2.°F) 0.00 j Factor 0.0000 Air-Side ho (BTU/hr-fl 2.°F) 0.00 Tube Wall Resistance (hr-ft 2 -F/BTU' 0.00031430 Overall Fouling (hr-fl 2.°F/BTU) 0.07593245 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)6,880.52 0.00 553,584 0.0000 553,584 Extrapolation Calculation for Row 1(Dry) 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/ftihr)

Density (Ibm/fl 3)Cp (BTU/lbm.°F)

K (BTU/hr-fi.°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 66,793.22 148.00 141.83 0.020268 0.020268 144.91 128.95 3.359.98 792**0.7254 0.0490 0.0000 0.0622 0.2402 0.0162 12.76 14.91 Tube-Side 37,264.79 116.10 118.87 117.4817 119.7606 2.9122 20,617 3.7310 1.3790 1.3495 61.7503 0.9988 0.3692 Tube-Side hi (BTU/hr'ft 2 -F) 998.32 j Factor 0.0082 Air-Side ho (BTU/hr ft2. F) 8.21 Tube Wall Resistance (hr-ft2.0 F/BTU') 0.00031430 Overall Fouling (hr-ft 2.0 F/BTU) 0.07593245 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)4.39 860.06 27.30 103,117 0.9189 103,117 (3 ** Reynolds Number Outside Range of Equation Applicability

- - Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average T 07-06-2005 12:28:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

Page 3 ComEd -- LaSalle Calculation Report for I(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F. Max FF, 5% Plug, reduction in air flow 7/6/05 Extrapolation Calculation for Row 2(Dry)II Air-Side Mass Flow (lbm/hr) 66,793.22 Inlet Temperature (IF) 141.83 Outlet Temperature (IF) 136.39 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 139.11 Skin Temperature (IF) 125.00 Velocity *** 3.359.98 Reynold's Number 798**Prandtl Number 0.7259 Bulk Visc (lbm/ft.hr) 0.0487 Skin Visc (lbm/fithr) 0.0000 Density (Ibm/fl 3) 0.0628 Cp (BTU/Ibm.°F) 0.2402 K (BTU/hr-ft.°F) 0.0161 Relative Humidity In (%) 14.91 Relative Humidity Out (%) 17.15 Tube-Side 37,264.79 113.66 116.10 114.8760 116.9114 2.9104 20,105 3.8354 1.4142 1.3866 61.7894 0.9988 0.3683 Tube-Side hi (BTU/hr-ft 2-0 F) 984.79 j Factor 0.0082 Air-Side ho (BTU/hr'ft 2-°F) 8.19 Tube Wall Resistance (hr-fft. F/BTU' 0.00031430 Overall Fouling (hr-ft 2-F/BTU) 0.07593245 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)4.38 860.06 24.12 90,846 0.9191 90,846** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)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 Visc (lbm/ftlhr)

Skin Visc (lbm/ftihr)

Density (Ibm/ft 3)Cp (BTU/lbm-°F)

K (BTU/hr-ft.°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 66,793.22 136.39 131.60 0.020268 0.020268 134.00 121.53 3.359.98 803**0.7264 0.0484 0.0000 0.0633 0.2402 0.0160 17.15 19.46 Tube-Side 37,264.79 111.50 113.66 112.5798 114.3961 2.9088 19,657 3.9313 1.4464 1.4208 61.8230 0.9988 0.3675 Tube-Side hi (BTU/hr-ft 2.°F) 972.82 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2.°F) 8.17 Tube Wall Resistance (hr-fl 2-°F/BTU. 0.00031430 Overall Fouling (hr-ft2.°F/BTU)

0.0 7593245

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)4.37 860.06 21.31 80,084 0.9193 80,084** Reynolds Number Outside Range of Equation Applicability

~f 4 ,4*** Air Mass Velocity (Lbm/hr-fi 2). Tube Fluid Velocity (fi/sec);

Air Density at Inlet T, Other Properties at Average T 07-06-2005 12:28:20 07-062005onRepPROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

Cages Page 4 CornEd -- LaSalle Calculation Report for l(2)VYO IA & 02A -CSCS Equipment Area Cooling Coils VYOI @~ 104 F. Max FF, 5% Plug, reduction in air flow 7/6/05 Extrapolation Calculation for Row 4(Dry)II Air-Side Mass Flow (Ibm/hr) 66,793.22 Inlet Temperature (IF) 131.60 Outlet Temperature (IF) 127.37 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (IF) 129.48 Skin Temperature (IF) 118.47 Velocity *** 3.359.98 Reynold's Number 808**Prandtl Number 0.7267 Bulk Visc (lbm/ft-hr) 0.0481 Skin Visc (lbm/ftfhr) 0.0000 Density (lbM/ft 3) 0.0638 Cp (BTU/lbm.°F) 0.2402 K (BTU/hr-ft.°F) 0.0159 Relative Humidity In (%) 19.46 Relative Humidity Out (%) 21.79 Tube-Side 37,264.79 109.61 111.50 110.5551 112.1747 2.9074 19,265 4.0193 1.4758 1.4522 61.8521 0.9988 0.3667 Tube-Side hi (BTU/hr-ft 2.°F) 962.23 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2.°F) 8.15 Tube Wall Resistance (hr-ft2.°F/BTU`

0.0 0031430

Overall Fouling (hr-ft2-°F/BTU)

0.0 7593245

U Overall (BTU/hrft 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)4.36 860.06 18.84 70,636 0.9194 70,636** Reynolds Number Outside Range of Equation Applicability 11 Extrapolation Calculation for Row 5(Dry)Mass Flow (lbm/hr)Inlet Temperature

(°F)Outlet Temperature

(°F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (°F)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbm/ftihr)

Density (lbm/ft 3)Cp (BTU/ibm-°F)

K (BTUihr-ft.°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 66,793.22 127.37 123.64 0.020268 0.020268 125.51 115.76 3.359.98 812**0.7270 0.0478 0.0000 0.0642 0.2402 0.0158 21.79 24.11 Tube-Side 37,264.79 107.93 109.61 108.7689 110.2121 2.9062 18,922 4.0995 1.5026 1.4809 61.8773 0.9988 0.3661 Tube-Side hi (BTU/hr.ft 2.°F) 952.85 j Factor 0.0081 Air-Side ho (BTU/hr-ft2.°F) 8.13 Tube Wall Resistance (hr- ft 2-°F/BTU' 0.00031430 Overall Fouling (hr.ft 2.°F/BTU) 0.07593245 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)4.35 860.06 16.66 62,333 0.9196 62,333 ( j1 ** Reynolds Number Outside Range of Equation Applicability cfl-ýd 4a&#;ý*** Air Mass Velocity (Lbm/hrRfi 2), Tube Fluid Velocity (fi/sec);

Air Density at Inlet T, Other Properties at Average T 07-06-2005 12:28:20 PROTO-HX 4.01 by Proto-Power Corporation (SN#PHX-0000)

Page 5 ComEd -- LaSalle Calculation Report for 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, Max FF, 5% Plug, reduction in air flow 7/6/05tJ ii Extrapolation Calculation for Row 6(Dry)II 1.Mass Flow (ibm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)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/Ibm 0'F)K (BTU/hr-ft-°F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 66,793.22 123.64 120.35 0.020268 0.020268 121.99 113.38 3.359.98 816**0.7273 0.0476 0.0000 0.0645 0.2402 0.0157 24.11 26.40 Tube-Side 37,264.79 106.45 107.93 107.1924 108.4777 2.9052 18,621 4.1726 1.5269 1.5070 61.8992 0.9989 0.3655 Tube-Side hi (BTU/hr ft 2 0.F) 944.56 j Factor 0.0081 Air-Side ho (BTU/hr-ft2-°F) 8.11 Tube Wall Resistance (hr-ft 2-°F/BTU'j

0.0 0031430

Overall Fouling (hr'ft2-°F/BTU)

0.0 7593245

U Overall (BTU/hrft 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)4.34 860.06 14.73 55,030 0.9197 55,030** Reynolds Number Outside Range of Equation Applicability I Extrapolation Calculation for Row 7(Dry) = 1 Air-Side Mass Flow (lbm/hr) 66,793.22 Inlet Temperature (OF) 120.35 Outlet Temperature

(°F) 117.44 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (OF) 118.89 Skin Temperature

(°F) 111.27 Velocity *** 3.359.98 Reynold's Number 819**Prandtl Number 0.7275 Bulk Visc (lbm/ft-hr) 0.0474 Skin Visc (lbm/ft-hr) 0.0000 Density (lbm/ft 3) 0.0649 Cp (BTU/lbm-°F) 0.2402 K (BTU/hr'fi'°F) 0.0157 Relative Humidity In (%) 26.40 Relative Humidity Out (%) 28.64 Tube-Side 37,264.79 105.15 106.45 105.8003 106.9444 2.9043 18,356 4.2388 1.5489 1.5308 61.9182 0.9989 0.3650 Tube-Side hi (BTU/hr.fl 2 .F) 937.22 j Factor 0.0081 Air-Side ho (BTU/hr'ft2.°F) 8.10 Tube Wall Resistance (hr-ft 2.°F/BTUj)

0.0 0031430

Overall Fouling (hr-ft 2.°F/BTU) 0.07593245 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)4.34 860.06 13.03 48,601 0.9198 48,601** Reynolds Number Outside Range of Equation Applicability 44 6 12 4ý4C 6 4*** Air Mass Velocity (Lbm/hr'ft 2). Tube Fluid Velocity (fti/sec):

Air Density at Inlet T. Other Properties at Average T 07-06-2005 12:28:20 PROTO-HIX 4.01 by Proto-Power Corporation (SN#PHX-0000)

Page 6 ComEd -- LaSalle Calculation Report for I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYOI1 @ 104 F, Max FF, 5% Plug, reduction in air flow 7/6/05 I. d Extrapolation Calculation for Row 8(Dry)II 11 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (7F)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 (lbm/ft-hr)

Density (lbm/ftl)Cp (BTU/Ibm 0'F)K (BTU/hr'ftr'F)

Relative Humidity In (%)Relative Humidity Out (%)Air-Side 66,793.22 117.44 114.87 0.020268 0.020268 116.15 109.41 3.359.98 822*" 0.7277 0.0472 0.0000 0.0651 0.2402 0.0156 28.64 30.79 Tube-Side 37,264.79 103.99 105.15 104.5707 105.5885 2.9036 18,123 4.2987 1.5688 1.5523 61.9348 0.9989 0.3645 Tube-Side hi (BTU/hrft 2 0.°F) 930.72 j Factor 0.0081 Air-Side ho (BTU/hr-fl 2-°F) 8.09 Tube Wall Resistance (hr-ft 2-°F/BTU, 0.00031430 Overall Fouling (hr-ft 2-.F/BTU) 0.07593245 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)4.33 860.06 11.53 42,938 0.9199 42,938** Reynolds Number Outside Range of Equation Applicability q-7 -o/9~~wL -2 t7A' ~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

-ATTACHMENT I -Design Analysis Approval Page 1 of 2 DESIGN ANALYSIS NO.: CaIc. #97-200 PAGE NO. 1 Major REV Number: A Minor Rev Number: 01[ ] BRAIDWOOD STATION[ ] BYRON STATION DESCRIPTION CODE:(cois)

MIO[ ] CLINTON STATION[ I DRESDEN STATION[X ] LASALLE CO. STATION DISCIPLINE CODE: (c011) M[ ] QUAD CITIES STATION Unit:[ ]0 [X]I [X ]2 [ 13 SYSTEM CODE: (C011) VY TITLE: VY COOLER THERMAL PERFORMANCE MODEL -1(2)VYOIA and 1(2)VY02A[X ] Safety Related [ ] Augmented Quality [ I 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)IVYOIA H15 DCD/ EC#337494 Y EVAL 2VYOIA H15 I IVY02A H15 ...._/2VY02A H15 //REMARKS:

CC-AA-309

-ATTACHMENT I -Design Analysis Approval Page 2 of 2 DESIGN ANALYSIS NO.97-200 REV: A01 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 Colburn 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 extension/size/datelhourlmin)

Design impact review completed?

[ ] Yes [ x J N/A, Per (If yes, attach impact review sheet)Prepared by: .B._L. Davenport

!_______/

6 I-primt -,.,,"sign Date Reviewed by: D. J. Schmit t_ _

I_ J____,__,-f/-son d late Method of Review..[, Detailed []Alternate

[]Test This Design Analysisupeviedw: (tA ac e 3 Attached)R pIevmiewe by ti __________

I"i ,W-W e11N...... Riv TearnýApproved by: _________________I___-____-__-________________

-si.t" Sig Daft EStecialDeinAays Revie Tea (iAd ttachment 3 Attched.Reviewed b: I-j PrrtSi n t S a Print Sngn Date Co any ASSUMPTIONS

/ ENGINEERING JUDGEMENTS require later verification?

[ ] Yes [(X ] No Tracked By: AT#. EC# etc.)Prn SinI at Calculation No.97-200, Rev. AO1 Page 2 of_--PurposelObiective 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 Colbum '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.97-200, Rev. AO1 Pagel oft that the program is indeed using the natural log (Ln) function for its calculations. (A 6-,)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-O03-02 OB:55 zoo P 0 1 PROTO-POWER CORPORATION 0A Utility Engineering SUibsdiary SKAG NuW~ber 15 THAMES STI~rrr C".ION*, Ci fOG340 PH* W30l44f.9795 I-X: P00.440,8292 WWW-PnmroP0Wcr.CAoM MEMORANDUM File No. 908OF/050119/M02001 To: Brian Davenport From: Joseph G- Fay;Date: April 3,2002

Subject:

PROT'O--HX Air Coil Module Brian, The PROTO-I-IX 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 questionsa, please feel free to give me a call.Sorry for the con'fuLaion.

JGF:baj CC: Joseph G. Fayan Job File

[ LASALLE CALCULATION EDITORIAL

-COMMENT TO CALCULATION AffectingNo:( -Rv:A o{R PgN.cumtions o itl n R i V i I I- ,( (- k PgeNo. 1041 The use of this form shall be limited to document corrections of editorial nature. Return to Sylvia Venecia Prepared by: ../\ rtri n -.Sign. Date Reviewed by: Print Sign Date Approved by: Print Sign Date Description of Correction:

W \hen these comments are incorporated, return this li0nn with the revised calculation.

Incorporated on Caic Rev. Biy: Date: I CC-AA-309

-ATTACHMENT 1 -Design Analysis Approval Page 1 of 2 Major REV Number: A Minor Rev Number: 00[ ] BRAIDWOOD STATION BYRON STATION[ I CBYRON STATION DESCRIPTION CODE:(c08)

Mý41-[1CLINTON STATION[ ] DRESDEN STATION[XI LASALLE CO. STATION DISCIPLINE CODE: (Coil) M[ I QUAD CITIES STATION Unit:[ 10 [X]I [X]2 1 33 SYSTEM CODE: (C011) VY TITLE: VY Cooler Thermal Performance Model -1(2)VYOIA and 1(2)VYO2A[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 Type/Sub Document Number Input (Y/N)1VY01A H15 _ _ _ /DCP EC# 334017 Y 2VY01A H15 /IVY02A H15 I 2VY02A 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 1 -Design Analysis Approval Page 2 of 2 DESIGN ANALYSIS NO.97-200 REV: AOO PAGE NO. 2 Revision Summary (including EC's incorporated):

Updated ProtoHX model for 1040F Service Water inlet temperature and calculated thermal margins with the design fouling factor and 5% tubes plugged for the Unit 1 and 2 A RHR Pump Room Coolers (1/2VY01A) and HPCS Pump Room Coolers (1/2VYo2A).

Electronic Calculation Data Files: ProtoHX 3.02. vy-0102a.phx.

1152 KB. 11/02/2001.2:14 am (Program Name. Version. File Name extension/sizeldate/hourlmin)

Design impact review completed?(If yes, attach impact review sheet)[I Yes [ X I N/A, Per EC#: 334017 Prepared by: Jeff W. VanStiten Reviewed by: BMian L Davenport I kh 1-i~z I ~I -Date JI -j,- 'rt-Method of Review:.P[Dt IX I Detailed[ Test Date] Alternate-Pam Sign date External DesMIn Analysis Review (Attachment 3 Attached)Reviewed by:I!-so Dde Approved by: /-Prift Si~gn Date Do any ASSUMPTIONS

/ ENGINEERING JUDGEMfENTS require later verification?

[]Yes [X] 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 CornEd Effective Date: 04/14/00 CALCULATION TABLE OF CONTENTS CALCULATION NO.97-200 REV. NO. AOO 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 7 8.0 ATTACHMENTS:

7 Attachment "A" -Proto-Hx Calc. Report for 1(2)VY01A

& 1(2)VY02A Al to A17 (CSCS=104°F

@ Design Fouling)Attachment "B" -Proto-Hx CaIc. Report for 1(2)VYOIA

& 1(2)VY02A B1 to B17 (CSCS=104°F

@ Design FF, 5% Plugged)Attachment "C" -Proto-Hx CaIc. Report for 1(2)VY01A

& 1(2)VY02A C1 to C17 (For VY01, CSCS=104 0 F @ Max. Allowable FF, w\ 5% plugged)(For VY02, CSCS=104 0 F @ Design FF, Room Temp. = 150 0 F)I I I E-FORM I CoA J NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE I CALCULATION NO.97-200 REV. NO. AOO PAGE NO. 4 of 7 1.0 PURPOSEIOBJECTIVE The purpose of this minor revision is to revise the thermal model of the A RHR Pump Room Coolers (1/2VY01A) and the HPCS Pump Room Coolers (1/2VY02A) using 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 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 100OF to 104OF and simulated for the following conditions:

design fouling factor and design fouling factor with a 5% tube plugging allowance.

The acceptance criteria will be for the thermal margin at each stated condition to exceed the LaSalle design heat load of 517,239 BTU/hr for 1/2VY01A and 646,235 BTU/hr for 1/2VY02A (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 these heat exchangers 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 I listed below.

5.0 REFERENCES

1. Calculation No.97-200, Rev. A," VY Cooler Thermal Performance Model -1(2)VY01A and 1 (2)VY02A." 2. Calculation No. L-002457, Rev. 4, "LaSalle County Station Ultimate Heat Sink Analysis".

I E-FORM I CornEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO.97-200 REV. NO. AOO PAGE NO. 5 of 7 6.0 CALCULATIONS The current calculation model is based on a Service Water inlet temperature of 1 00 0 F with a varying service water flow rates. Based on Reference 1 Calculations, the limiting flow rates, heat transfer rates, and thermal margins are as follows: Table 1: At Limiting Flow rates, 100°F Service Water Inlet Temp. and Overall FF = 0.03976622 hr*ft 2*OF/BTU (Ref. 1, table 9).Limiting Flow Qrequdred Qavallable Cooler Rate (gpm) (BTU/hr) (BTUIhr) Thermal Margin (%)1(2)VY0IA 75 517,239 675,177 30.5%1 (2)VY02A 108 646,235 707,030 9.4%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: The rmalM arg in x 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 overall fouling factor of 0.02832467 hr*ft2*OF/BTU, the new thermal margins are shown in Table 2.Table 2: At Limiting Flow rates, 104 0 F Service Water Inlet Temp. and Design Overall FF =0.02832467 hr*ft 2*OF/BTU [,AttachmentA_.

Limiting Flow Qrequlred Qavallable Cooler Rate (gpm) (BTU/hr) (BTU/hr) Thermal Margin (%)1(2)VY01A 75 517,239 629,279 21.7%1 (2)VY02A 108 646,235 659,062 2.0%I E-FORM I CornEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE ICALCULATION NO.97-200 REV. NO. AOO PAGE NO. 6 of 7 Furthermore, if we consider the above conditions (in Table 2) and factor in a 5% tube plugging allowance the following Thermal Margins are calculated in Attachment B.Table 3: At Limiting Flow rates, 104 0 F Service Water Inlet Temp., Design FF = 0.02832467 hr*ft 2*OF/BTU and 5% plu, ged [Attachment B].Limiting Flow Qrequlred Qavallable Cooler Rate (gpm) (BTUlhr) (BTUlhr) Thermal Margin (%)1(2)VY01A 75 517,239 625,070 20.8%1 (2)VY02A 108 646,235 653,739 1.2%In addition, the maximum allowable Fouling Factors for each cooler, while maintaining at least a 5% thermal margin at 104 0 F inlet service water temperature with a 5% tube plugging allowance, are listed in Table 4.Table 4: Maximum Allowable Fouling Factors at 104 0 F Service Water inlet temp. and 5% plugged.[Attachment C1.Maximum Cooler Overall FF 1(2)VYO1A 0.0949 1(2)VY02A Note 1 Note 1: As demonstrated by the results in tables 2 and 3, air cooler 1(2)VY02A does not have analytical thermal margin in excess of the assumed 5% model uncertainty at the elevated inlet service water temperature of 104 0 F, room air temperature of 148 0 F and the design overall fouling factor of 0.02832467 hr*ft 2*0FIBTU. However an additional Proto-HX run at a room air temperature of 150 0 F, service water inlet temperature of 104 0 F, no tubes plugged and the design overall fouling factor of 0.02832467 hr*ft 2 0*F/BTU demonstrated in excess of the 5% thermal margin needed to account for analytical uncertainty

[Attachment C]. This is discussed further in the summary and conclusion section below.E-FORM I CornEd NES-G-14.02 Effective Date: 04/14/00 CALCULATION PAGE 1 CALCULATION NO.97-200 REV. NO. AOO PAGE NO. 7 of 7 7.0

SUMMARY

AND CONCLUSIONS The A RHR Pump Room Coolers (1/2VY01A) and HPCS Pump Room Coolers (1/2VY02A) were found to have adequate thermal margin for a maximum lake temperature of 104OF when operated at design fouling conditions (the design overall fouling factor of 0.02832467 hr*ft 2*OF/BTU).

The maximum allowable overall fouling factor for the 1(2)VY01A coolers is 0.0949 hr*ft 2*OF/BTU (includes an allowance for 5% of the tubes to be plugged).For the 1 (2)VY02A coolers the maximum allowable fouling factor is equal to the design overall fouling factor of 0.02832467 hr*ft 2*OF/BTU (this does NOT include a 5% tube plugging allowance).

It should be noted that the inlet air temperature was increased 2 0 F (from 148OF to 150 0 F) to achieve the desired thermal margin of 5%. A review of the EQ equipment in the room determined that all EQ components are qualified for temperature exceeding 150OF for the first 24 hours2.777778e-4 days 0.00667 hours 3.968254e-5 weeks 9.132e-6 months of the LOCA. The time at which the service water inlet temperature could experience 104 0 F is short term in nature and bounded by the 24-hour period specified above. The post LOCA peak service water temperature profile is documented within reference

2. Figure G7.1 within reference 2 demonstrates that the maximum post accident service water temperatures remain well below 100 OF except for a short period of time within the first day after the SCRAM occurs.8.0 ATTACHMENTS:

Attachment "A" -Proto-Hx Calc. Report for 1(2)VY01A

& 1(2)VY02A (CSCS=104 0 F @ Design Fouling)Attachment "B" -Proto-Hx CaIc. Report for 1(2)VY01A

& 1(2)VY02A (CSCS=104 0 F @ Design FF, 5% Plugged)Attachment "C" -Proto-Hx Calc. Report for 1(2)VY01 A & 1 (2)VY02A (For VY01, CSCS=104*F

@ Max. Allowable FF, w\ 5% plugged)(For VY02, CSCS=104 0 F @ Design FF, Room Temp. = 150 0 F)Final Page (Last Page)I E-FORM I CornEd CALCULATION NO.97-200 REVISION NO. AO0 PAGE NO. Al of A17 Attachment "A" Proto-Hx Calc. Report for 1(2)VY01A

& 1(2)VY02A (CSCS=104°F

@ Design Fouling)I E-FORM I 17:51:19 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 04/24/02 ComEd -- LaSalle Data Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, DESIGN FF Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 21,179.00 acfm 150.00 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 109.40 OF 115.30 OF Outlet Wet Bulb Temp 84.10 OF Outlet Relative Humidity %Tube Fluid Name Fresh Water Tube Fouling Factor 0.001500 Air-Side Fouling 0.000000 Design Heat Transfer (BTU/hr) 750,000 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 VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]Coil Finned Length (in) 104.250 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) 1.495 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) 1.452 Number of Serpentines 1.000 Tube Wall Conductivity (BTU/hr-ft.°F) 225.00 Calculation No.97-200 Revision No. AOO Attachment

_t)_Page No. Ai- of 17:51:19 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/24/02 CornEd -- LaSalle Calculation Report for: I(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VYOI (@2 104 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 (OF)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) 75.00 Air Flow (acfm) 19,120.00 Tube Inlet Temp (OF) 104.00 Air Inlet Temp (OF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (OF) 0.00 Atmospheric Pressure 14.315 Calculation No.97-200 Revision No. AO0 Attachment A Page No. _ of 4/7 17:51:19 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VYO @ 104 F, DESIGN FF 04/24/02 FI Extrapolation Calculation Summary 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/ftfhr)

Density (lbm/ft 3)Cp (BTU/Ibm 0'F)K (BTU/hr-ft 0-F)Air-Side 70,654.85 148.00 112.40 Tube-Side 37,262.20 104.00 120.93 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*.F/BTU. 0.00031430 Overall Fouling (hr-ft2. F/BTU) 0.02832467 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)7,242.65 629,279 629,279'I Extrapolation Calculation for Row l(Dry)II II Mass Flow (lbm/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/ltfhr)

Skin Visc (lbm/ff-hr)

Density (Ibm/ft3)Cp (BTU/lbm-°F)

K (BTU/hr'fr°F)

Air-Side 70,654.85 148.00 140.90 0.0203 0.0203 144.45 125.98 3,376.53 796**0.7254 0.0490 Tube-Side 37,262.20 117.56 120.93 119.24 121.97 2.77 19,916 3.6630 1.3561 1.3218 61.7233 0.9988 0.3698 Tube-Side hi (BTU/hr1ft 2.F) 967.24 j Factor 0.0082 Air-Side ho (BTU/hruft 2.F) 8.24 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2.'F/BTU) 0.02832467 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)5.55 905.33 25.01 125,565 0.9186 125,565 0.0623 0.2402 0.0162** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment

_Page No. Al of!Og*** Air Mass Velocity (Lbm/hrfiV2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 17:51:19 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

ComEd -- LaSalle Calculation Report for: 1(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, DESIGN FF 04/24/02 0_Extrapolation Calculation for Row 2(Dry)II i Air-Side Tube-Side Mass Flow (lbm/hr) 70,654.85 37,262.2(Inlet Temperature (IF) 140.90 114.6(Outlet Temperature (IF) 134.79 117.5 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 137.84 116.1 Skin Temperature (IF) 121.93 118.4'Velocity *** 3,376.53 2.7 Reynold's Number 803** 19,32'Prandtl Number 0.7260 3.785!Bulk Visc (Ibm/if-hr) 0.0486 1.397L Skin Visc (lbm/ft-hr) 1.365[Density (lbm/ft 3) 0.0630 61.771(Cp (BTU/lbm-°F) 0.2402 K (BTU/hr-fi.°F) 0.0161 0.368** Reynolds Number Outside Range of Equation Applicability 5 7 7 5 4 8 7 Tube-Side hi (BTU/hr-ft 2.°F) 951.58 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2 .°F) 8.21 Tube Wall Resistance (hr-ft 2.°F/BTU, 0.00031430 Overall Fouling (hr-ft 2.F/BTU) 0.02832467 U Overall (BTU/hr-fl 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)5.52 905.33 21.57 107,856 0.9189 107,856 VNWI. -1 Extrapolation Calculation for Row 3(Dry)II 1. .'Air-Side Tube-Side Mass Flow (Ibm/hr) 70,654.85 37,262.21 Inlet Temperature (OF) 134.79 112.1'Outlet Temperature (OF) 129.55 114.6i Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 132.17 113.4 Skin Temperature (OF) 118.45 115.4 Velocity *** 3,376.53 2.7 Reynold's Number 809** 18,82'Prandtl Number. 0.7265 3.896 Bulk Visc (lbm/ft-hr) 0.0483 1.434(Skin Visc (lbm/ft-hr) 1.405'Density (lbm/ft 3) 0.0635 61.810'Cp (BTU/Ibm-°F) 0.2402 0.998: K (BTU/hr-ft.°F) 0.0160 0.367:** Reynolds Number Outside Range of Equation Applicability 0 7 6 1 9 6 7 7 9 Tube-Side hi (BTU/hr-ft 2.'F) 938.05 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2.'F) 8.18 Tube Wall Resistance (hr-ft 2 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 U Overall (BTU/hrft2.°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)5.50 905.33 18.61 92,745 0.9191 92,745 Calculation No.97-200 Revision No. AOO Attachment

__Page No. A5 of ArI*** Air Mass Velocity (Lbm/hr'fi 2), Tube Fluid Velocity (ftlsec);

Air Density at Inlet T, Other Properties at Average T 17:51:19 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY0I @ 104 F, DESIGN FF 04/24/02.1 (ft Extrapolation Calculation for Row 4(Dry)11 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//f-hr)

Air-Side 70,654.85 129.55 125.03 0.0203 0.0203 127.29 115.45 3,376.53 814*4 0.7269 0.0479 Tube-Side 37,262.20 110.02 112.17 111.09 112.90 2.76 18,399 3.9956 1.4679 Tube-Side hi (BTU/hr'ft 2 °F) 926.37 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.F) 8.16 Tube Wall Resistance (hr ft 20.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 U Overall (BTU/hr'ft 2'°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)5.49 905.33 16.07 79,826 0.9193 79,826 Skin Visc (Ibm/ft-hr) 1.4417 Density (ibm/fl 3) 0.0640 61.8445 Cp (BTU/lbm'°F) 0.2402 0.9988 K (BTU/hr'ft'°F) 0.0158 0.3669** Reynolds Number Outside Range of Equation Applicability

-14M I[-Extrapolation Calculation for Row 5(Dry)II I.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/fl 3)Cp (BTU/lbm-'F)

K (BTU/hr-ft'°F)

Air-Side 70,654.85 125.03 121.14 0.0203 0.0203 123.08 112.87 3,376.53 818**0.7272 0.0477 Tube-Side 37,262.20 108.17 110.02 Tube-Side hi (BTU/hr-ft 2-F) 916.28 j Factor 0.0081 Air-Side ho (BTU/hr'ft 2-F) 8.15 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2 l-F/BTU) 0.02832467 109.10 110.67 2.76 18,034 4.0846 1.4976 1.4740 61.8727 0.9988 0.3662 U Overall (BTU/hr-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)5.47 905.33 13.88 68,762 0.9194 68,762 0.0644 0.2402 0.0158** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment A Page No. A ot'17*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ftisec);

Air Density at Inlet T, Other Properties at Average T 17:51:19 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, DESIGN FF 04/24/02 Extrapolation Calculation for Row 6(Dry)II'I 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/f-hr)

Air-Side 70,654.85 121.14 117.79 0.0203 0.0203 119.46 110.64 3,376.53 822**0.7274 0.0474 Tube-Side 37,262.20 106.58 108.17 107.38 108.75 2.76 17,722 4.1639 1.5240 1.5028 Tube-Side hi (BTU/hr' ft 2-OF) 907.56 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.°F) 8.13 Tube Wall Resistance (hr-ft 2-F/BTU, 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 U Overall (BTU/hr-ft2.

F)Effective Area (ft 2)LMTD Total Heat T-ansferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.46 905.33 11.99 59,274 0.9196 59,274 Density (lbm/ft 3) 0.0648 61.8966 Cp (BTU/lbm.'F) 0.2402 0.9989 K (BTU/hr-ft-'F) 0.0157 0.3656** Reynolds Number Outside Range of Equation Applicability MOM. I1 Extrapolation Calculation for Row 7(Dry)II I.Air-Side Tube-Side Mass Flow (lbrn/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 (lbm/ft 3)Cp (BTU/lbm-'F)

K (BTU/hr-ft-.F) 70,654.85 117.79 114.89 0.0203 0.0203 116.34 108.72 3,376.53 826**0.7276 0.0473 0.0651 0.2402 0.0156 37,262.20 105.21 106.58 105.89 107.09 2.76 17,454 4.2343 1.5474 1.5285 61.9169 0.9989 0.3650 Tube-Side hi (BTU/hr ft 2-°F) 900.01 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2-OF) 8.12 Tube Wall Resistance (hr-ft 2.°F/BTUP, 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 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)5.45 905.33 10.37 51,127 0.9197 51,127** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment

_pL Page No. A7 of Al7*** Air Mass Velocity (Lbm/hr-fi 2). Tube Fluid Velocity (ft/sec);

Air Density at Inlet T. Other Properties at Average T 17:51:19 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

ComEd -- LaSalle Calculation Report for: I(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, DESIGN FF 04/24/02 WI p Extrapolation Calculation for Row 8(Dry)II P.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/ft-hr)

Skin Visc (lbm/ftfhr)

Density (Ibm/ft)Cp (BTU/lbm-°F)

K (BTU/hr-ft-'F)

Air-Side 70,654.85 114.89 112.40 0.0203 0.0203 113.64 107.06 3,376.53 829**0.7278 0.0471 Tube-Side 37,262.20 104.02 105.21 Tube-Side hi (BTU/hrft 2 0.'F) 893.49 j Factor 0.0081 Air-Side ho (BTU/hr ft 2.'F) 8.11 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr'ft 2-F/BTU) 0.02832467 104.61 105.65 2.76 17,224 4.2966 1.5680 1.5513 61.9342 0.9989 0.3646 U Overall (BTU/hr-ft-°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)5.44 905.33 8.96 44,124 0.9198 44,124 0.0654 0.2402 0.0155** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment

_A Page No. AV' of An Air Mass Velocity (Lbrn/hr-fi 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T Inlet Air Flowrate Calculator

-1(2)VY01A Total P: P=Dry Bulb T OUT: T=Specific Hum.: W =H20 yap P: Pv = (W*Rv*P)/(Ra+(W*Rv)

=Dry Air P: Pa = P -Pv =Dry Air rho OUT: rho a = (144/Ra)*(PaI(459.67+T)

=Dry Air rho IN: rho a = (144/Ra)*(Pa/(459.67+T)

=Dry Bulb T IN: T=Outlet Air Flow: V =14.315 psia Inlet Air Flow 112.4 F 19120 acfm 0.020274 0.451875 psia Rv = 85.778 (ft-lbf)/(Ibm-R)

Ra = 53.352 (ft-lbf)/(Ibm-R) 13.86313 psia 0.0654 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 18000 cfm Calculation No.97-200 Revision No. AOO Attachment Page No. Aj of 18:00:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 04/24/02 ComEd -- LaSalle Data Report for: 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 21,179.00 acfm 150.00 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 109.40 OF 115.30 OF Outlet Wet Bulb Temp 84.10 OF Outlet Relative Humidity %Tube Fluid Name Fresh Water Tube Fouling Factor 0.001500 Air-Side Fouling 0.000000 Design Heat Transfer (BTU/hr) 750,000 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 VY Coolers 01A/02A j EXP[-2.5088

+ -0.3436

LOG(Re)]Coil Finned Length (in) 104.250 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) 1.495 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) 1.452 Number of Serpentines 1.000 Tube Wall Conductivity (BTU/hr'ft'°F) 225.00 CaIcuL ation No.97-200 Revision No. A00 Attachment Page No. Aiiotf AO 18:00:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/24/02 ComEd -- LaSalle Calculation Report for: 1(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 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 ('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) 108.00 Air Flow (acfm) 19,173.00 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.97-200 Revision No. AO0 Attachment AL Page No. -of A/17 18:00:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF 04/24/02 Extrapolation Calculation Summary II 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/ifthr)

Skin Vise (Ibm/ft hr)Density (lbm/ftV)Cp (BTU/lbm 0'F)K (BTU/hr'ff'-F)

Air-Side 70,850.70 148.00 110.81 Tube-Side 53,657.57 104.00 116.29 Tube-Side hi (BTU/hr-ft 2-°F)j Factor Air-Side ho (BTUihr fi2.0 F)Tube Wall Resistance (hr-ft 2.°F/BTU; 0.00031430 Overall Fouling (hr-ft 2-F/BTU) 0.02832467 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)7,242.65 659,062 659,062 WI. .1 Extrapolation Calculation for Row l(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 (Ibm/ft'hr)

Density (Ibmi/f 3)Cp (BTU/Ibm'°F)

K (BTU/hr-ft-°F)

Air-Side 70,850.70 148.00 139.65 0.0203 0.0203 143.82 122.08 3,385.89 799**0.7255 0.0490 Tube-Side 53,657.57 113.53 116.29 114.91 117.36 3.98 27,510 3.8340 1.4137 1.3806 61.7889 0.9988 0.3683 Tube-Side hi (BTU/hr ft 2.°F) 1,266.21 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2-°F) 8.25 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr.ft 2.°F/BTU) 0.02832467 U Overall (BTU/hr.ft 2.F)Effective Area (if 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.70 905.33 28.70 148,029 0.9185 148,029 0.0624 0.2402 0.0162** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment

_Page No. A_, .of A1_*** Air Mass Velocity (Lbmi/hrftfi), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T. Other Properties at Average T 18:00:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: I(2)VYOlA

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF 04/24/02 I -.1 Extrapolation Calculation for Row 2(Dry)II 11 -1 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (°F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (Ibm/frhr)

Density (lbm/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hr'fl-°F)

Air-Side 70,850.70 139.65 132.79 0.0203 0.0203 136.22 118.31 3,385.89 807**0.7262 0.0485 Tube-Side 53,657.57 111.26 113.53 112.39 114.44 3.98 26,839 3.9393 1.4490 1.4202 61.8258 0.9988 0.3674 Tube-Side hi (BTU/hr-ft 2.°F) 1,249.06 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2-°F) 8.22 Tube Wall Resistance (hr.ft 2.°F/BTU; 0.00031430 Overall Fouling (hr-ft 2-'F/BTU) 0.02832467 U Overall (BTU/hr-ft 2 i.F)Effective Area (ft')LMTD Total Heat Transfe-red (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.67 905.33 23.65 121,509 0.9188 121,509 0.0632 0.2402 0.0160** Reynolds Number Outside Range of Equation Applicability vr~tw. .1* Extrapolation Calculation for Row 3(Dry)II 1.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 (Ibm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr-ft-°F)

Air-Side 70,850.70 132.79 127.16 0.0203 0.0203 129.97 115.21 3,385.89 813*4 0.7267 0.0481 Tube-Side 53,657.57 109.40 111.26 Tube-Side hi (BTU/hr ft 2.-F) 1,234.94 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.°F) 8.19 Tube Wall Resistance (hr-ft 2-°F/BTU" 0.00031430 Overall Fouling (hr'ft'°F/BTU)

0.0 2832467

110.33 112.03 3.98 26,293 4.0293 1.4791 1.4543 61.8554 0.9988 0.3667 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)5.66 905.33 19.50 99,875 0.9190 99,875 0.0638 0.2402 0.0159** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment A Page No. Ao of Ai-7*** Air Mass Velocity (Lbm/hr'ft'), Tube Fluid Velocity (ft/sec), Air Density at Inlet T, Other Properties at Average T 18:00:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: I(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF 04/24/02[I Extrapolation Calculation for Row 4(Dry) I Air-Side 70,850.70 Tube-Side 53,657.57 Mass Flow (lbmrhr)Inlet Temperature (IF) 127.16 107.86 Outlet Temperature (IF) 122.52 109.40 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (°F) 124.84 108.63 Skin Temperature (IF) 112.66 110.04 Velocity *** 3,385.89 3.98 Reynold's Number 819** 25,847 Prandtl Number 0.7271 4.1059 Bulk Visc (lbm/ft-hr) 0.0478 1.5047 Skin Visc (ibm/ftbhr) 1.4834 Density (lbm/ft 3) 0.0643 61.8793 Cp (BTU/lbm'°F) 0.2402 0.9988 K (BTU/hr-it'°F) 0.0158 0.3660** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hr- ft 2-°F) 1,223.28 j Factor 0.0081 Air-Side ho (BTU/hr ft 2.°F) 8.17 Tube Wall Resistance (hr-ft 2.°F/BTU, 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 U Overall (BTU/hr.ft 2-°F)Effective Area (ft 2)LMTD Total Heat Transferred (BTUT/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.64 905.33 16.09 82,183 0.9192 82,183 tin.Extrapolation Calculation for Row 5(Dry)II IL_Mass Flow (lbm/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 (ibm/ft-hr)

Skin Visc (lbm/ftdhr)

Density (Ibm/ft 3)Cp (BTU/lbm'°F)

K (BTU/hr'ft-°F)

Air-Side 70,850.70 122.52 118.70 0.0203 0.0203 120.61 110.56 3,385.89 823**0.7274 0.0475 0.0647 0.2402 0.0157 Tube-Side 53,657.57 106.60 107.86 107.23 108.40 3.97 25,481 4.1707 1.5263 1.5081 61.8987 0.9989 0.3655 Tube-Side hi (BTU/hr-ft 2-°F) 1,213.65 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.°F) 8.15 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.63 905.33 13.28 67,688 0.9194 67,688** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment A Page No. A of Ai7 Air Mass Velocity (Lbm/hr-it 2), Tube Fluid Velocity (ft/see);

Air Density at Inlet T, Other Properties at Average T 18:00:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF 04/24/02 I. .1 Extrapolation Calculation for Row 6(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 (Ibm/if3)Cp (BTU/1bm'°F)

K (BTU/hr-ft'°F)

Air-Side 70,850.70 118.70 115.55 0.0203 0.0203 117.13 108.83 3,385.89 827**0.7276 0.0473 0.0651 0.2402 0.0156 Tube-Side 53,657.57 105.56 106.60 106.08 107.05 3.97 25,182 4.2254 1.5444 1.5291 61.9144 0.9989 0.3651 Tube-Side hi (BTU/hr.ft 2.°F) 1,205.71 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2'°F) 8.14 Tube Wall Resistance (hrift 2.F/BTU; 0.00031430 Overall Fouling (hr-ft 2'-F/BTU) 0.02832467 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)5.62 905.33 10.97 55,792 0.9195 55,792** Reynolds Number Outside Range of Equation Applicability t.ism .1 Extrapolation Calculation for Row 7(Dry)II Air-Side Tube-Side Mass Flow (lbm/hr) 70,850.70 53,657.57 Inlet Temperature

(°F) 115.55 104.70 Outlet Temperature

(°F) 112.96 105.56 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (°F) 114.26 105.13 Skin Temperature

(°F) 107.40 105.94 Velocity *** 3,385.89 3.97 Reynold's Number 830** 24,935 Prandtl Number -.. ..0.7278 4.2713 Bulk Visc (Ibm/ft-ir) 0.0471 1.5597 Skin Visc (Ibm/ft-hr) 1.5467 Density (lbm/ft 3) 0.0654 61.9273 Cp (BTU/lbm-°F) 0.2402 0.9989 K (BTU/hr'ft'°F) 0.0156 0.3647** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hr-ft 2-°F) 1,199.14 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.°F) 8.12 Tube Wall Resistance (hrft 2.°F/BTU, 0.00031430 Overall Fouling (hr-ft2.°F/BTU)

0.0 2832467

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)5.61 905.33 9.06 46,015 0.9196 46,015 Calculation No.97-200 Revision No. AOO Attachment A Page No. -of Al17*** Air Mass Velocity (Lbm/hr-fIV), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average T 18:00:16 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF 04/24/02 1l Extrapolation Calculation for Row 8(Dry) 11 Air-Side Mass Flow (lbm/hr) 70,850.70 Inlet Temperature (0 F) 112.96 Outlet Temperature

(°F) 110.81 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (°F) 111.89 Skin Temperature (7F) 106.22 Velocity *** 3,385.89 Reynold's Number 833**Prandtl Number 0.7279 Bulk Visc (lbm/ftrhr) 0.0470 Skin Visc (lbm/ftfhr)

Density (lbm/ft 3) 0.0656 Cp (BTU/Ibm-°F) 0.2402 K (BTU/hr'ft-'F) 0.0155 Tube-Side 53,657.57 103.99 104.70 104.35 105.01 3.97 24,733 4.3099 1.5725 1.5615 61.9378 0.9989 0.3644 Tube-Side hi (BTU/hr fF2.°F) 1,193.72 j Factor 0.0081 Air-Side ho (BTU/hr-ft1 2-F) 8.11 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr ft 2.°F/BTU) 0.02832467 U Overall (BTU/hr.ftV.'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)5.60 905.33 7.49 37,972 0.9197 37,972** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment Page No. L of_*** Air Mass Velocity (Lbrn/hr'tV), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T Inlet Air Flowrate Calculator

-1(2)VY02A 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: 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=14.315 psia Inlet Air Flow 110.81 F 19173 acfm 0.020274 0.451875 psia Rv = 85.778 (ft-Ibf)/(Ibm-R)

Ra = 53.352 (ft-lbf)/(Ibm-R) 13.86313 psia 0.0656 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 18000 cfm Calculation No.97-200 Revision No. AO0 Attachment A Page No. Ar_

CornEd CALCULATION NO.97-200 REVISION NO. AOO PAGE NO. B1 of B17 Attachment "B" Proto-Hx Calc. Report for 1(2)VY01A

& 1(2)VY02A (CSCS=104 0 F @ Design FF, 5% Plugged)II E-FORM 18:12:37 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 04/24/02 ComEd -- LaSalle Data Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, DESIGN FF, 5% PLUG Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 21,179.00 acfm 150.00 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 109.40 OF 115.30 OF Outlet Wet Bulb Temp 84.10 OF Outlet Relative Humidity %Tube Fluid Name Fresh Water Tube Fouling Factor 0.001500 Air-Side Fouling 0.000000 Design Heat Transfer (BTU/hr) 750,000 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 VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]Coil Finned Length (in) 104.250 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) 1.495 Number of Coils Per Unit 2 Number of Tube Rows 8 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) 1.500 Transverse Tube Pitch (in) 1.452 Number of Serpentines 1.000 Tube Wall Conductivity (BTU/hr-ft-°F) 225.00 Calculation No.97-200 Revision No. AO0 Attachment D Page No. j- of_&!

18:12:37 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/24/02 CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F, DESIGN FF, 5% PLUG 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 (fF)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) 75.00 Air Flow (acfm) 19,113.00 Tube Inlet Temp (OF) 104.00 Air Inlet Temp (OF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (OF) 0.00 Atmospheric Pressure 14.315 Calculation No.97-200 Revision No. AOO Attachment g Page No. 6-1 of Rr-18:12:37 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: I(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VYO0 @ 104 F, DESIGN FF, 5% PLUG 04/24/02 0..Extrapolation Calculation Summary II Air-Side Mass Flow (lbn/hr) 70,628.98 Inlet Temperature (0 F) 148.00 Outlet Temperature (0 F) 112.62 Inlet Specific Humidity Outlet Specific Humidity Average Temp (°F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm//.fhr)

Skin Visc (lbm/ft-hr)

Density (ibm/fl 3)Cp (BTU/lbm-°F)

K (BTU/hr'ft'F)

Tube-Side 37,262.20 104.00 120.76 Tube-Side hi (BTU/hr-ft.F) j Factor Air-Side ho (BTU/hr.ft 2'F)Tube Wall Resistance (hr'ft2-°F/BTU'

0.0 0031430

Overall Fouling (hr.ft7 2.F/BTU) 0.02832467 U Overall (BTU/hrft2-°'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)6,880.52 625,070 625,070 B .3 Extrapolation Calculation for Row l(Dry)II 1.Air-Side Tube-Side Mass Flow (lbm/hr) 70,628.98 37,262.2(Inlet Temperature (0 F) 148.00 117.4z Outlet Temperature (0 F) 141.01 120.7(Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 144.50 119.1(Skin Temperature (0 F) 125.96 121.81 Velocity *** 3,552.94 2.9 Reynold's Number 838** 20,93.Prandtl Number 0.7254 3.668 Bulk Visc (lbm/fthr) 0.0490 1.358(Skin Visc (lbrn/ft-hr) 1.3231 Density (Ibm/ft 3) 0.0623 61.725(Cp (BTU/lbm 0'F) 0.2402 0.9981 K (BTU/hr-ft.°F) 0.0162 0.369** Reynolds Number Outside Range of Equation Applicability 5 7 Tube-Side hi (BTU/hr-ft 2-F) 1,007.00 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2-F) 8.52 Tube Wall Resistance (hr-ft2. F/BTU' 0.00031430 Overall Fouling (hr ft 2-F/BTU) 0.02832467 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)5.70 860.06 25.22 123,549 0.9162 123,549 Calculation No.97-200 Revision No. AOO Attachment g Page No. a4 of S,7 Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 18:12:37 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYO @, 104 F, DESIGN FF, 5% PLUG 04/24/02'I Extrapolation Calculation for Row 2(Dry)II II1~Mass Flow (lbm/hr)Inlet Temperature

(°F)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature

('F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (Ibm/ft)Cp (BTU/Ilbm'°F)

K (BTU/hr-ft'F)

Air-Side 70,628.98 141.01 134.98 0.0203 0.0203 137.99 121.96 3,552.94 845**0.7260 0.0486 Tube-Side 37,262.20 114.58 117.44 116.01 118.38 2.91 20,325 3.7895 1.3987 1.3672 61.7725 0.9988 0.3687 Tube-Side hi (BTU/hr-ft 2.°F) 990.92 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2'°F) 8.49 Tube Wall Resistance (hr.ft 2.°F/BTU' 0.00031430 Overall Fouling (hrlft 2.°F/BTU) 0.02832467 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)5.67 860.06 21.82 106,500 0.9164 106,500 0.0629 0.2402 0.0161** Reynolds Number Outside Range of Equation Applicability

'M1 II Extrapolation Calculation for Row 3(Dry)II 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/ft'hr)

Skin Visc (ibm/ft-hr)

Density (ibm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hrif1.°F)

Air-Side 70,628.98 134.98 129.78 0.0203 0.0203 132.38 118.50 3,552.94 851*0.7265 0.0483 Tube-Side 37,262.20 112.11 114.58 113.34 115.42 2.91 19,804 3.8991 1.4355 1.4067 61.8119 0.9988 0.3677 Tube-Side hi (BTU/hr-ft2.°F) 976.99 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.46 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2 0-F/BTU) 0.02832467 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)5.65 860.06 18.90 91,897 0.9166 91,897 0.0635 0.2402 0.0160** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment Page No. j s of Ar7 Air Mass Velocity (Lbmihrft-').

Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 18:12:37 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

ComEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY0I @ 104 F, DESIGN FF, 5% PLUG 04/24/02 N .I-Extrapolation Calculation for Row 4(Dry)II I -Air-Side 70,628.98 Tube-Side 37,262.20 Mass Flow (lbm/hr)Inlet Temperature (0 F) 129.78 109.98 Outlet Temperature (7F) 125.29 112.11 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 127.53 111.04 Skin Temperature (7F) 115.52 112.86 Velocity *** 3,552.94 2.91 Reynold's Number 856** 19,358 Prandtl Number 0.7269 3.9979 Bulk Visc (Ibm/f hr) 0.0480 1.4686 Skin Visc (lbm/ft-hr) 1.4424 Density (lbM/ffP) 0.0640 61.8452 Cp (BTU/Ibm'°F) 0.2402 0.9988 K (BTU/hr'ft-F) 0.0159 0.3669** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hr ft 2-'F) 964.92 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.44 Tube Wall Resistance (hr.ft 20.00031430 Overall Fouling (hr-ft 2-0 F/BTU) 0.02832467 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)5.64 860.06 16.37 79,368 0.9168 79,368.1 Extrapolation Calculation for Row 5(Dry)II 1.Mass Flow (lbmrhr)Inlet Temperature

(°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/ftfhr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm'°F)

K (BTU/hr-ft-°F)

Air-Side 70,628.98 125.29 121.40 0.0203 0.0203 123.34 112.94 3,552.94 861*0.7272 0.0477 0.0644 0.2402 0.0158 Tube-Side 37,262.20 108.13 109.98 109.05 110.64 2.91 18,975 4.0866 1.4982 1.4745 61.8733 0.9988 0.3662 Tube-Side hi (BTU/hr-ft 2.°F) 954.45 j Factor 0.0080 Air-Side ho (BTU/hr.ft 2.°F) 8.42 Tube Wall Resistance (hr-ft 2.°F/BTU, 0.00031430 Overall Fouling (hr ft 2-°F/BTU) 0.02832467 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)5.62 860.06 14.19 68,601 0.9170 68,601** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AO0 Attachment Page No. P, of ,,_*** Air Mass Velocity (Lbni/hr fi 2), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average [

18:12:37 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VYOI @- 104 F, DESIGN FF, 5% PLUG 04/24/02 Extrapolation Calculation for Row 6(Dry)II I. *1 Air-Side Tube-Side Mass Flow (lbm/hr) 70,628.98 37,262.20 Inlet Temperature (OF) 121.40 106.54 Outlet Temperature (OF) 118.05 108.13 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 119.72 107.33 Skin Temperature (OF) 110.71 108.72 Velocity *** 3,552.94 2.91 Reynold's Number 865** 18,646 Prandtl Number 0.7274 4.1659 Bulk Vise (Ibm/if hr) 0.0475 1.5246 Skin Vise (ibm/ft-hr) 1.5033 Density (lbm/ft 3) 0.0648 61.8972 Cp (BTU/Ibm-'F) 0.2402 0.9989 K (BTU/hr-ft-°F) 0.0157 0.3656** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hr-fl 2.°F) 945.37 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.41 Tube Wall Resistance (hr-ft 2-°F/BTU' 0.00031430 Overall Fouling (hr-ft 2 1-F/BTU) 0.02832467 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)5.61 860.06 12.30 59,336 0.9171 59,336 V, -FI=Extrapolation Calculation for Row 7(Dry)II I1 Mass Flow (Ibm/hr)Inlet Temperature (OF)Outlet Temperature

(°F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (°F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)

Skin Vise (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm-°F)

K (BTU/hr-ft.°F)

Air-Side 70,628.98 118.05 115.14 0.0203 0.0203 116.59 108.78 3,552.94 869**0.7276 0.0473 0.0651 0.2402 0.0156 Tube-Side 37,262.20 105.16 106.54 105.85 107.06 2.90 18,364 4.2365 1.5481 1.5290 61.9176 0.9989 0.3650 Tube-Side hi (BTU/hr-ft 2.°F) 937.50 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2-F) 8.39 Tube Wall Resistance (hr ft 2.°F/BTU, 0.00031430 Overall Fouling (hr.ft 2.°F/BTU) 0.02832467 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)5.60 860.06 10.67 51,352 0.9172 51,352** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. A00 Attacg hmen. _ _.Page No. ofi*** Air Mass Velocity (Lbnihr-fi 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 18:12:37 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1 (2)VYO IA & 02A -CSCS Equipment Area Cooling Coils VYOI @ 104 F. DESIGN FF, 5% PLUG 04/24/02 11II Extrapolation Calculation for Row 8(Dry)II I -Air-Side 70,628.98 Mass Flow (lbm/hr)Inlet Temperature (0 F) 115.14 Outlet Temperature (0 F) 112.62 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 113.88 Skin Temperature (0 F) 107.11 Velocity *** 3,552.94 Reynold's Number 872**Prandtl Number 0.7278 Bulk Visc (lbm/ftbhr) 0.0471 Skin Visc (lbm/ft-hr)

Density (lbm/ft 3) 0.0654 Cp (BTU/1bm-'F) 0.2402 K (BTU/hr'fti'F) 0.0155** Reynolds Number Outside Range of Equation Tube-Side 37,262.20 103.96 105.16 104.56 105.62 2.90 18,120 4.2992 1.5689 1.5518 61.9349 0.9989 0.3645 Applicability Tube-Side hi (BTU/hr-ft 2.°F) 930.67 j Factor 0.0079 Air-Side ho (BTU/hr-ft1-°F) 8.38 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr fi-'°F/BTU)

0.0 2832467

U Overall (BTU/hr-ft 2-°F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/br)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.59 860.06 9.25 44,466 0.9173 44,466 Calculation No.97-200 Revision No. AO0 Attachment is Page No. _j, of ail*** 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)VY01A 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: W--Pv = (W*Rv*PY(Ra+(W*Rv)

=Pa = P -Pv=rho a = (144/Ra)*(Pa/(459.67+T)

=rho a = (144IRa)*(Pa/(459.67+T)

=T=V =14.315 psia Inlet Air Flow 112.62 F 19113 acfm 0.020274 0.451875 psia Rv = 85.778 (ft-lbf)/(Ibm-R)

Ra = 53.352 (ft-lbf)/(lbm-R) 13.86313 psia 0.0654 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 18000 cfm Calculation No.97-200 Revision No. A00 Attachment a-Page No. _j of -

18:07:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 04/24/02 ComEd -- LaSalle Data Report for: I(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF, 5% PLUG Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 21,179.00 acfm 150.00 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 109.40 OF 115.30 OF Outlet Wet Bulb Temp 84.10 OF Outlet Relative Humidity %Tube Fluid Name Fresh Water Tube Fouling Factor 0.001500 Air-Side Fouling 0.000000 Design Heat Transfer (BTU/hr) 750,000 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 VY Coolers 01 A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]Coil Finned Length (in) 104.250 Fin Pitch (Fins/Inch) 10.000 Fin Conductivity (BTU/hr-fti.F) 128.000 Fin Tip Thickness (inches) 0.0120 Fin Root Thickness (inches) 0.0120 Circular Fin Height (inches) 1.495 Number of Coils Per Unit 2 Number of Tube Rows 8 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) 1.500 Transverse Tube Pitch (in) 1.452 Number of Serpentines 1.000 Tube Wall Conductivity (BTU/hr-ft-°F) 225.00 Calculation No.97-200 Revision No./\00 Attachment Page No. gi of 817 18:07:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/24/02 CornEd -- LaSalle Calculation Report for: l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF, 5% PLUG 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 (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) 108.00 Air Flow (acfm) 19,164.00 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.97-200 Revision No. AO0 Attachment t_Paige No. _p,, of 0r7 18:07:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: I(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF, 5% PLUG 04/24/02 A -11 Extrapolation Calculation Summary 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/ft-hr)

Density (lbm/fl 3)Cp (BTU/lbm-'F)

K (BTU/hr'f 0'F)Air-Side 70,817.44 148.00 111.10 Tube-Side 53,657.57 104.00 116.20 Tube-Side hi (BTU/hr-ft 2.°F)j Factor Air-Side ho (BTU/hr-ft 2-°F)Tube Wall Resistance (hr-fl 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2 0-F/BTU) 0.02832467 U Overall (BTU/hr'ftV"°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)6,880.52 653,739 653,739.I 11 Extrapolation Calculation for Row l(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 (lbm/ft-hr)

Skin Visc (Ibm/ft hr)Density (Ibm/ft 3)Cp (BTU/lbm-°F)

K (BTU/hr'ftb'F)

Air-Side 70,817.44 148.00 139.81 0.0203 0.0203 143.90 122.15 3,562.42 841 0.7255 0.0490 0.0624 0.2402 0.0162 Tube-Side 53,657.57 113.50 116.20 114.85 117.28 4.19 28,941 3.8364 1.4145 1.3817 61.7897 0.9988 0.3683 Tube-Side hi (BTU/hr-ft 2.0 F) 1,318.81 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2 f-F) 8.53 Tube Wall Resistance (hr-ft 2-°F/BTU, 0.00031430 Overall Fouling (hr ft 2-°F/BTU) 0.02832467 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)5.85 860.06 28.85 145,141 0.9161 145,141** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment Page No. _ of orl*** Air Mass Velocity (Lbm/hr ft 2). Tube Fluid Velocity (ft/sec);

Air Density at Inlet T. Other Properties at Average T 18:07:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

ComEd -- LaSalle Calculation Report for: l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF, 5% PLUG 04/24/02.1 Extrapolation Calculation for Row 2(Dry)II~1 Air-Side Tube-Side Mass Flow (lbrn/hr) 70,817.44 53,657.5 Inlet Temperature (0 F) 139.81 111.2 Outlet Temperature (0 F) 133.05 113.5 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (7F) 136.43 112.3 Skin Temperature (7F) 118.43 114.4 Velocity *** 3,562.42 4.1 Reynold's Number 849** 28,24 Prandtl Number 0.7262 3.940 Bulk Visc (lbm/ft-hr) 0.0485 1.449 Skin Visc (Ibm/ift-hr) 1.420 Density (Ibm/fi 3) 0.0631 61.826 Cp (BTU/lbm-°F) 0.2402 0.998.K (BTU/hr-ft-°F) 0.0161 0.367** Reynolds Number Outside Range of Equation Applicability 7 6 0 Tube-Side hi (BTU/hr-ft 2-°F) 1,301.27 j Factor 0.0080 Air-Side ho (BTU/hr.ft 2.°F) 8.50 Tube Wall Resistance (hr-ft 2.°F/BTU, 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 8 1 9 8 0 3 6 0 8 4 U Overall (BTU/hr.ft2-°F)

Effective Area (fl)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.83 860.06 23.88 119,696 0.9163 119,696 Extrapolation Calculation for Row 3(Dry)ii*1 Mass Flow (lbm/hr)Inlet Temperature (fF)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/ft 3)Cp (BTU/lbm.°F)

K (BTU/hr.ft-°F)

Air-Side 70,817.44 133.05 127.47 0.0203 0.0203 130.26 115.35 3,562.42 855**0.7267 0.0481 0.0637 0.2402 0.0159 Tube-Side 53,657.57 109.42 111.26 110.34 112.04 4.19 27,680 4.0288 1.4790 1.4541 61.8552 0.9988 0.3667 Tube-Side hi (BTU/hr.ft 2-°F) 1,286.74 j Factor 0.0080 Air-Side ho (BTU/hr.ft 2.°F) 8.47 Tube Wall Resistance (hr-ft 2.°F/BTU, 0.00031430 Overall Fouling (hrfit 2 f.F/BTU) 0.02832467 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)5.81 860.06 19.78 98,838 0.9166 98,838** Reynolds Number Outside Range of Equation Applicability Calctilation No.97-200 Revision No. AGO Attachment g Page No. a of t Ofil*** Air Mass Velocity (L.bm/hr-ft 2), Tube Fluid Velocity (ft'sec);

Air Density at Inlet T, Other Properties at Average T 18:07:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VY02 Ca) 104 F, DESIGN FF, 5% PLUG 04/24/02 Ki Extrapolation Calculation for Row 4(Dry)HI 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 (ibm/ft hr)Skin Visc (ibm/f hr)Density (lbm/ft 3)Cp (BTU/lbm-'F)

K (BTU/hr'ft-'F)

Air-Side 70,817.44 127.47 122.86 0.0203 0.0203 125.17 112.81 3,562.42 861*0.7270 0.0478 Tube-Side 53,657.57 107.89 109.42 108.65 110.07 4.18 27,214 4.1047 1.5043 1.4829 61.8789 0.9988 0.3661 Tube-Side hi (BTU/hr-ft2-°F) 1,274.71 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.45 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.79 860.06 16.40 81,701 0.9168 81,701 0.0642 0.2402 0.0158** Reynolds Number Outside Range of Equation Applicability ON"- -Extrapolation Calculation for Row 5(Dry)II 1.Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature

("F)Inlet Specific Humidity Outlet Specific Humidity Average Temp ('F)Skin Temperature (7F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/lfthr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/1bm'°F)

K (BTU/hr.ft.°F)

Air-Side 70,817.44 122.86 119.04 0.0203 0.0203 120.95 110.71 3,562.42 866**067273 0.0475 Tube-Side 53,657.57 106.63 107.89 107.26 108.44 4.18 26,831 4.1693 1.5258 1.5075 61.8982 0.9989 0.3655 Tube-Side hi (BTU/hr-ft 2.°F) 1,264.72 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2"'F) 8.43 Tube Wall Resistance (hr-ft 2-0 F/BTU' 0.00031430 Overall Fouling (hr.ft 2.0 F/BTU) 0.02832467 U Overall (BTU/hrft 2-1F)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)5.78 860.06 13.59 67,596 0.9169 67,596 0.0647 0.2402 0.0157** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment

>Page No. 1 ot' ff_8*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T. Other Properties at Average T 18:07:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF, 5% PLUG 04/24/02.1 Extrapolation Calculation for Row 6(Dry)II 11 ..Air-Side 70,817.44 Tube-Side 53,657.57 Mass Flow (lbm/hr)Inlet Temperature (0 F) 119.04 105.5'Outlet Temperature (0 F) 115.88 106.6: Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (7F) 117.46 106.1 Skin Temperature (0 F) 108.97 107.0'Velocity *** 3,562.42 4.1 Reynold's Number 870** 26,51.Prandtl Number 0.7276 4.223 Bulk Visc (lbm/ftrhr) 0.0473 1.5441 Skin Visc (Ibm/ft hr) 1.528, Density (Ibm/f') 0.0650 61.9141 Cp (BTU/Ibm-°F) 0.2402 0.998'K (BTU/hr'ft'-F) 0.0156 0.365** Reynolds Number Outside Range of Equation Applicability 9 3 Tube-Side hi (BTU/hrft 2 0.'F) 1,256.44 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.0 F) 8.41 Tube Wall Resistance (hr-ft2.°F/BTU, 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 1 9 8 5 9 0 4 0 9 1 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)5.77 860.06 11.28 55,967 0.9171 55,967.1 Extrapolation Calculation for Row 7(Dry)11 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 (lbm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm-'F)

K (BTU/hr'ft--F)

Air-Side 70,817.44 115.88 113.27 0.0203 0.0203 114.58 107.53 3,562.42 873**0.7278 0.0471 0.0653 0.2402 0.0156 Tube-Side 53,657.57 104.72 105.59 105.15 105.97 4.18 26,255 4.2701 1.5593 1.5461 61.9269 0.9989 0.3648 Tube-Side hi (BTU/hr-ft 2-F) 1,249.57 j Factor 0.0079 Air-Side ho (BTU/hr.ft 2.`F) 8.40 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2.F/BTU) 0.02832467 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)5.76 860.06 9.36 46,367 0.9172 46,367** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. A00 Attachment t Page No. B15y of g,;*** Air Mass Velocity (Lbnmhr-ft).

Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 18:07:06 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ 104 F, DESIGN FF, 5% PLUG 04/24/02 I. ii Extramolation Calculation for Row 8(Dry)II It 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/ft-hr)

Skin Visc (lbm/fI-hr)

Density (lbm/ft 3)Cp (BTU/lbm-'F)

K (BTU/hr'ft'°F)

Air-Side 70,817.44 113.27 111.10 0.0203 0.0203 112.18 106.34 3,562.42 876**0.7279 0.0470 0.0656 0.2402 0.0155 Tube-Side 53,657.57 104.01 104.72 104.36 105.05 4.18 26,039 4.3090 1.5722 1.5610 61.9375 0.9989 0.3645 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-.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)1,243.87 0.0079 8.39 0.00031430

0.0 2832467

5.75 860.06 7.76 38,433 0.9173 38,433** Reynolds Number Outside Range of Equation Applicability Calculation No.97-100 Revision No. AOO Attachment 13 Page No. Bit of arl*** 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)VY02A Total P: P=Dry Bulb T OUT: T=Specific Hum.: W H20 Yap 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)*(PaJ(459.67+T)

=Dry Bulb T IN: T=Outlet Air Flow: V =14.315 psia Inlet Air Flow 111.1 F 19164 acfm 0.020274 0.451875 psia Rv = 85.778 (ft-lbf)/(Ibm-R)

Ra = 53.352 (ft-lbf)/(lbm-R) 13.86313 psia 0.0656 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 18000 cfm Calculation No.97-200 Revision No. AO0 Attachment Page No. _ oi:_O_

CornEd CALCULATION NO.97-200 REVISION NO. AOO PAGE NO. C1 of C17 Attachment "C" Proto-Hx Calc. Report for 1(2)VY01A

& 1(2)VY02A (For VY01, CSCS=104 0 F @ Max. Allowable FF, w\ 5% plugged)(For VY02, CSCS=104 0 F @ Design FF, Room Temp. = 150 0 F)I E-FORM I 18:21:26 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Data Report for: l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY01 @ MAX FF, w\ 5% PLUG 04/24/02 I Air Coil Heat Exchanger Input Parameters I 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 21,179.00 acfm 150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side 150.00 gpm 105.00 OF 115.30 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.°F)

Fresh Water 0.005000 0.000500 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 19.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Calculation No.97-200 Revision No. A00 Attachment c Page No. 6z- of , i 18:21:26 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/24/02 ComEd -- LaSalle Calculation Report for: l(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VY01 @ MAX FF., w\ 5% PLUG 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) 75.00 Air Flow (acfm) 18,982.00 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.97-200 Revision No. AGO Attachment c Page No. "3e of tc-18:21:26 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VY01 @ MAX FF, w\ 5% PLUG 04/24/02 U, Extrapolation Calculation Summary 1i Air-Side Mass Flow (ibm/hr) 70,144.89 Inlet Temperature (IF) 148.00 Outlet Temperature (IF) 116.55 Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/fthr)

Skin Visc (ibm/ftuhr)

Density (Ibm/fl 3)Cp (BTU/1bm.°F)

K (BTU/hr'ft'°F)

Tube-Side 37,262.20 104.00 118.87 Tube-Side hi (BTU/hr ft 2.°F)j Factor Air-Side ho (BTU/hr-ft2-°F)

Tube Wall Resistance (hr- ft 2-F/BTU Overall Fouling (hr-ft 2.0 F/BTU)U Overall (BTU/hr-ft 2-°F)Effective Area (ft 2)LMTD Total Heat Transf~rred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.00031430

0.0 9491556

6,880.52 551,834 551,834 Di Extrapolation Calculation for Row l(Dry)II I.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 Visc (lbm/ft-hr)

Skin Visc (Ibm/ft-hr)

Density (Ibm/ft 3)Cp (BTU/Ibm-F)

K (BTU/hrift.°F)

Air-Side 70,144.89 148.00 142.44 0.0203 0.0203 145.22 130.56 3,528.59 831*0.7254 0.0491 0.0622 0.2402 0.0162 Tube-Side 37,262.20 116.24 118.87 117.56 119.71 2.91 20,630 3.7281 1.3780 1.3501 61.7492 0.9988 0.3692 Tube-Side hi (BTU/hr-ft 2-°F) 998.47 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2-F) 8.48 Tube Wall Resistance (hr-ft 2 .F/BTU, 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.09491556 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)4.12 860.06 27.55 97,604 0.9165 97,604** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment C.Page No. 4 of !, 7*** Air Mass Velocity (Lbm/hr fi 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 18:21:26 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils VYO0 @ MAX FF, w\ 5% PLUG 04/24/02 Extrapolation Calculation for Row 2(Dry) I Air-Side Tube-Side Mass Flow (lbm/hr) 70,144.89 37,262.20 Tube-Side hi (BTU/hr-ft2.°F) 985.60 Inlet Temperature (OF) 142.44 113.89 j Factor 0.0081 Outlet Temperature (OF) 137.45 116.24 Air-Side ho (BTU/hr-ft 2"°F) 8.46 Inlet Specific Humidity 0.0203 Tube Wall Resistance (hr-ft 2.°F/BTU, 0.00031430 Outlet Specific Humidity 0.0203 Overall Fouling (hr-ft 2.°F/BTU) 0.09491556 Average Temp (OF) 139.94 115.07 Skin Temperature (OF) 126.76 117.03 U Overall (BTU/hr.ft 2"°F) 4.11 Velocity *** 3,528.59 2.91 Effective Area (ft 2) 860.06 Reynold's Number 837** 20,141 LMTD 24.78 Prandtl Number 0.7259 3.8275 Total Heat Transferred (BTU/hr) 87,561 Bulk Visc (lbm/ft-hr) 0.0487 1.4115 Skin Visc (lbm/ft'hr) 1.3851 Surface Effectiveness (Eta) 0.9167 Density (lbm/ft 3) 0.0627 61.7865 Sensible Heat Transferred (BTU/hr) 87,561 Cp (BTU/lbm'°F) 0.2402 0.9988 Latent Heat Transferred (BTU/hr)K (BTU/hr'ft-'F) 0.0161 0.3683 Heat to Condensate (BTU/hr)** Reynolds Number Outside Range of Equation Applicability L Extrapolation Calculation for Row 3(Dry)Air-Side Tube-Side Mass Flow (lbm/hr) 70,144.89 37,262.20 Inlet Temperature (OF) 137.45 111.78 Outlet Temperature

(°F) 132.97 113.89 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (°F) 135.21 112.84 Skin Temperature

(°F) 123.35 114.61 Velocity *"*

3,528.59 2.91 Reynold's Number 842** 19,705 Prandtl Number 0.7263 3.9205 Bulk Visc (lbm/ft-hr) 0.0484 1.4427 Skin Visc (Ibm/ft-hr) 1.4178 Density (Ibm/ft 3) 0.0632 61.8193 Cp (BTU/lbm'°F) 0.2402 0.9988 K (BTU/hr'ft'°F) 0.0160 0.3676** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hr-ft 2.°F) 974.02 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2"°F) 8.44 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2"°F/BTU) 0.09491556 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)4.10 860.06 22.28 78,587 0.9169 78,587 Calculation No.97-200 Revision No. AOO Attachment Co Page No. C_!;_ of c_gL!*** Air Mass Velocity (Lbbm/hr'ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 18:21:26 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VYOlIA

& 02A -CSCS Equipment Area Cooling Coils VYQ I @ MAX FF, w\ 5% PLUG 04/24/02 Extrapolation Calculation for Row 4(Dry)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 (Ibm/ft-hr)

Skin Visc (lbm/lf-hr)

Density (Ibm/fl 3)Cp (BTU/lbm-°F)

K (BTU/hr'fti'F)

Air-Side 70,144.89 132.97 128.95 0.0203 0.0203 130.96 120.29 3,528.59 846**0,7266 0.0482 Tube-Side 37,262.20 109.88 111.78 Tube-Side hi (BTU/hr-ft 2.°F) 963.58 j Factor 0.0080 Air-Side ho (BTU/hr ft 2 .F) 8.42 Tube Wall Resistance (hr-ft2.°F/BTU'

0.0 0031430

Overall Fouling (hr-ft 2.°F/BTU) 0.09491556 110.83 112.45 2.91 19,317 4.0071 1.4717 1.4483 61.8482 0.9988 0.3668 U Overall (BTU/hr-fl 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)4.09 860.06 20.05 70,561 0.9170 70,561 0.0636 0.2402 0.0159** Reynolds Number Outside Range of Equation Applicability t?4i~U.Extrapolation Calculation for Row 5(Dry)II I. *1 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/1bm'°F)

K (BTU/hr-ftV'F)

Air-Side 70,144.89 128.95 125.34 0.0203 0.0203 127.14 117.54 3,528.59 851**0.7269 0.0479 0.0640 0.2402 0.0158 Tube-Side 37,262.20 108.18 109.88 109.03 110.50 2.91 18,971 4.0875 1.4986 1.4766 61.8736 0.9988 0.3662 Tube-Side hi (BTU/hr-ft 2-°F) 954.18 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.40 Tube Wall Resistance (hrft 2.°F/BTU, 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.09491556 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)4.09 860.06 18.04 63,378 0.9172 63,378** Reynolds Number Outside Range of Equation Applicability Calculation No.97-100 Revision No. AOO Attachment C Page No. c! of(t,-*** Air Mass Velocity (Lbmihr-fth), Tube Fluid Velocity (ftlsec);

Air Density at Inlet T. Other Properties at Average T 18:21:26 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: I(2)VYO0A

& 02A -CSCS Equipment Area Cooling Coils VY01 @ MAX FF, w\ 5% PLUG 04/24/02 I Extrapolation Calculation for Row 6(Dry)II I -Air-Side Mass Flow (lbm/hr) 70,144.89 Inlet Temperature (OF) 125.34 Outlet Temperature (OF) 122.09 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 123.71 Skin Temperature (OF) 115.07 Velocity *** 3,528.59 Reynold's Number 855**Prandtl Number 0.7272 Bulk Visc (Ibm/ft-hr) 0.0477 Skin Vise (lbm/ft-hr)

Density (lbmr/ft) 0.0643 Cp (BTU/lbm-°F) 0.2402 K (BTU/hr'f 0'F) 0.0158 Tube-Side 37,262.20 106.65 108.18 107.42 108.74 2.91 18,662 4.1621 1.5234 1.5029 61.8961 0.9989 0.3656 Tube-Side hi (BTU/hr'.ft2 .F) 945.71 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.39 Tube Wall Resistance (hr-ft 2 -F/BTU, 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.09491556 U Overall (BTU/hr-ft 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)4.08 860.06 16.23 56,946 0.9173 56,946** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)II I.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'°F)

K (BTU/hr-ftV.F)

Air-Side 70,144.89 122.09 119.17 0.0203 0.0203 120.63 112.86 3,528.59 858**0.7274 0.0475 0.0647 0.2402 0.0157 Tube-Side 37,262.20 105.28 106.65 105.96 107.17 2.90 18,386 4.2309 1.5463 1.5273 61.9160 0.9989 0.3651 Tube-Side hi (BTU/hr ft2.OF) 938.08 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.37 Tube Wall Resistance (hr-ft 2-°F/BTU, 0.00031430 Overall Fouling (hr.ffl.°F/BTU)

0.0 9491556

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)4.07 860.06 14.61 51,182 0.9174 51,182** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment

_L Page No. c- of C/1*** Air Mass Velocity (Lbm/hr-ft'), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 18:21:26 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VYOI @ MAX FF, w\ 5% PLUG 04/24/02 a m.ii Extrapolation Calculation for Row 8(Dry)II Air-Side Mass Flow (lbm/hr) 70,144.89 Inlet Temperature

('F) 119.17 Outlet Temperature (0 F) 116.55 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (*F) 117.86 Skin Temperature (0 F) 110.86 Velocity *** 3,528.59 Tube-Side 37,262.20 104.04 105.28 Tube-Side hi (BTU/hr'ft2-°F) 931.21 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.36 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2"°F/BTU) 0.09491556 104.66 105.75 2.90 Reynold's Number 861** 18,13t Prandtl Number 0.7276 4.294, Bulk Visc (Ibm/f hr) 0.0473 1.5671 Skin Visc (Ibm/ft hr) 1.549'Density (lbm/Ift 3) 0.0650 61.933 Cp (BTU/1bm'°F) 0.2402 0.9985 K (BTU/hrift-°F) 0.0156 ** Reynolds Number Outside Range of Equation Applicability 8 7 5 9 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)4.07 860.06 13.15 46,015 0.9175 46,015 Calculation No.97-200 Revision No. AOO Attachment C Page No. .( of C/7*** Air Mass Velocity (Lbm/hrIffV).

Tube Fluid Velocity (ft/see);

Air Density at Inlet T, Other Properties at Average T Inlet Air Flowrate Calculator

-1(2)VY01A 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: 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=14.315 psia Inlet Air Flow 116.55 F 18982 acfm 0.020274 0.451875 psia Rv = 85.778 (ft-lbf)/(Ibm-R)

Ra = 53.352 (ft-lbf)/(Ibm-R) 13.86313 psia 0.0649 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 18000 cfm Calculation No.97-200 Revision No. AOO Attachment c Page No. .!i of r-_r 19:37:17 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 04/24/02 ComEd -- LaSalle Data Report for: l(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ CSCS= 104 F, ROOM T= 150 F Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fluid Quantity, Total 21,179.00 acfm 150.00 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 109.40 OF 115.30 OF Outlet Wet Bulb Temp 84.10 OF Outlet Relative Humidity %Tube Fluid Name Fresh Water Tube Fouling Factor 0.001500 Air-Side Fouling 0.000000 Design Heat Transfer (BTU/hr) 750,000 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 VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]Coil Finned Length (in) 104.250 Fin Pitch (Fins/Inch) 10.000 Fin Conductivity (BTU/hrlft.°F) 128.000 Fin Tip Thickness (inches) 0.0120 Fin Root Thickness (inches) 0.0120 Circular Fin Height (inches) 1.495 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) 1.452 Number of Serpentines 1.000 Tube Wall Conductivity (BTU/hr-ft.°F) 225.00 Calculation No.97-200 Revision No. AOO Attachment c Page No. c i. of C(I 19:37:17 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371) 4/24/02 CornEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ CSCS=104 F, ROOM T=150 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 (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 Tube Flow (gpm)Tube Temp In ('F)Tube Temp Out (°F)Condensate Temperature

('F)Extrapolation Data Tube Flow (gpm) 108.00 Air Flow (acfm) 19,162.00 Tube Inlet Temp ('F) 104.00 Air Inlet Temp ('F) 150.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp ('F) 0.00 Atmospheric Pressure 14.315 Calculation No.97-200 Revision No. AQO Attachment L-Page No. cii of t,7 19:37:17 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: I(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ CSCS=104 F, ROOM T=150 F 04/24/02 ml. II I Extrapolation Calculation Summary II 1.Air-Side Mass Flow (lbm/hr) 70,460.57 Inlet Temperature (IF) 150.00 Outlet Temperature (IF) 111.14 Inlet Specific Humidity Outlet Specific Humidity Average Temp (IF)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm./fthr)

Skin Visc (lbm/ftfhr)

Density (lbmlft)Cp (BTU/Ibm-°F)

K (BTU/hr-ft-°F)

Tube-Side 53,657.57 104.00 116.85 Tube-Side hi (BTU/hr.ft 2-°F)j Factor Air-Side ho (BTU/hr1ft2.°F)

Tube Wall Resistance (hr-ft 2.°F/BTU, 0.00031430 Overall Fouling (hr-ft 2.0 F/BTU) 0.02832467 U Overall (BTU/hrft2-°OF)

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)7,242.65 686,379 686,379 M Extrapolation Calculation for Row l(Dry)II 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 Visc (lbm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm'°F)

K (BTU/hr'ft'°F)

Air-Side 70,460.57 150.00 141.26 0.0213 0.0213 145.63 122.89 3,367.24 793**0.7253 0.0491 0.0622 0.2402 0.0163 Tube-Side 53,657.57 113.97 116.85 115.41 117.96 3.98 27,644 3.8137 1.4069 1.3727 61.7815 0.9988 0.3685 Tube-Side hi (BTU/hr-ft 2-.F) 1,269.63 j Factor 0.0082 Air-Side ho (BTU/hr ft 2.°F) 8.23 Tube Wall Resistance (hr'ft.°F/BTU'

0.0 0031430

Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.69 905.33 30.00 154,454 0.9187 154,454** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment

_.PageNo. Liz of oil*** Air Mass Velocity (Lbm/hr&ft'), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 19:37:17 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: I(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ CSCS= 104 F. ROOM T= 150 F 04/24/02 I Extrapolation Calculation for Row 2(Dry) I 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/Ibm 0'F)K (BTU/hr-ft'°F)

Air-Side 70,460.57 141.26 134.08 0.0213 0.0213 137.67 118.95 3,367.24 801**0.7260 0.0486 Tube-Side 53,657.57 111.60 113.97 112.78 114.91 3.98 26,943 3.9226 1.4434 1.4137 61.8201 0.9988 0.3675 Tube-Side hi (BTU/hrI'ft 2 -.F) 1,251.77 j Factor 0.0082 Air-Side ho (BTU/hr'ft 2.'F) 8.19 Tube Wall Resistance (hr'ft 2 00.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 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)5.66 905.33 24.70 126,678 0.9190 126,678 0.0629 0.2402 0.0161** Reynolds Number Outside Range of Equation Applicability

.1 Extrapolation Calculation for Row 3(Dry)II I.Mass Flow (lbm/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 Vise (lbm/ft-hr)

Density (Ibm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr-ft-°F)

Air-Side 70,460.57 134.08 128.19 0.0213 0.0213 131.14 115.71 3,367.24 808**0.7266 0.0482 0.0636 0.2402 0.0159 Tube-Side 53,657.57 109.66 111.60 110.63 112.40 3.98 26,373 4.0159 1.4746 1.4490 61.8510 0.9988 0.3668 Tube-Side hi (BTU/hr.ft 2.F) 1,237.05 j Factor 0.0082 Air-Side ho (BTU/hr'ft-'°F) 8.17 Tube Wall Resistance (hr ft 2 .F/BTU' 0.00031430 Overall Fouling (hr'ft 2-F/BTU) 0.02832467 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)5.65 905.33 20.36 104,043 0.9193 104,043** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment

_CZ Page No. zi of c i7 Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet Tr. Other Properties at Average T 19:37:17 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: I(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils VY02 @ CSCS=104 F, ROOM T=150 F 04/24/02 a..Extrapolation Calculation for Row 4(Dry)11 II *Air-Side Tube-Side Mass Flow (lbm/hr) 70,460.57 53,657.5-Inlet Temperature

(°F) 128.19 108.0(Outlet Temperature

(°F) 123.35 109.6(Inlet Specific Humidity 0.0213 Outlet Specific Humidity 0.0213 Average Temp (IF) 125.77 108.8(Skin Temperature (IF) 113.06 110.3-2 Velocity *** 3,367.24 3.9ýReynold's Number 813** 25,90ýPrandtl Number 0.7270 4.095_2 Bulk Visc (lbm/ft.hr) 0.0478 1.5011 Skin Visc (lbm/ftrhr) 1.4791 Density (lbm/ft 3) 0.0641 61.876(Cp (BTU/lbm-°F) 0.2402 0.998K K (BTU/hr'ft'°F) 0.0158 0.3661** Reynolds Number Outside Range of Equation Applicability 7 Tube-Side hi (BTU/hr-ft 2-°F) 1,224.91 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2"°F) 8.14 Tube Wall Resistance (hr'ft 2_-F/BTU' 0.00031430 Overall Fouling (hr-ft2-°F/BTU)

0.0 2832467

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)5.63 905.33 16.79 85,551 0.9195 85,551.1 Extrapolation Calculation for Row 5(Dry)II Mass Flow (lbm/hr)Inlet Temperature

("F)Outlet Temperature

("F)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 (lbm/ftihr)

Density (Ibm/ft 3)Cp (BTU/bm-°F)

K (BTU/hr-ft.°F)

Air-Side 70,460.57 123.35 119.36 0.0213 0.0213 121.36 110.87 3,367.24 818*4 0.7273 0.0476 Tube-Side 53,657.57 106.75 108.06 Tube-Side hi (BTU/hr-ft 2.°F) 1,214.90 j Factor 0.0081 Air-Side ho (BTU/hrf 2-°F) 8.12 Tube Wall Resistance (hr-ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 107.41 108.63 3.97 25,527 4.1625 1.5235 1.5047 61.8962 0.9989 0.3656 U Overall (BTU/hr-fi 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)5.62 905.33 13.85 70,414 0.9196 70,414 0.0645 0.2402 0.0157** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment

(_Page No. /4 of e it*** Air Mass Velocity (Lbm/hrtt), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average T 19:37:17 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: 1(2)VYO I A & 02A -CSCS Equipment Area Cooling Coils VY02 @ CSCS= 104 F, ROOM T= 150 F 04/24/02-2 Extrapolation Calculation for Row 6(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 (Ibm/ft-hr)

Skin Visc (lbm/ft-hr)

Air-Side 70,460.57 119.36 116.08 0.0213 0.0213 117.72 109.07 3,367.24 822**0.7276 0.0473 Tube-Side 53,657.57 105.67 106.75 106.21 107.22 3.97 25,215 4.2192 1.5424 1.5264 Tube-Side hi (BTU/hr-ft 2-°F) 1,206.63 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.F) 8.11 Tube Wall Resistance (hr.ft 2.°F/BTU' 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.61 905.33 11.43 58,002 0.9198 58,002 Density (lbm/ft 3) 0.0649 61.9126 Cp (BTU/lbm'°F) 0.2402 0.9989 K (BTU/hr'fR'F) 0.0156 0.3651** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)II Air-Side 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-0 F)K (BTU/hr-fi'°F) 70,460.57 116.08 113.37 0.0213 0.0213 114.73 107.58 3,367.24 825**0.7278 0.0471 Tube-Side 53,657.57 104.78 105.67 Tube-Side hi (BTUihrft2.°IF) 1,199.81 j Factor 0.0081 Air-Side ho (BTU/hr ft2.°F) 8.10 Tube Wall Resistance (hr-ft 2-°F/BTU' 0.00031430 Overall Fouling (hr.ft 2.F/BTU) 0.02832467 105.22 106.06 3.97 24,959 4.2668 1.5582 1.5447 61.9260 0.9989 0.3648 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)5.60 905.33 9.43 47;809 0.9199 47,809 0.0652 0.2402 0.0156** Reynolds Number Outside Range of Equation Applicability Calculation No.97-200 Revision No. AOO Attachment C Page No. c/i- of 0 7 Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (fiisec);

Air Density at Inlet T, Other Properties at Average T 19:37:17 PROTO-HX 3.01 by Proto-Power Corporation (SN#663-7371)

CornEd -- LaSalle Calculation Report for: I(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils VY02 @ CSCS=104 F, ROOM T=150 F 04/24/02 I. ii Extrapolation Calculation for Row 8(Dry)II 11 Air-Side Tube-Side Mass Flow (lbm/hr) 70,460.57

/ 3,657/.57 Inlet Temperature (OF) 113.37 104.04 Outlet Temperature (OF) 111.14 104.78 Inlet Specific Humidity 0.0213 Outlet Specific Humidity 0.0213 Average Temp (OF) 112.26 104.41 Skin Temperature (OF) 106.36 105.1(Velocity *** 3,367.24 3.9'Reynold's Number 828** 24,74S Prandtl Number 0.7279 4.3068 Bulk Visc (lbmr/fthr) 0.0470 1.5714 Skin Visc (ibm/ft hr) 1.5601 Density (lbn/ft 3) 0.0655 61.936S Cp (BTU/lbm'°F) 0.2402 0.998S K (BTU/hr'f:'°F) 0.0155 0.3645** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hr-ft 2.°F) 1,194.18 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2-°F) 8.09 Tube Wall Resistance (hr-ft 2 -F/BTU' 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 U Overall (BTU/hr-ft 2.OF)Effective Area (ftf)LMTD Total Heat Transferrcd (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.59 905.33 7.79 39,429 0.9200 39,429 Calculation No.97-200 Revision No. AOO Attachment P_Page No. C_'b of C¢jI*** 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)VY02A 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: 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 =14.315 psia Inlet Air Flow 111.14 F 19162 acfrn 0.020274 0.451875 psia Rv = 85.778 (ft-lbf)/(Ibm-R)

Ra = 53.352 (ft-lbf)/(lbm-R) 13.86313 psia 0.0656 Ibm/ft 3 0.061575 Ibm/ft 3 148 F 18000 cfm Calculation No.97-200 Revision No. A00 Attachment C Page No. CJ of C 1i A-4 PROTO-POWER CORPORATION CALCULATION TITLE SHEET CLIENT: PROJECT: Commnonwealth Edison LaSalle Station GL 89-13 Heat Exchanger Testing Program CALCULATION TITLE: CALCULATION NO.: VY Cooler Thermal Performance Model -- 1(2)VYOIA and 1(2) VYO2A 97-200 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 205 Lloyd Philpot Merid Above, Page i of vi Form No.: P1050101 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE II OF vi GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOB NO.31-003 CLIENT Commonwealth Edison IROJEc LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VYO1A and 1(2)VY02A 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 CALCINO.97-200 REV A 'AGE ill OF vi GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 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)VYO1A and I(2)VY02A CALCULATION VERIFICATION FORM REVIEW METHOD: Approach Checked: Logic Checked: Arithmetic Checked: Alternate Method (Attach Brief Summary)Computer Program Used (Attach Listing)Other EXTENT OF VERIFICATION:

Complete Calculation:

Elf-N/A N/A N/A N/A El El E]0-1 Revised areas only: Other (describe below): E3 El[7 N/A [E E-1 N/A *Errors Detected*Error Resolution S ezA -' .4o .c, 7 -S Vt tý -I.ex-A-etA-I --t' b j 7. A*Other Comments*Extra References Used*(Attach extra sheets if needed)CALCULATION FOUND TO BE VALID AND CONCLUSIONS TO BE CORRECT AND REASONABLE:

IDV Signature:

Printed Name: M6-,q AGc>-7 Initials:

LA:zzi Date: 6/12-1 I'7 Form No.: P1050103 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO.97-200 Rv A PAGE iv O vi GROTON, CONNECTICUT ORIGINAI"OR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOB NO 31-003 CLIEN Commonwealth Edison ',"J' LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Perfor-nance Model -- l(2)VYOIA and I(2)VY02A TABLE OF CONTENTS CA LCULATIO N TITLE SH EET .................................................................................................

i CA LC ULATIO N REV ISIO N H ISTO RY ...................................................................................

ii CAL CU LATIO N V ERIFICATIO N SH EET .............................................................................

iii TA BLE O F CO NTENTS .............................................................................................................

iv LIST O F ATTACH M ENTS ........................................................................................................

A Total Number of Pages in Preface of Calculation:

6 1. PURPO SE ...................................................................................................................................

1 2. BA CK G RO UND ........................................................................................................................

1 3. DESIG N INPUTS ......................................................................................................................

2 4. A PPR O A CH ...............................................................................................................................

5 5. A SSUM PTIO NS .........................................................................................................................

5 6. AN ALY SIS .................................................................................................................................

6 6.1 Tube Pitch ..........................................................................................................................................

6 6.2 Coil Configuration

.............................................................................................................................

6 6.3 Sensible Heat Ratio ............................................................................................................................

7 6.4 Derivation of Benchmarking Inputs .............................................................................................

7 6.5 M odel Benchmarking

.......................................................................................................................

10 6.6 Effective Coil Finned Length ......................................................................................................

14 6.7 Extrapolation Conditions

.................................................................................................................

14 6.8 Therm al M argin Assessment

.....................................................................................................

16 6.9 Lim iting Cooling W ater Flow Analysis ......................................................................................

17 6.10 Fouling Sensitivity Analysis .....................................................................................................

17 7. RESULTS .................................................................................................................................

18 7.1 M odel Benchmarking

.......................................................................................................................

18 7.2 Therm al M argin Analysis ...............................................................................................................

19 7.3 Lim iting Cooling W ater Flow Rate Analysis ............................................................................

19 7.4 Fouling Sensitivity Analysis .......................................................................................................

21 Form No.: P1050104 Rev.: 10 Date: 10121/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE v oF Vi GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 V'ERIFIED M. Aboye Jo0 No 31-003 CLIEN Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TILE VY Cooler Thermal Performance Model -- l(2)VY01A and 1(2)VY02A 8. C O N C LU SIO NS ......................................................................................................................

22 9. RE FER EN C ES .........................................................................................................................

22 Total Number of Pages in Body of Calculation:

23 Form No.: P1050104 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO.97-200 REv A PAGE vi OF vi GROTON, CONNECTICUT R L. Philpot DATE 6/24/98 V-RIFID M. Aboye -oB No.31-003 CLIELN Commonwealth Edison PROJECt LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thenral Performance Model -- 1(2)VYOIA and 1(2)VY02A LIST OF ATTACHMENTS Attachment Subject Matter Total Pages[ A Attachment A to Proto-Power Calculation 97-200 Rev. A: Design Input Data -- Selected References 13 B Attachment B to Proto-Power Calculation 97-200 Rev. A: 3 Cooler Inspection Photographs

-- IVYOIA and IVY02A C Attachment C to Proto-Power Calculation 97-200 Rev. A: 8 PROTO-HX T M Reports -- Initial Benchmark Case D Attachment D to Proto-Power Calculation 97-200 Rev. A: 2 Excerpt from Compact Heat Exchangers, Kays and London E Attachment E to Proto-Power Calculation 97-200 Rev. A: 15 PROTO-HXTM Reports -- Final Benchmark Case F Attachment F to Proto-Power Calculation 97-200 Rev. A: 8 PROTO-HXTM Reports -- Thermal Margin Assessment (Clean)G Attachment G to Proto-Power Calculation 97-200 Rev. A: 8 PROTO-HXTM Reports -- Thermal Margin Assessment (Service)H Attachment H to Proto-Power Calculation 97-200 Rev. A: 13 Derivation of Moist Air Properties I Attachment I to Proto-Power Calculation 97-200 Rev. A: 22 PROTO-HXTr M Reports -- Limiting Flow Analysis J Attachment J to Proto-Power Calculation 97-200 Rev. A: 40 PROTO-HX T 1' Analytical Uncertainty Analysis K Attachment K to Proto-Power Calculation 97-200 Rev. A: 4 Comparing Surface Areas of Spiral and Circular Fins L Attachment L to Proto-Power Calculation 97-200 Rev. A: 6 Walkdown Data for Coil Physical Dimensions M Attachment M to Proto-Power Calculation 97-200 Rev. A: 32 PROTO-HX T Il Reports -- Fouling Sensitivity Analysis N Attachment N to Proto-Power Calculation 97-200 Rev. A: 2 PROTO-HX T Il Model Database Disk (plus disk)Complete Calculation (total number of pages): 205 Form No.: P1050104 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE 1 OF 23 GROTON, CONNECTICUT ORJGINATOR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOB NO.31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Perfonnance Model -- 1 (2)VY0 IA and 1(2)VY02A 1. PURPOSE The purpose of this calculation is to develop a thermal performance analysis model for the Commonwealth Edison (CornEd) LaSalle Station NW and SW cubicle area coolers l(2)VY01A and 1(2)VY02A.

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 below.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°F* Water: 32-500°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 CALCNo 97-00 R A PAGE 2 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 VERIFIED 3Y M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison IPROJR-C LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VY0IA and I(2)VY02A 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 0CFR21, 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.

Table 1: LaSalle Station Reference Conditions Parameter Value Reference*

Heat Rate -- 1(2)VY0IA (BTU/hr) 517,239 2 Heat Rate -- 1(2)VY02A (BTU/hr) 646,235 3 Atmospheric Pressure (in-w.g.)

-0.4 4 Air-Side Inlet Temperature

-- Dry Bulb ('F) 148 4 Fan Volumetric Flow Rate (cfmn) 18,000 18,19 Tube-Side Flow Rate (gpm) 150 5 Tube-Side Inlet Temperature

('F) 100 6*Selected references included as Attachment A

PROTO-POWER CORPORATION CALC NO. 97_200 REV A PAGE 3 OF 23 GROTON, CONNECTICUT oRIGINATOR L. Philpot [DATE 6/24/98 VERIFIID 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)VYOIA and l(2)VYO2A Table 2: Vendor Specified Performance Parameter Value Reference*

Air-Side Fouling Factor (Design) 0 Assumption (I)Air-Side Entering Fluid Flow Rate (scfm) 17,330 7 Air-Side Inlet Dry Bulb Temperature (0 F) 150 7 Air-Side Inlet Wet Bulb Temperature (0 F) 92 7 Air-Side Outlet Dry Bulb Temperature (0 F) 109.4 7 Air-Side Outlet Wet Bulb Temperature

('F) 84.1 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) 150 7 Tube Side Inlet Temperature (0 F) 105 7 Tube Side Outlet Temperature (0 F) 115.3 7 Design Q (BTU/hr) 750,000 7*Selected references included as Attachment A

PROTO-POWER CORPORATION CACNO 97-200 REV A PAGE 4 OF 23 GROTON, CONNECTICUT OIGINAIOR L. Philpot DATE 6/24/98 VERIFIED BY M .Aboye JOB NO. 3 1-003 CLIENT Commonwealth Edison 'RoJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VYOIA and 1(2)VY02A 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) 108.00 -- specified (2) 7 104.25 -- effective (2) 20 Fin Pitch (fins/in) 10.0 7 Fin Material ASTM B209 Aluminum 7 Fin Conductivity (BTU/hr-ft-0 F) 128 16 Fin Thickness (in) 0.012 7 Fin Height (in) 1.495 20 Number of Coils per Unit 2 7 Number of Tube Rows 8 7 Number of Tubes per Row 20 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) 1.452 20 Tube Layout Staggered 20 Number of Serpentines I (i.e., "Full Circuiting")

7 Tube Wall Material SB75 Copper 7 Tube Wall Conductivity (BTU`/hr-ft-°F) 225 12 Sensible Heat Ratio 1 (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.97-200 REV A PAGE 5 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 VFRIFIED 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)VYOIA and l(2)VY02A 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)VY01A/02A 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 Colbum 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 I. The fouling factor specified in Reference (8) is for the tube-side only and design air-side fouling is zero. Future validation of this assumption is not required.2. The slope of the "Colbum 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 each VY Cooler. Future validation of this assumption is not required.4. The VY cooler spiral fin geometry is closely approximated by the PROTO-HXT M circular fin configuration.

This is due to the relatively tight fin pitch configuration resulting in a PROTO-POWER CORPORATION CALCNO.97-200 REV A PAGE 6 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOB NO.31-003 CLIENT Commonwealth Edison I'ROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Perfornance Model -- 1(2)VYOIA and 1(2)VY02A 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'F to the current licensing limit of 148 0 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 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 12.00 inches. Dividing the stack depth evenly between 8 tube rows yields a longitudinal (horizontal) tube pitch of 1.500 inches.6.2 Coil Configuration The coil configuration for modeling coolers l(2)VYOIA and 1(2)VY02A 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 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-HXTM circular fin configuration is negligible.

The negligible difference is illustrated further in Attachment K using a simplified area comparison.

PROTO-POWER CORPORATION CALCNO.97-200 REV A PAGE 7 OF 23 GROTON, CONNECTICUT L. Philpot DATE 6/24/98 Y. M. Aboye JOBl NO.31-003 CLIENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I(2)VY0IA and l(2)VY02A Figu, re 1 Coil Configuration CF-9.05-3/4 J-A jij) 0.7742 1 .75 -4015 C F -9.0 5- 3 / 4 J- A 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 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 17,330 scfin. PROTO-HXTM requires air-side flow rate to be given at actual inlet air conditions (units of ac/hn).

PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE s OF 23 GROTON, CONNECTICUT O[IGINATOR L. Philpot DATE 6/24/98 VERIFIED BY Aboye JOB NO.31-003 C:WENT Commonwealth Edison PROJECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VY0IA and 1(2)VY02A The correction of scfin to acfin is made as follows (holding mass flow rate constant for the defining case): mh = *sfil) X(p~ld ) x (60rinl'where:= (acfm) x x l60min Equation (1)rhI = mass flow (Ibm/hr)scfm volumetric flow rate at standard conditions (ft 3/min)Prad = standard density of 0.075 Ibm/ft 3 acfm = volumetric flow rate at specified (non-standard) conditions (ft 3/min)Pa,:=1 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: (acfmi) = (scfm) x (P~ld)(PGata)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 (17,330 scfm) as well as an actual flow (18,000 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: (p aca) (scfrn) x (Ps)(acfm)-(17,330)0.07500 x 18,000-0.0722 lbiy/f 3 The local atmospheric pressure is found by iterative solution using Reference (14) as shown in Attacluhent H. Pressure input is varied with the specified temperature and humidity conditions PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE 9 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 VRIFIED BY M. Aboye JOB NO.31-003 CLIENT Commonwealth Edison IROJKLc LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VYOIA and 1(2)VY02A held constant until a dry air density of 0.0722 Ibni/ft 3 is reached. The result of the iterative process is as follows: Given ner Reference ( 13)Dry Bulb Temperature:

Relative Humidity: 70.00°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 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 707F 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: Derived per Attachment H Relative Humidity: Specific Humidity: 150.00 0 F 92.007F 14.315 psia 12.18%0.02034 lbmv/lbma PROTO-POWER CORPORATION CALCNO,97-200 R[EVA PAGE 10Ol: 23 GROTON, CONNECTICUT ORIGINArOR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JoB NO 31-003 CL0,ENT Conmmonwealth Edison ,ROJF_i.7 LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I(2)VYOIA and 1(2)VY02A Dry Air Pressure: Vapor Pressure: Dry Air Density: Vapor Density: 13.8617 psia 0.4533 psia 0.06137 lbm/ftA3 0.001248 lbm/ft^3 The actual volumetric flow rate at vendor specified inlet conditions is then calculated as: (acfm) = (scfm) x (P~Id) -(P.atua,)(17,330)0.07500 x 0.06137-21,179 ft~min Summary of PROTO-HXTM lnputs for Model Benchmarkin2 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 150 gpm 105 0 F 21,179 acfmn 150°F 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 Colburn 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.

f i PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE I 10O 23 GROTON, CONNECTICUT

},ORIGINATOR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOB NO.31-003 CLIENT Commonwealth Edison PROJEc LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VY0IA and l(2)VY02A Reference (15) defines the Colburmj-factor as follows.Let: Cpa Specific heat of air (Btu/lbm-0 F)ka = Thermal conductivity of air (Btu/hr-ft-°F) ma = Absolute viscosity of air (lbm/ft-hr) ra = Density of air (ib/flt 3)A =in Minimum air-side flow area (Section 3.3.8) (in2)A1= Frontal Area (Section 3.3.8) (in 2)DH = Hydraulic diameter (Section 3.3.8) (ft)do= Tube outside diameter (in)i = Colbum j-Factor NC= Number of coils per unit NL = Number of active tube rows Qa = Specified air flow rate (acfm)SL = Longitudinal Tube Pitch (in)ST= Transverse Tube Pitch (in)The Prandtl Number for air, Pr,, (a dimensionless parameter), is given by: Pra c- '" P"k,, Equation (3)

PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE 12 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOB NO.31-003 CLIENT Commonwealth Edison PROJE-i LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY01A and 1(2)VY02A The mass flow rate of air per coil, Ma (1bnf,/r), is calculated based on the input total air flow and the number of coils per unit: Ma -60pQ, Nc Equation (4)The bulk-stream mass flux, G (lbm/ hr-ft 2), is: G= 144 M, AMIN Equation (5)The Colburnj-factor is defined in terms of the Stanton Number, Sta, as: j Sta prp / = .Glo Pr 21 3 r G1ý -cp, Equation (6)Therefore, the outside heat transfer coefficient, ho (Btu/hr-ft 2-oF), may be defined in terms of thej-factor: Pr,'Equation (7)Per Reference (15), thej-factor for the various coil configurations tested are provided as functions of the Reynolds Number based on hydraulic diameter, DH(in): i = f(Re 0)where: Re,, = G-D'/" Equation (8)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 slightly greater than the value specified by the manufacturer (see performance run in Attachment C). For this reason, a PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE 13 OF 23 GROTON, CONNECTICUT L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOB NO 31-003 CLIENT Commonwealth Edison PROJECI LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VY0IA and I(2)VY02A new curve relating the Colbumj-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.* A design performance run was then executed using the new Colburn 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.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 0.00758 8000 0.0044 0.00371 i [-~2.5088

-0.3436 *Ln(Re)]Equation (9)Equation (9) was added to the PROTO-HXTM Library for use in conjunction with Area Coolers I(2)VYOIA and 1(2)VY02A.

As noted in Assumption (2) 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-HX T M "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 PROTO-POWER CORPORATION CALCNO.97-200 REV A PAGE 14 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 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)VYOIA and l(2)VY02A 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.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 for all subsequent analysis.

An effective coil finned length of 104.25 inches is used per Reference 20.6.7 Extrapolation Conditions The LaSalle Station Reference Conditions defined in Table I 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 1A, 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 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 PROTO-POWER CORPORATION CALCNO. 97_200 REV A PAGE 15 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98'ERIFIED 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)VYOlA and 1(2)VY02A 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/ft3O 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°F in lieu of 150'F per Assumption 5).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 lbm/ftA3 148.00°F 14.315 psia 91.6 0 F 12.76 %Since fans are constant volume equipment, the air volumetric flow rate of 18,000 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; PROTO-POWER CORPORATION CALCNO.97-200 REV A PAGE 16 Or 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 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)VYO1A and 1(2)VY02A" 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: (cfm 1 i.) =(PoUL) (0.06631929)___(cfmo, ) x -(18,000) x (0.06631929) 19,387 (Fan Temperature=

104.53)(pin) (0.061575103)

Service: (cfmj.) =(cfm ) x ) =(18,000) x (0.06609320)

(0.061575103)

= 19,321 (Fan Temperature

= 106.46)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-HX T M 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 150 gpm 100lF (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 (qciean) is calculated using the benchmarked PROTO-HXrM model and the inlet conditions defined in PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE 17 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOB NO.31-003 CIENT Commonwealth Edison PROlEC." LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thernal Performance Model -- 1(2)VYOI A and 1(2)VY02A Section 6.7 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 (qsei-,ic)-

For the purposes of this thermal margin assessment, thermal margin is defined as follows: Margin (BTU / hi) = q available

-q required Margin (%) q available -q required X 100 q required X 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 is achieved.

For the case of l(2)VY01A, the target thermal margin is approximately 30% with the increased design fouling factors. For the case of 1(2)VY02A, the target thermal margin is approximately 10% with the increased design fouling factors.6.10 Fouling Sensitivity Analysis To assess the sensitivity of the l(2)VYOIA and l(2)VY02A 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 PROTO-POWER CORPORATION cALc No. 97_200 A PAGE 18 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 VERIFIED B' M. Aboye JOB No 31-003 CLIENT Commonwealth Edison IROJEC" LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- 1(2)VY01A and l(2)VY02A capability resulting from each fouling increment is compared to the required heat load to assess the thermal margin. Thernial 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-HXT-l 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) PROTO-HX T M Percent Cooler (BTU/hr) Predicted q (BTU/hr) Difference 1(2)VY0IA 750,000 775,120 +3.35%1(2)VY02A (1) 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 Table 6. The PROTO-HXTM reports associated with the final benchmarking cases are included as Attachment E.Table 6: Final Benchmark Case -- Customized Colburn J-Factor Cooler Design q0) (BTU/hr) Predicted q (BTU/hr) Percent Difference 1(2)VYO0A 750,000 749,965 (2) -0.0047%1(2)VY02A 1(2)VY0 IA 750,000 746,297 (3) -0.49%1(2)VY02A Notes: (1) Heat rate specified by cooler vendor (2) With specified coil tinned length per Reference 7 (benchmarking basis)(3) With effective coil finned length per Reference 20 (subsequent analysis basis)

PROTO-POWER CORPORATION CALC NO.97-200 REv A P^AGE 19 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 VERIFIED B) 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)VY0IA and I(2)VY02A 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 7 below.Table 7: Heat Transfer Capacity Heat Transfer Capacity Fouling Condition (BTU/hr)Clean (f = 0.0000) 779,018 Service (f = 0.0015) 741,876 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 8. The PROTO-HXTM reports associated with the thermal margin assessment are included as Attachments F and G for zero and design fouling conditions, respectively.

Table 8: Thermal Margin at LaSalle Station Reference Conditions (f = 0.0000/0.0015) qrequired qavailable Margin Margin Cooler Fouling (f) (BTU/hr) (BTU/hr) (BTU/hr) (%)1(2)VYOIA zero 517,239 779,018 261,779 50.61 design 517,239 741,876 224,637 43.43 l(2)VY02A zero 646,235 779,018 132,783 20.55 design 646,235 741,876 95,641 14.80 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 l(2)VYO1A coolers and a thermal margin of 10% for the l(2)VY02A 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 PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE 20 OF 23 GROTON, CONNECTICUT ORIGINAIr(E L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye 10o NO.31-003 CLIENT Commonwealth Edison PROJE'C LaSalle Station GL 89-13 Heat Exchanger Testing TTLE VY Cooler Thermal Performance Model -- l(2)VYO1A and l(2)VY02A Table 9. The 108 gpm Case was added as a limiting flow case for 1(2)VY02A since available system flow is limited by pump capability.

The PROTO-HXTM reports associated with the limiting flow analysis for both coolers are included as Attachment I.Table 9: Limiting Cooling Water Flow Rate at Reference Conditions (f= 0.0020/0.0020)

Limiting qrequired qavailable Margin Margin Cooler Flow Rate (BTU/hr) (BTU/hr) (BTU/hr) (%)1(2)VYOIA 75 gpm 517,239 675,177 157,938 30.53 1(2)VY02A 115 gpm 646,235 710,964 64,729 10.02 1(2)VYO2A 108 gpm 646,235 707,030 60,795 9.41 The uncertainty in the analytical methodology used to identify the limiting flow for 1(2)VY02A 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 +/- 4.27 to +/- 4.88% for the ranges of cooling water flow evaluated.

An uncertainty of+/- 4.90% 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 10 below.Table 10: 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)VYO1A 75 gpm 517,239 675,177 30.53 24.14 1(2)VY02A 115 gpm 646,235 710,964 10.02 4.62 1(2)VY02A 108 gpm 646,235 707,030 9.41 4.05 PROTO-POWER CORPORATION CAI.c NO.97-200 REV A PAGE 21 OF 23 GROTON, CONNECTICUT ORIGINATOR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOB NO.31-003 CLIENT Connmonwealth Edison PEOIECT LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- l(2)VYOIA and 1(2)VY02A 7.4 Fouling Sensitivity Analysis The results of the fouling sensitivity analysis are included in Tables 11 and 12. The PROTO-HXTM reports associated with the fouling sensitivity analysis for both coolers and a graphical presentation of the results are included as Attachment M. The 108 gpm Case is used to represent the 1(2)VY02A coolers since this flow rate will bound that of the 115 gpm Case. It should be noted that neither the Tables 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.Table 11: Fouling Sensitivity Analysis -- 1(2)VYO1A at 75 gpm Air-Sidef Tube-Sidef Required q Available q %Margin 0.0020 0.0000 517,239 723,937 39.96%0.0020 0.0010 517,239 698,599 35.06%0.0020 0.0020 517,239 675,177 30.53%0.0020 0.0030 517,239 651,570 25.97%0.0020 0.0040 517,239 630,961 21.99%Table 12: Fouling Sensitivity Analysis -- 1(2)VY02A at 108 gpm Air-Sidef Tube-Sidef Required q Available q %Margin 0.0020 0.0000 646,235 756,011 16.99%0.0020 0.0010 646,235 731,028 13.12%0.0020 0.0020 646,235 707,030 9.41%0.0020 0.0030 646,235 683,298 5.74%0.0020 0.0040 646,235 660,999 2.28%

PROTO-POWER CORPORATION CALC NO.97-200 REV A PAGE 22 OF 23 GROTON, CONNECTICUT ORIINAI"OR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOBNo. 3N1-003 CLIENT- Commonwealth Edison 1RoJEL' LaSalle Station GL 89-13 Heat Exchanger Testing TITLE VY Cooler Thermal Performance Model -- I(2)VY0IA and 1(2)VY02A 8. CONCLUSIONS A model for the LaSalle County Station Units 1 & 2 NW and SW Cubicle Area Coolers was developed using PROTO-HXTM 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 model is 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 150 gpm and for reduced flow rates of 75 gpm, 108 gpm, and 115 gpm in support of service water system flow requirements.

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-0102a.phx, with a file size of 1,146,880 bytes, and a file date and time of 6/24/98 at 2:25:30 pm. The saved database is set up to run the 108 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 I. 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-001078, Revision 2, RHR Pump A Cubicle Cooler Ventilation System 3. LaSalle Calculation L-001221, Revision 2, HPCS Pump Cubicle Cooler Ventilation System 4. LaSalle Station Updated Final Safety Analysis Report, Table 3.1 1-8, 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 (Attachment A)6. LaSalle Station Updated Final Safety Analysis Report, Section 9.2.6, Ultimate Heat Sink (Attachment A)

PROTO-POWER CORPORATION CALC NO.97-200 REv A PAGE 23 OF 23 GROTON, CONNECTICUT ORIGINA FOR L. Philpot DATE 6/24/98 VERIFIED BY M. Aboye JOB NO.31-003 CLIENT Commonwealth Edison 7R(lJEcr LaSalle Station GL 89-13 Heat Exchanger Testing"TirE VY Cooler Thermal Performance Model -- l(2)VYO1A and 1 (2)VY02A 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 2605-1-1 1,12,13, & 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 (Attachment A)14. Proto-Power Calculation 96-069, Revision -, Fluid Properties

-Moist Air -Range 8' to 3001F 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 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-0835 (Attachment L)

Attachment A to Proto-Power Calculation 97-200 Revision A Proto-Power Caic: 97-200

Attachment:

A Rev: A Page 1 of Ae1 3 14,ýeromce.

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 EOUIPMENT IS OPERATING 4M+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 hours0.00127 days 0.0306 hours 1.818783e-4 weeks 4.1855e-5 months (-921 days). The .100 days accident conditions are included.Radiation:

1 x 107 rads gamma (integrated)

Pressure:-0.4 inch W.G.1(VY OZA NOTE: The bounding radiation dose (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: 97-200

Attachment:

A i/ 6/)/9 Rev: A Page 2 of J1-'TABLE 3.11-8 REV. 6 -APRIL 1990 LSCS-UFSAR rQ ce S 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: 97-200

Attachment:

A pie Rev: A Page 3 of "f 13 9.2-2 REV. 10 -APRIL 1994 LSCS-UFSAR Re ekrer~ce Q 0 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 and accident conditions perm!ssible water temperature supplied.!o the plant"-s 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 andj2.5.9.2.6.1.2 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: 97-200

Attachment:

A Rev: A Page 4 of ,2,/3 9'.2-18 REV. 0 -APRIL 1984 TUBE MC FACE -ING ITO MAKENT.AIR ILVC..AIR E~r v. d~d TOTA 1AAIR SiE IUBE 1DEI DESIGN DEIN (LN, nIN FOR TPA TEM (OF) AERIWATI R T ANFR IPESlI%+PESS.mApI WIESUEOIjNCL 1.HIP ..nAr IF 0 m , TE NO~FIEM(Fh TU UT 0i)KQ (IN i4>0 rLOF1120JI OSIG IT 20 I ULI21.4 1 OAIVOA 47330 b tO./')L 109.4/84.1 IOb.O 115.3 1 150. 1 .75 1 .42 1 27.0 1 250 200 1 2 1 815 1 1026.I I IbO-/ 02.L= .(LLLV MA-rFRIAL 5PECIFICAT-0hIS-TUBE5- Lo.o. ASIVE S57COPPrt, .049 WAL.L-HiCKV4EIS.

FIWS -ASrtMi 5209 ALUM. 0.012 IN.T14b(.

SPIQALINfPC AIEC64AMICAL.

e-owO, 10.0 P~tJs/i..cw.

WADERS-22 1`0M.504-80 eLAC14 STEEL PIPE. 4STM A-53 ,qACk~lNCa A.5Th A'126, 14 GA. 0bLV. SIEErL a.0 0 0 40 0 0 T, to 1 4ZQR~S~.LLF~ Cr3UWTY Pt~NFR ST~TI0~J.U~Jrr4ti/~

E 8'r R , 15 1-121-741 GENE P~A..I LERA 5 DECIMALS -+.12 UULESS OTHERWISE SPECIFIED DIMERSIOUdS INq IMCUES _JOB LOCATION 5E:E,, 1 BUYER COMMONWEALTH EDISON COMPANY dUYER NO. IJ417I CARRIEI1 NO. dOO20 *0 e. --.e...-d ii " i- .-I...I I ICSCS EQUIPMENT.AREA COOLING COILS 1WhA7ID\Nca.

NO. DIV.I2VY~iA2vY2 28SW1OZ15L13II I I t

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I .... m

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A Rev: A Page 6 of I. a.".. , "" " I BB -10 I Q* 4.S~&I.'~.qUV~~%i

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Attachment:

A Rev: A Page 7 of Y"/ s q *4' A a. m~ro Imp% slm& FM~ 4101. V1. ;4 E l ipi f.4). 'o HOLES h-;a..C,.2iC 3. & l9 l M US 113u LMI. At WL. I'm lm fil" 0 f " 4V7 -I. I M S M IS M VA 11. u,. i um "ue .sm a. I x w e 0 pg. p K = S MOST a*. " .ran " o w m I a .a It. uq L.-. --M SL 10 V9 10 OILC. IW r t N oiu W CIm. "."r-O 44 tP*5EE OF UNtltMOI0.145 -W L IC ARAN ILUNCOV SPEC flI54Z S.- ..' * ~~~ 2 !%AE 1A.5 CjANCHOR 1 o AL? ~ -I5'.4 UOLIStIS Ul 011`400 tEP!sNCONN (ArAIL- 12)3 L~~Y-i N!OAS*Ii ,-OLPULL. SPACE 'i 1 I 0- ~OPERATING WEIGT 5450'tA SEE DwG-2605-L 6FO& MATm. SPECS 24~ ~ ~ p: 3VOOPENINO

..2 IT ] ___NGHT? HAND UNIT-2 -.. PANEL~NtCS1A4NL BASE (0"IP.-Go IGROOvE *PiPIfII coe.DroNDAAt:E~?

Q AWN BY ELEVATION .NO T TO CEKDs 97-20 -CSCS EOUIPMENEI AREA AIR I4ANOLEING UNIT *Proto-PowerCac eroacs -eov &...Rev: A Page 8 of f41 3 K) ..~. ~:* *j 4 0 o.GLCStjUOCý-.C HOLEF nD K-=-.wiog FLAN~GE ALL 4 $WE&thjI[CbT cqmbuEwrONjm T PEPufTAOfu j~t~a- i~ib ',AECýA.S AftCI4O 5".11" U'iT$4 f? o rOW RI,*tu Vw'PA 2. AlF W 011'" SIKt*h1 P'0'r OP"I. 11 IsI'-*A -1.F 'V.3 fD 1%m VMU ismI. 11. factrI mom .'iV.0. SIWPi VI W2 Wif kMIS tV1 tW C .U. jtiNiip W~p IL IMemo" Mt eVI .fwv gw a. S.W-.IP2.6L (MME CWL 32 W1 VA %t Ai 0411t ownt -ol Pw -i s, vt millif Nol% I. 11114. -aW tIISW "S It to. W.q 1.JU.DiS fa(n i fUt II 0 .UW 1Pt S '11.~. 19 zijj iih (4,'.li- -EL A-1 Ef INEA ANlchOR BoLT P~LANl E 7 L r% ot ro$-..?a$.f

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Attachment:

Rev: A Page 9 of Xi3r;-If '.)/i l)if 9..r air,'

GENERAL QUALITY ASSURANCE PROCEDURE LSRGNT',,LUNDYJ CIft N1J%.~TITLE & Al:1PROVAL PAGE CECO CiCT'ro"ILIC a"SAFETY RELATED ITEMS ARE PART OF THI S SPECIFICATION" Client CECO Specification Title Specification Number Project Identification Heat Exchange Coils and Cabinets J-2582 La Salle County -Units I and 2 4266-00/4267-00 Project Number Mechanical/HVAC Department

~k/j-. .*1 REV DATE PREPARER APPROVER PURPOSE OF ISSUE 1 1-16-75 0011-L)I ( rgýxýý-wIssue to CEC0 for bids.er Calc: 97-200 Proto-Pov%

Attachmenk:

A Rev: A rage 10 of 4-2* 3 IV Z/10yI-I '-- Y 4/Function or Service ...........

Equipment Numbers .............

Safety related or Nonsafety related (SR or NSR)...........

403. PERFORMANCE DATA (HEAT EXCHANGE Auxiliary Pr imary CSCS Eqpt. CSCS Eqpt. CSCS Eqpt.Control Electric Contain- Area Area IArea Room Equipment ment Vent. Cooling Coolin8 ;Coolng OVC02AA OVEO1AA IVP03AA IVYOA 1VYO3A [ IVYO4A OVC02AB OVEOIAB 1VP03AB IVYO2A ZVYO3A 2VYO4A 2VP03AA 2VYO1A 2VP03AB 2VYO2A _SRand____ ___ ___ ____ ____ ___ _ __ ____ _ 1 403.q-J COIL CABINETS)1 Mode of Operation

.............

a. Entering Air Dry Bulb ...... (*F)b. Entering Air Wet Bulb ..... .(F)c. Leaving Air Dry Bulb ....... (OF)d. Leaving Air Wet Bulb. ...... (0 F)e. Actual Air Quantity at 700F, 407% RH and Site Elevation 3...................... (ft /min)f. Standard Air Quantity at .075 lb/ft3 ............ (Std ftl/min)g. Cooling Medium .................

h. Evaporator Refrigerant Tempera-, ture .......................

(*F)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 ............... (Btu/h)m. Maximum Coil Face Velocity..................... (it/m n)SR Cooling 81.8 63.1 54.3 52.8 26340 25380 R-22 42 SR 6ooling 81.9 63.2 54.9 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 150 110 150 SR and ASME III Cooling 110 SR and ASME III a CD 0 N:-Lw a%0 0o n\0 Cooling 150 Add. I 110 Add.l1 Add. 1 18000 17330 Water 105.150.748,700 748,700 700 It 26400 25420 Water 105.220.1. 1 X 106 1. 0 :0 LO6 700ý8500 27450[ ater 797,000 725,000 600 936,000 847,000 600 105.Z40 L. 19 10 06 1. 19 x106 700 Add. l I' Re Ieracce Kp 26.10 1997 ASi 1RAE Fu ndamueutals ltandl (Table 1A Healting and Wind Design C(.nditin.--l.ited Stalteslite Uifut C(ohc.", Mungllh W.S/M0K) 9 f'MS.'MVWII to A8 Annual Vjev. 1lealing 03 Spred 0,4% I% '99.% 0.4% m tean I -s stblion W,' tas. ong. It pina lals 99 6*/ 99% 1% .5t V'. MtlD WS.MUD MWug PiD ,.SVW :. Mi,. 4"', wA.'RGLi.u'4rPriswi C, lun~trs, hwnl Mmmg_Ml~rit hu. DiNItr All B Ailms,I KAnnwk Cn.:lunin Calunsbnll, hsim Anni~o F Haonolulu ziuluiMoCdAS IIAW110 Ulnhule Notolksai IDXHO Boise Burley Idabo Falls Lniwjn MosaWrlin oMne. Al BMultan 18J2403 PocafrdloSCOa AFB Cbsu*g, rFild (hasup. allan lol A sprivo Pleru, West tanea Per,L,+ ~ound. 'ai Wa lpd s Dest M'aim Emnt LOitt'omLs iam 0ik.Frlwm Bisilinpo 722'1'1) 26.6' -1012 NI Sf6? 41's" 4' 47 2, Si S' .', "1 U 'J IiA 1.. Iii I 9 IS 7n 7.1160 7 2110 7221 80 722137 722255 722170 7i2270 723200 722070 747810 722166 722 30 911780 912850 911820 911900 911760 9)1650 911860 726910 725867 725785 727830 726815 727836 725780 31.53 33.93.13.65.3.37 31.15 32.33 32.52 32.70 33.9-34.35.12.13 10.97 10.78 31.25 84 IX 191 83 32 tIO 84.42 10,4 81.97 148 83.38 20 85.00 2.31 84.93 797£7.65 361 84.52 1070 85.17 643 81.20 49 83.20 233 83.28 203 82.40 151 21.32 158.07 19.72 155.07 21.35 157.93.20.90 156.43 21.45 157 77 21.98 159.35 21.15 157.10 49 16 16 66 10 148 449 43.57 42.55 43.52 46.38 43.05 47.47 42.92 116.22 2867 113.77 4150 112.07 4741 117.02 1437 115.87 2995 115.80 3317 112.60 4478 724338 38.55 89.85 725340 41.78 87.73 725300 41.98 87.90 72531.6i 39:83_9.81.97 725.A16 42.08 87.82 744600 41.37 88.68 725440 41.45 90.52 725320 40.67 89.68.724396' 39.95. 91-20 725430 4220 89.10 724390 39.85 89.67 725305 41.92 88.25 72-4320 725330 724380 724386 725335 725310 724373 725455 725450 725460 125490 725466 725485 725465 725570 726500 725490 724580 724510 72,1$51 724515 7746.30 38.05 41.00 39.73 40.42 40.65 41.70 39.45 4078 41.88 42 53 42.55 40.62 43.15 41.10 42.40 43 17 4255 39.55 37 77 3905 37.93 39 37 87913 8520 8627 86.93 86.15 86.32 87.32 91.13 91.70 93.65 94 18 9395 93.33 92.45 9638 95.15 92.40 97.65 99.97 96 77 t00.72 101.70 453 623 673 682 653 738 594 663 768 741 614 758 387 827 807 607 810 774 584 699 869 965 1165 1122 1214 846 1102 1339 879 1483 2592 1066 2890.1685.3 1 14.617 14 685 14 572 14 4A6 14.i103 14 136 14.357 14 669 14.572 14588 14.6 15 14.6(19 14 67c1 14.6R7 14.661 14.690 14.617 14.458 13.235 12.621 12.346 13.94A 13.173 13.017 12.468 14.457 14-167 14.342.14.337 14.352 14.308 14.383 14.347 14.292 14.306 14.373 14.491 14.262 14.272 14.376 14.270 14.289 14.."8 14.328 14.240 14.190 14.087 14.. 1 14.062 14. 251 14 119 11:998 14.2.34 13 925.3.370 14 138 13.224 12.840 s."93 6193 6!93 6193 8293 1 '91 6193 6193 8293 6191 829 1£29.1 829.1 6293 6193 6193 6193 6193 8293 6193 8293 8293 8293 8293 8293 6193 8293 8293 69293 6193 8293 8293 6193 6193 8293 6193 6193 8293 6193 6193 6193 8293 8293 6193 8293 8293 8293 6293 8293.6193 8293 619.1 A291 619)1 8291 6193 8293 8293 6393 20 30 21 21 15 26.30 28 29 59 61 61 59 67 60 60 2-.5-12 6 0-1-7 3-4-6-2-3-s-8-6-4-10-4-7 3-4-3-5-3-2-4-Il-11.03-6-95-ii-16-14-4-2-.3.3 145 3;.I 27 27 26 21 29 34 31 32 62 63 63 61 68 62 61 9 2-6 5 7 0 10 3-1 4 1-3-t.2-4 2 0 9 2 3 3 4 3 5 0 0-15-9 6 4 2"0 214).j -0 310 320 3441 340 2-11 360"40 250 40 230 320 160 190 270 70 130 60 360 280 90 14 54)360 240 270 310 250 290 290 290 330 290 270 290 320 250 230 270 270 230 310 300 320 300 3211 320 3O0 300 360 I0.150 160 2i11 4 9 9 9 In 9 9 6 6 9 8"'Sij 151)250 2210*510 240 270 270.100 3041 240 60 Hio 110 50 70 60 60 320 280 I80 310 350 10 2%190 220 230 210 240 250 200 I O 210 200 230 240 2441 230 2341 220 210 230 230 2'00[ 84)i R.4)194)7.t-4)2001 2410 180 180 10 1811I'M 1 00')S 98+it)99 100 98 9.1 99 99 98 93 88 91 92 88 87 92 I1)1 98 96 IL" 1o5 92 98 100 97 96 99 98 96 97 96 97 95 97 96 97 95 94 97 96 95 96 98 96 98 5')(97 98 99 109 96 1.04 1404 (12-.1.0 II 9 35 7.3 ih1 1.7 56'2 2 5 7 4.4 2.9 £.7 14 2.3 6.1 '14 2. 6.4-3.6 6. " 4 3.8: 18 3.0 5.4 -21 2.5 7.6 17 32 ":7 21 7 7.6 35 16214 #58 1.6 j 4 1.9 22 40 1. 290 57 1.4 3.0 4-3 4 22o-4 i .7 9-12 4 8.5 '-20 3.6 9.0 K.3 2.7 9.9 1-6 3.2 8-3-7 2 7.9.-15 21 9.1 '-3.I 7.2-10 1.2 81-12 2.8 6.5-(0 SL1: .-10 3.1 7.7-11 4 5.9-14 2.7 6. 0-12 3.3 6.1-16 31 5.5-II 2.8 5- :-24 32 7.7-4 2.7 3. 2,-11. 3.6 5.2-10 2.8 618-11 .3.8 7!.Z-8 3.8 7.4 10 3.3 5.8 i0 3.2 79 9 12 II 12 9 12 It 11 13 II 9 14 15 14 12 13 16 j7 16 1.1 l0.15..15-t2-23-12-I2'-24)-8-6-5-9--Il 4 3.6 3.4 49 4.3 3.6 4 3.6 6.3"4 4 28 3,3 27.29 6.8 5.4 5 1 49 68 11.4 6.8 4.7 4.0)5.9 9.4 56 9.0 6.5 6.6 W"400 -U'Wurldl Oetem'olugscal Ilrgasunaion number 1.1 a Iziasude.

LAW& -6sogiAudC Eley elcvalin.

ft Sid5 " standard pressure al galtios (r Iltl J Z,_buUfl) 1enperatsar:.

'F V'5 tu-ind speed ripht Proto-Power Calc: 97-2.(

Attachment:

A j Rev: A Page 12 0o III--

ff11, gt jtttttt I L P'hysical Properties of' Mtterials 36.3 Trhle 3 Properties of Solids SjpcciEric I lea I, M)usiky, Thermtial (onducti' it.%, Material Description thIhi/(t.1 ulkt't -f"lr At I'Dulnun (atlly I 100) 0.214' j 71" t 2K'it I iisiv it'~Riati.0. 2(y" Sutr ier. Condition Lil ,vtrCi~d s.heft leLLovIV O%.L1I~e~d Alunninuxtt bronize (76% Cu, 221' 7i., 2% All Astwstoz" Fiber In llSlatioll Ashes, wood Asphalt Bakelile Bell lacial h3asnuth tin (lick, building 0.09'0.25h, o.20'o.20'0.351'0.0861 (122)0 040" 0.2" 0,09" 0.09" 0.104,'0.055'0.172 51"; .4i?;132" 810 1230 548" 519u 530'5,4,0j$8"" Brass: Red (815% Cu. 15% 7-11)Yellow (65% Cu. 35% Z1n).Bronte Cadmium Carbon (gas retort)Cardboard Cellulose Cement (poriland clinker)Chalk Charcoal (wood)Chrome brick U 097'0.1,,92

0 41'970" 37.6*0.4"5" (371)513.7"'0.20" (2)1.04" 0.033'0.01'7P 0.48" 0.03' (392)0.67")0.93'0.030" l1:ghlly polished 0.0331' Highly polished 0.0 2 d 0.81L (I)931 0.32" 0_16" 0.215'0.2 1.1 0,171'3.4'120'143'15, 200" 0.34" About 250TF Clay 0.22t 63'Coal 0.3" 90W 0.098' (32)Coal tan 0,35" (104) 75i' 0.07 Coke (petroleum, powdered) 0.36' (752) 62" 0.55b (752)Concrete (stone) 0. 156 ' (392) 144" 0.54 Copper (electrolytic) 0.092' 556" 227' 0.072" Commercial, shiny Cork (granulated) 0.485' 5.4' 0.02W (23)Cotton (fiber) 0.3190 95" 0.0240 Cryolite (AIF--3NaF) 0.253h 1810 Diamond 0.147h 151' 271 Earth (dry and packed) 95' 0.037" 0.41l Fel 20,6"' 0.03" Fireclay brick 0_198b (212) 112' 0.58' (392) 0.750 At 18321F Flrorspar (CaF 2) 0.21" 199" 0.63'German silver (nickel silver) 0.094 545: 19" 0.135" Polished Glass: Crown (soda4ime) 0.18" 154' 0.590 (200) 0.94" Smooth Flint (lead) 0. 1 17? 2670 0.79" Heat-resistant 0.200 139' 0.59' (200)"Wool" 0.157' 3.25' 0.022'Gold 0.0312" 12080 172' 0.02a I tighly polished Graphite:

Powder 0.165" 0.1060 Impervious 0.16" 1179 75" 0.75a Gypsum 0.2590 78' 0.25' 0.903b On a smooth plate Hemp (fiber) 0.323* 93" lee: 32'F 0.4&7 57. 1.3" 0,950-4*F 0.4651 1.41'Iron: Cast 0.12"(212) 450' 27.6h (129) 0.435" Freshly turned Wrought 485" 34.9" 0.94" Doull. oxidized Lad 0.0309M 707" 20.10 0.28" Gray, oxidized Leather (sole) 62.4" 0.092'Limestone 0.217" 103" 0.54' 0.36* to 0.90 At 145 to 380F Linen 0.0o5 Litharge (lead monoxide) 0.0.551. 4901h Magncsiat Powdered 0.234h (212) 49.7" 0.15h (117)Light carbonate 131 0.034'Magnesize brick 0.2220 (212) 1581' 2.2" (400)Magne'sium 0241t 108l 91" 0.55" Oxidized Marle 0.21' 162t' I 5h' 0.9311 light gray, polishird Nickel. polished 0.1051 5.5s 34.4v 0.'45" Elecrioplaecd Paints: White lacquer 0.80" While enlamel 0.91" 011 Tough pl1lme Black 0 10" Black shellac 63u 0 15 0.91 n "Matte" fiti.sh Flat tlack lacquei 0.96" Aluminum lacquer 0.39" On plate'D(a source unknown, 2. Sue lscnitltllers indictetl dafa source fron ihrh. O Nofr..: 1. Valuc- ale siw (or non untcss noirld in parelheParc t --t:Vl., -A= 1 P , /a I-.-.. -/ V --~'-. -

Attachment B to Proto-Power Calculation 97-200 Revision A Proto-Power Calc: 97-200

Attachment:

B Rev: A Page 1 of 3 Page No.09(15192 LA SALLE COUNTY STATION MEAT EXCHANGER (WATER TO AIR)DATABASE NUMBER/NAME iVY01C"A" RNR AREA COOLER INSPECT DATE B A S E P H 0 T PHOTO STORAGE LOCATION GENERAL APPEARANCE

.. SC.... ==A VSSUU~vlC TUBE CONDITION NO DAMAGE OR LEAKS FOUND.FINS CONDITION SmSmUwUUUU.C CLEAN NO DEBRIS.A FEW FINS BENT.DEFECTS COR R E C T I V E RECOMM4ENDED sunassolimtlll newns MUSS ACT DNMS ACTUAL 09/15/92 N Y BTN/XAPSHOT Hx#l VERY CLEAN. NO DEBRIS.NONE.NONE NEEDED.N/A vyoia VY01C-Coo le'r-C00ý , Ir P.=r C.)'~0*1 0 0 0 CD 0 C'0-J"3 0 0 0 t,)10'o1c r-~~~, /~9 ~'6C~r~I V ýLl IC klfl-SýDE LA SALLE COUNTY STATION HEAT EXCHANGER (WATER TO AIR)DATABASE EQUIPMENT NUMBER/NAME 1VY02C NPCS AREA COOLER INSPECT DATE B A S E P 14 0 T PHOTO STO#AGE LOCATION.twlSUmvltfl BTN /XAPSHOT HX#l GENERAL APPEARANCE n B p=== m=nzatu~ttut gt..TUBE CONDITION 09101/92 N Y VERY CLEAN. NO DEBRIS FOUND.CLEAN. NO DAMAGE NOTICED.FINS CONDI TION zsuamaznzzm=

JUST A FEW FINS SENT.GENERAL CONDITION IS VERY CLEAN.C RR FC r I VE RECOMMENDED Z2 ... n. -zwzn A ACT I ONKS ACTUAL*uzz utuuzzIHs.3..amm DEFECTS NONE.NOINE, N/A C Cvo e--r-c- 0Co&IeýVY'c4C~~Pt'-Cb jvýozc IWLL-Fsipc 1 doz ILCS8~CVIA L vt6zc.- OLtmrsFtt Attachment C to Proto-Power Calculation 97-200 Revision A Proto-Power Calc: 97-200

Attachment:

C Rev: A Page 1 of 8 16:50:12 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Data Report for: I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 06/19/98 Air Coil Heat Exchanger Input Parameters j FliilQt-idi i- Tf I.....T6 .thV. ..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 2 1-,-79.00 -fifi 150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side..50.00- gpm 105.00 OF 115.30 OF Fresh Water 0.001500 0.000000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 750,000 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-fi.°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 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

C Rev: A Page 2 of 8 16:50:12 PROTO-HIX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/19/98 CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -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 ('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) 150.00 Air Flow (acfm) 21,179.00 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: 97-200

Attachment:

C Rev: A Page 3 of 8 16:50:12 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 06/19/98 Extrapolation Calculation Summary 1I Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature

(°F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature

(°F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/lt-hr)

Skin Visc (lbm/ft'hr)

Density (ibm/fl 3)Cp (BTU/lbm-°F)

K (BTU/hr-ft--F)

Air-Side 77,999.05 150.00 110.28 Tube-Side 74,508.32 105.00 115.42 Tube-Side hi (BTU/hr'ft 2.OF)j Factor Air-Side ho (BTUihr" ft 2.-F)Tube Wall Resistance (hr-ft2.°F/BTU

0.0 0031430

Overall Fouling (hr ft 2-0 F/BTU) 0.02832467 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)7,503.18 775,120 775,120 W Extrapolation Calculation for Row l(Dry)11 Air-Side Mass Flow (lbm/hr) 77,999.05 Inlet Temperature (OF) 150.00 Outlet Temperature (OF) 140.10 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 145.05 Skin Temperature (OF) 122.46 Velocity *** 3,598.07 Reynold's Number 848*, Prandtl Number 0.7254 Bulk Visc (Ibm/ft-hr) 0.0491 Skin Visc (lbm/ft-hr)

Density (Ibm/fl 3) 0.0624 Cp (BTU/Ibm-0 F) 0.2402 K (BTU/hr-ft.°F) 0.0162 Tube-Side 74,508.32 112.82 115.42 114.12 116.51 5.53 37,906 3.8666 1.4247 1.3920 61.8006 0.9988 0.3680 Tube-Side hi (BTU/hr'-ft-F) 1,639.65 j Factor 0.0095 Air-Side ho (BTU/hr ft 2.°F) 10.20 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft2.°F/BTU)

0.0 2832467

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)6.72 937.90.30.66 193,146 0.9017 193,146** Reynolds Number Outside Range of Equation Applicability W Proto-Power Calc: 97-200

Attachment:

C Rev: A Page 4 of 8* Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 16:50:12 PROTO-HX 3.01 by Proto-Power Corporation (SN#PH X-0000)CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 06/19/98 FA Extrapolation CJalculation for Row 2(Dry)II it Air-Side Tube-Side Mass Flow (lbm/hr) 77,999.05 Inlet Temperature (IF) 140.10 Outlet Temperature (IF) 132.32 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 136.21 Skin Temperature

("F) 118.38 Velocity *** 3,598.07 Reynold's Number 857*-Prandtl Number 0.7262 Bulk Vise (lbm/ft-hr) 0.0485 Skin Vise (Ibm/ft-hr)

Density (Ibm/fl 3) 0.0632 Cp (BTU/lbm-°F) 0.2402 K (BTU/hr-ft-'F) 0.0160 74,508.32 110.78 112.82 111.80 113.70 5.52 37,051 3.9648 1.4576 1.4304 61.8343 0.9988 0.3672 Tube-Side hi (BTU/hr-ft 2.°F) 1,618.86 j Factor 0.0095 Air-Side ho (BTU/hr'ft 2-°F) 10.15 Tube Wall Resistance (hrft 2`"F/BTU 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 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)6.69 937.90 24.20 151,828 0.9020 151,828** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)________II Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature

(°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 Vise (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hr-ft:.F)

Air-Side 77,999.05 132.32 126.20 0.0203 0.0203 129.26 115.17 3,598.07 865*1 0.7267 0.0481 0.0639 0.2402 0.0159 Tube-Side 74,508.32 109.17 110.78 109.98 111.49 5.52 36,382 4.0450 1.4844 1.4620 61.8603 0.9988 0.3665 Tube-Side hi (BTU/hr ft 2"-F) 1,602.43 j Factor 0.0095 Air-Side ho (BTU/hr-ft 2.°F) 10.12 Tube Wall Resistance (hr-ft 2 7-F/BTU 0.00031430 Overall Fouling (hr. ft 2-°F/BTU) 0.02832467 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)6.67 937.90.19.11 119,548 0.9024 119,548** Reynolds Number Outside Range of Equation Applicability Proto-Power Cale: 97-200

Attachment:

C Rev: A Page 5 of 8*** Air Mass Velocity (Lbmihr'ft 2), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average T 16:50:12 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 06/19/98 Extrapolation Calculation for Row 4(Dry)II I Mass Flow (lbrilhr)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 (lbm/Rf 3)Cp (BTU/lbm.°F)

K (BTU/hrftl.°F)

Air-Side 77,999.05 126.20 121.37 0.0203 0.0203 123.78 112.65 3,598.07 871*" 0.7271 0.0477 0.0644 0.2402 0.0158 Tube-Side 74,508.32 107.91 1.09.17 108.54 109.74 5.52 35,858 4.1100 1.5061 1.4878 61.8805 0.9988 0.3660 Tube-S ide hi (BTU/hr- ft 2 -F) 1,589.45 j Factor 0.0094 Air-Side ho (BTU/hr-ft 2-°F) 10.09 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr. ft 2-F/BTU) 0.02832467 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)6.65 937.90 15.11 94,256 0.9026 94,256** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)II Air-Side Mass Flow (Ibm/hr) 77,999.05 Inlet Temperature

(°F) 121.37 Outlet Temperature

(°F) 117.55 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (°F) 119.46 Skin Temperature

(°F) 110.65 Velocity *** 3,598.07 Reynold's Number 876*.Prandtl Number 0.7274 Bulk Visc (Ibm/ft-hr) 0.0474 Skin Visc (lbmift-hr)

Density (Ibm/fl 3) 0.0648 Cp (BTU/lbm-°F) 0.2402 K (BTU/hr-ft'°F) 0.0157 Tube-Side 74,508.32 106.91 107.91 107.41 108.36 5.52 35,447 4.1625 1.5235 1.5087 61.8962 0.9989 0.3656 Tube-Side hi (BTU/hr ft 2.'F) 1,579.19 j Factor 0.0094 Air-Side ho (BTU/hr ft 2.'F) 10.07 Tube Wall Resistance (hr-ft 2 -F/BTU 0.00031430 Overall Fouling (hr- ft 2-F/BTU) 0.02832467 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)6.64 937.90 11.95 74,393 0.9028 74,393** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

C Rev: A Page 6 of 8 Air Mass Velocity (Lbn/hr.ft 2), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average T 16:50:12 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 06/19/98 Extrapolation Calculation for Row 6(Dry)II Air-Side Tube-Side Mass Flow (lbm/hr) 77,999.05 Inlet Temperature (IF) 117.55 Outlet Temperature

(°F) 114.54 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 116.05 Skin Temperature (IF) 109.08 Velocity *** 3,598.07 Reynold's Number 880**Prandtl Number 0.7277 Bulk Visc (lbm/ft-hr) 0.0472 Skin Visc (ibm/ftrhr)

Density (lbm/fW) 0.0652 Cp (BTU/Ibm 0'F) 0.2402 K (BTU/hr'ft'°F) 0.0156 74,508.32 106.12 106.91 106.51 107.27 5.52 35,123 4.2047 1.5376 1.5256 61.9085 0.9989 0.3653 Tube-Side hi (BTU/hr ft 2.0 F) 1,571.08 j Factor 0.0094 Air-Side ho (BTU/hr'ft 2"°F) 10.05 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr' ft 2"°F/BTU) 0.02832467 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)6.63 937.90 9.45 58,765 0.9029 58,765** Reynolds Number Outside Range of Equation Applicability

ý RM Extrapolation Calculation for Row 7(Dry)11 Mass Flow (lbmlhr)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/ft.hr)

Density (Ibm/fl 3)Cp (BTU/lbm-°F)

K (BTU/hr-ft.°F)

Air-Side 77,999.05 114.54 112.16 0.0203 0.0203 113.35 107.84 3,598.07 884**0.7278 0.0471 0.0654 0.2402 0.0155 Tube-Side 74,508.32 105.49 106.12 105.81 106.41 5.52 34,868 4.2386 1.5488 1.5392 61.9181 0.9989 0.3650 Tube-Side hi (BTU/hr ft2. F) 1,564.65 j Factor 0.0094 Air-Side ho (BTU/hrft2.°F) 10.03 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr ft2.°F/BTU)

0.0 2832467

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)6.62 937.90 7.48 46,450 0.9031 46,450** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

C Rev: A Page 7 of 8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 16:50:12 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils Initial Benchmark Case -- Standard Coil 06/19/98 Extrapolation Calculation for Row 8(Dry)I U~I 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 Vise (ibm/ft-hr)

Skin Vise (ibm/ft hr)Density (Ibm/fl 3)Cp (BTU/Ibm.°F)

K (BTU/hr-ft-.F)

Air-Side 77,999.05 112.16 110.28 0.0203 0.0203 111.22 106.86 3,598.07 886**0.7280 0.0469 0.0657 0.2402 0.0155 Tube-Side 74,508.32 105.00 105.49 105.25 105.72 5.52 34,667 4.2656 1.5578 1.5501 61.9257 0.9989 0.3648 Tube-Side hi (BTU/hr-ft 2-°F) 1,559.57 j Factor 0.0094 Air-Side ho (BTU/hr ft.°'F) 10.02 Tube Wall Resistance (hr-fl 2.0 FfBTU 0.00031430 Overall Fouling (hr ft2.°F/BTU)

0.0 2832467

U Overall (BTU/hr'ft 2.'F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/lu)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.61 937.90 5.92 36,735 0.9032 36,735** Reynolds Number Outside Range of Equation Applicability Proto-Power CaIc: 97-200

Attachment:

C Rev: A Page 8 of 8*** Air Mass Velocity (Lbn/hr ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T Attachment D to Proto-Power Calculation 97-200 Revision A Proto-Power Calc: 97-200

Attachment:

D Rev: A Page 1 of 2 268 Comjipact Heat Exchangt-t.r.

Fig. 10-84 Findcircular tubes. sujrface CF-9.05-314J. (Dat aoffamcsnea.)

Tobe outsik~ diameter -0.774 in = 19.66 x 10'3m Fin pitch = 9.05 per in -356 per m Fin thickness 0.012 in -0.305 x 10-3m Fin area/total area -0.835 F low passage hvdrau I ic A B diameter, 4 rb -0.01681 0.02685-. 5.131 i 10-3 8.179 x 10-C 0 E 0.0445 0.01587 0.02108 ft 13.59 x 10-3 4.846 x 10-3 6.426 x 10"2m Free.flow area/fetrtal area, o = 0.45 Heat transfer areat tolal volLnme. is 108 354 5 0.572 0.688 0.537 0.572 B5.1 61.9 135 0ft8iWt 279 203 443 354 ni m/t Nntc: I~Ain,.icur fre~e-flc'w atea in oll cases occuLts in the soacr's transvemrs to the 1mow. c-ceest for DI, in whichi Bll' mr~i-,ai~r-3 rv isin The diailonals, Proto-Power Caic: 97-200

Attachment:

D Rev: A Page 2 of 2 Attachment E to Proto-Power Calculation 97-200 Revision A Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 1 of 15 17:01:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#IPX-0000)

ComEd -- LaSalle Data Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 06/19/98 Air Coil Heat Exchanger Input Parameters Fl f-iiU-Qm-fi-T65

..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 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction)

Air-Side Tube-Side-2 ITf7. 0&fi......-50.00 gpm 150.00 OF 105.00 OF 92.00 OF 109.40 OF 115.30 OF 84.10 OF Fresh Water 0.001500 0.000000 750,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

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) 108.000 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 2 of 15 17:01:46 PROTO-HX 3.01 by Proto-Powver Corporation (SN#PHX-0000) 6/19/98 CornEd -- LaSalle Calculation Report for: 1(2)VY0IA

& 02A -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 (OF)Air Dry Bulb Temp Out (°F)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (OF)Wet Bulb Temp Out (°F)Atmospheric Pressure Tube Flow (gpm)Tube Temp In (°F)Tube Temp Out (OF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm) 150.00 Air Flow (acfin) 21,179.00 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: 97-200

Attachment:

E Rev: A Page 3 of 15 17:01:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 06/19/98.1 Extrapolation Calculation Summary II Air-Side Mass Flow (lbm/hr) 77,999.05 Inlet Temperature

(°F) 150.00 Outlet Temperature

(°F) 111.57 Inlet Specific Humidity Outlet Specific Humidity Average Temp (°F)Skin Temperature

(°F)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.°F)

Tube-Side 74,508.32 105.00 115.11 Tube-Side hi (BTU/hr ft 2.°F)j Factor Air-Side ho (BTU/hr" ft 2 -F)Tube Wall Resistance (hr ft2. F/BTU 0.00031430 Overall Fouling (hr- ft 2.°F/BTU) 0.02832467 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)7,503.18 749,965 749,965 w Extrapolation Calculation for Row 1(Dry)I.Air-Side Mass Flow (lbm/hr) 77,999.05 Inlet Temperature (OF) 150.00 Outlet Temperature (OF) 140.99 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (OF) 145.50 Skin Temperature (0 F) 121.51 Velocity *** 3,598.07 Reynold's Number 847*" Prandtl Number 0.7253 Bulk Vise (lbm/ft-hr) 0.0491 Skin Vise (lbmift-hr)

Tube-Side 74,508.32 112.75 115.11 113.93 116.10 5.53 37,836 3.8745 1.4273 1.3974 Tube-Side hi (BTU/hr.ft2-°F) 1,637.56 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.59 Tube Wall Resistance (hr.ft 2-°F/BTU 0.00031430 Overall Fouling (hr-ft 2-F/BTU) 0.02832467 U Overall (BTU/hr-ft 2.F)Effective Area (1t2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.98 937.90 31.35 175,742 0.9155 175,742 Density (lbmift3) 0.0623 61.8034 Cp (BTU/Ibm-'F) 0.2402 0.9988 K (BTU/hr-flf.F) 0.0163 0.3679** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 4 of 15*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 17:01:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 06/19/98 Extrapolation Calculation for Row 2(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 (Ibm/fl hr)Skin Visc (lbm/ft-hr)

Density (Ibm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr'ft-'F)

Air-Side 77,999.05 140.99 133.73 0.0203 0.0203 137.36 117.93 3,598.07 856**0.7261 0.0486 0.0631 0.2402 0.0161 Tube-Side 74,508.32 110.84 112.75 111.79 113.57 5.52 37,048 3.9651 1.4577 1.4323 61.8344 0.9988 0.3672 Tube-Side hi (BTU/hr'ft 2'°F) 1,618.52 j Factor 0.0080 Air-Side ho (BTU/hr'ftt 2-F) 8.56 Tube Wall Resistance (hr ft 2-°F/BTU 0.00031430 Overall Fouling (hr ft 2"°F/BTU) 0.02832467 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)5.95 937.90 25.39 141,802 0.9158 141,802** Reynolds Number Outside Range of Equation Applicability K.-.. __ --Extrapolation Calculation for Row 3(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 (Ibm/ft 3)Cp (BTU/Ibm.°F)

K (BTU/hr.flt-F)

Air-Side 77,999.05 133.73 127.86 0.0203 0.0203 130.79 115.04 3,598.07 863**0.7266 0.0482 0.0637 0.2402 0.0159 Tube-Side 74,508.32 109.30 110.84 110.07 111.52 5.52 36,416 4.0408 1.4830 1.4616 61.8590 0.9988 0.3666 Tube-Side hi (BTU/hr- ft2.F) 1,603.09 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.53 Tube Wall Resistance (hr-ft 2-0 F/BTU 0.00031430 Overall Fouling (hr-ft 2_-F/BTU) 0.02832467 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)5.94 937.90 20.58 114,578 0.9161 114,578** Reynolds Number Outside Range of Equation Applicability Proto-Power Cale: 97-200

Attachment:

E Rev: A Page 5 of 15*** Air Mass Velocity (Lbmrhr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 17:01:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: I(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 06/19/98 M Extrapolation Calculation for Row 4(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (OF)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 (Ibm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr-ft.°F)

Air-Side 77,999.05 127.86 123.11 0.0203 0.0203 125.48 112.71 3,598.07 869**0.7270 0.0478 0.0642 0.2402 0.0158 Tube-Side 74,508.32 108.06 109.30 108.68 109.86 5.52 35,909 4.1037 1.5039 1.4861 61.8786 0.9988 0.3661 Tube-Side hi (BTU/hr:ft2-OF) 1,590.59 j Factor 0.0080 Air-Side ho (BTU/hr.ft 2-°F) 8.50 Tube Wall Resistance (hrft 2 0.°F/BTU 0.00031430 Overall Fouling (hr- ft 2.° F/BTU) 0.02832467 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)5.92 937.90 16.69 92,686 0.9163 92,686** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)H Mass Flow (lbm/hr)Inlet Temperature (OF)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-°F)

K (BTU/hr'ft--F)

Air-Side 77,999.05 123.11 119.26 0.0203 0.0203 121.18 110.82 3,598.07 874*., 0.7273 0.0476 0.0646 0.2402 0.0157 Tube-Side 74,508.32 107.05 108.06 107.55 108.51 5.52 35,499 4.1558 1.5213 1.5065 61.8943 0.9989 0.3656 Tube-Side hi (BTU/hr ft 2.°F) 1,580.44 j Factor 0.0079 Air-Side ho (BTU/hr ft 2.°F) 8.48 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft2-°F/BTU)

0.0 2832467

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)5.91 937.90 13.54 75,047 0.9164 75,047** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 6 of 15 Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 17:01:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 06/19/98 Extrapolation Calculation for Row 6(Dry)II II I.Mass Flow (lbm/hr)Inlet Temperature (0 F)Outlet Temperature (IF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (°F)Skin Temperature

(°F)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.°F)

Air-Side 77,999.05 119.26 116.14 0.0203 0.0203 117.70 109.29 3,598.07 878*" 0.7276 0.0473 0.0650 0.2402 0.0156 Tube-Side 74,508.32 106.23 107.05 106.64 107.42 5.52 35,169 4.1987 1.5356 1.5233 61.9068 0.9989 0.3653 Tube-Side hi (BTU/hr'ft 2"°F) 1,572.22 j Factor 0.0079 Air-Side ho (BTU/hr'ft 2"°F) 8.47 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 U Overall (BTU/hr ft 2-°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)5.90 937.90 10.99 60,810 0.9166 60,810** Reynolds Number Outside Range of Equation Applicability Ift" Extrapolation Calculation for Row 7(Dry)11 Air-Side Mass Flow (lbm/hr) 77,999.05 Inlet Temperature (IF) 116.14 Outlet Temperature (OF) 113.62 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (°F) 114.88 Skin Temperature (OF) 108.05 Velocity *** 3,598.07 Reynold's Number 882*1 Prandtl Number 0.7277 Bulk Vise (lbm/ft-hr) 0.0472 Skin Vise (lbm/ft'hr)

Density (Ibm/Ift 3) 0.0653 Cp (BTU/lbm-°F) 0.2402 K (BTU/hr-ft-°F) 0.0156 Tube-Side 74,508.32 105.57 106.23 105.90 106.54 5.52 34,902 4.2341 1.5473 1.5372 61.9169 0.9989 0.3650 Tube-Side hi (BTU/hr fV2-°F) 1,565.54 j Factor 0.0079 Air-Side ho (BTU/hr-ft 2.°F) 8.46 Tube Wall Resistance (hr-ft 2-F/BTU 0.00031430 Overall Fouling (hr- ft 2.°F/BTU) 0.02832467 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)5.89 937.90 8.92 49,305 0.9167 49,305** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 7 of 15*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ftisec);

Air Density at Inlet T, Other Properties at Average T 17:01:46 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Calculation Report for: 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark Case -- Custom Coil 06/19/98"I.Extrapolation Calculation for Row 8(Dry)II 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 (lbm/ft 3)Cp (BTU/Ibm.°F)

K (BTU/hr-ft-°F)

Air-Side 77,999.05 113.62 111.57 0.0203 0.0203 112.59 107.05 3,598.07 885*" 0.7279 0.0470 0.0655 0.2402 0.0155 Tube-Side 74,508.32 105.03 105.57 105.30 105.82 5.52 I' 34,686 4.2631 1.5569 1.5486 61.9250 0.9989 0.3648 Tube-Side hi (BTU/hr-ft'.°F) 1,560.11 j Factor 0.0079 Air-Side ho (BTU/hr-ft 2-0 F) 8.45 Tube Wall Resistance (hr-ft2-°F/BTU

0.0 0031430

Overall Fouling (hr ft 2.°F/BTU) 0.02832467 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)5.89 937.90 7.24 39,996 0.9168 39,996** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 8 of 15*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:04:26 PROTO-IX 3.01 by Proto-Power Corporation (SN#IPHX-0000)

CornEd -- LaSalle Data Report for: 1(2)VYOI A & 02A -CSCS Equipment Area Cooling Coils Final Benchmark

-Effective Coil Length 06/22/98 Air Coil Heat Exchanger Input Parameters Flu-Qii-ifiity, To ....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 1- V79.00 -fifi 150.00 OF 92.00 OF Tube-Side.150.00 gpm 105.00 OF 109.40 OF 115.30 OF 84.10 OF Fresh Water 0.001500 0.000000 750,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration' Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

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) 104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 9 of 15 07:04:26 PROTO-IHX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 ComEd -- LaSalle Calculation Report for: l(2)VY0IA

& 02A -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 (acfrn)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) 150.00 Air Flow (acfm) 21,179.00 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: 97-200

Attachment:

E Rev: A Page 10 of 15 07:04:26 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark

-Effective Coil Length 06/22/98 Extrapolation Calculation Summary_________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/Ibm-°F)

K (BTU/hr-ft--F)

Air-Side 77,999.05 150.00 111.76 Tube-Side 74,508.32 105.00 115.02 Tube-Side hi (BTU/hr-ft 2.°F)j Factor Air-Side ho (BTUihr-fl 2 t.F)Tube Wall Resistance (hr-ft 2-°F/BTU 0.00031430 Overall Fouling (hr'ft 2.F/BTU) 0.02832467 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)7,242.65 746,297 746,297 w Extrapolation Calculation for Row l(Dry)II Air-Side Mass Flow (Ibm/hr) 77,999.05 Inlet Temperature (OF) 150.00 Outlet Temperature (IF) 141.13 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 145.56 Skin Temperature (IF) 121.59 Velocity *** 3,727.50 Reynold's Number 878*" Prandtl Number 0.7253 Bulk Visc (lbm/ft-hr) 0.0491 Skin Visc (lbm/ft-hr)

Tube-Side 74,508.32 112.69 115.02 113.86 116.08 5.53 37,810 3.8775 1.4283 1.3978 Tube-Side hi (BTU/hr ft 2_-F) 1,637.06 j Factor 0.0079 Air-Side ho (BTU/hr.ft 2.°F) 8.79 Tube Wall Resistance (hr- ft2.F/BTU

0.0 0031430

Overall Fouling (hr- ft 2.°F/BTU) 0.02832467 U Overall (BTU/hr-it2.f 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)6.07 905.33 31.49 173,186 0.9137 173,186 Density (Ibm/ift 3) 0.0623 61.8044 Cp (BTU/Ibm'°F) 0.2402 0.9988 K (BTU/hr-ft-VF) 0.0163 0.3679** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 11 of 15*** Air Mass Velocity (Lbm/hr-ft), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:04:26 PROTO-IHX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark

-Effective Coil Length 06/22/98 Extrapolation Calculation for Row 2(Dry)II TL_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 Vise (lbm/ft-hr)

Skin Vise (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hr-ft.

0 F)Air-Side 77,999.05 141.13 133.94 0.0203 0.0203 137.53 118.04 3,727.50 887**0.7261 0.0486 0.0630 0.2402 0.0161 Tube-Side 74,508.32 110.81 112.69 111.75 113.57 5.52 37,032 3.9670 1.4583 1.4323 61.8350 0.9988 0.3672 Tube-Side hi (BTU/hr-ft 2.0 F) 1,618.25 j Factor 0.0079 Air-Side ho (BTU/hr-ft 2-°F) 8.76 Tube Wall Resistance (hr-ft 2 -F/BTU 0.00031430 Overall Fouling (hrft 2-°F/BTU) 0.02832467 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)6.05 905.33 25.61 140,305 0.9140 140,305** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)II Air-Side Tube-Side Mass Flow (lbmihr) 77,999.05 74,508.32 Inlet Temperature (OF) 133.94 109.28 Outlet Temperature

(°F) 128.10 110.81 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (°F) 131.02 110.04 Skin Temperature (OF) 115.16 111.53 Velocity *** 3,727.50 5.52 Reynold's Number 894** 36,406 Prandtl Number 0.7266 4.0420 Bulk Visc (lbm/ft-hr) 0.0482 1.4834 Skin Visc (lbm/ft-hr) 1.4614 Density (lbm/ft 3) 0.0637 61.8594 Cp (BTU/Ibm-°F) 0.2402 0.9988 K (BTU/hr-ft.°F) 0.0159 0.3666** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hr-ft 2.°F) 1,602.95 j Factor 0.0079 Air-Side ho (BTU/hr-ft 2-F) 8.73 Tube Wall Resistance (hr-ft 2.F/BTU 0.00031430 Overall Fouling (hr- ft2-F/BTU)

0.0 2832467

U Overall (BTU/hr-ft 2-°F) 6.03 Effective Area (ft 2) 905.33 LMTD 20.84 Total Heat Transferred (BTU/hr) 113,821 Surface Effectiveness (Eta) 0.9143 Sensible Heat Transferred (BTU/hr) 113,821 Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)Proto-Power Cale: 97-200

Attachment:

E Rev: A Page 12 of 15*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:04:26 PROTO-IIX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CoinEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark

-Effective Coil Length 06/22/98 Extrapolation Calculation for Row 4(Dry)II 1ýAir-Side Mass Flow (ibm/hr) 77,999.05 Inlet Temperature

(°F) 128.10 Outlet Temperature (0 F) 123.37 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 125.73 Skin Temperature (0 F) 112.82 Velocity *** 3,727.50 Reynold's Number 900*1 Prandtl Number 0.7270 Bulk Visc (Ibm/ft-hr) 0.0478 Skin Visc (lbm/ft.hr)

Tube-Side 74,508.32 108.04 109.28 108.66 109.88 5.52 35,901 4.1046 1.5043 1.4858 Tube-Side hi (BTU/hr ft 2.°F) 1,590.49 j Factor 0.0079 Air-Side ho (BTU/hrTft 2.°F) 8.70 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr ft 2.°F/BTU) 0.02832467 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)6.02 905.33 16.96 92,439 0.9145 92,439 Density (Ibm/fl 3) 0.0642 61.8789 Cp (BTU/ibm-°F) 0.2402 0.9988 K (BTU/hr-fi.°F) 0.0158 0.3661** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)*1II Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature

(°F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (Ibm/ft hr)Density (lbm/ft 3)Cp (BTU/lbm-°F)

K (BTU/hr-fti.F)

Air-Side 77,999.05 123.37 119.52 0.0203 0.0203 121.44 110.92 3,727.50 905**0.7273 0.0476 0.0646 0.2402 0.0157 Tube-Side 74,508.32 107.03 108.04 107.53 108.53 5.52 35,491 4.1567 1.5216 1.5062 61.8945 0.9989 0.3656 Tube-Side hi (BTU/hruft2-°F) 1,580.35 j Factor 0.0078 Air-Side ho (BTU/hr-ft 2-°F) 8.68 Tube Wall Resistance (hr-ft 2 0.F/BTU 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)6.01 905.33 13.82 75,142 0.9147 75,142** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 13 of 15*** Air Mass Velocity (Lbmhr- ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:04:26 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark

-Effective Coil Length 06/22/98 A Extrapolation Calculation for Row 6(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/ft-hr)

Skin Visc (lbmlft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr'ft'°F)

Air-Side 77,999.05 119.52 116.38 0.0203 0.0203 117.95 109.38 3,727.50 910*" 0.7275 0.0474 0.0650 0.2402 0.0156 Tube-Side 74,508.32 106.20 107.03 106.62 107.43 5.52 35,160 4.1998 1.5359 1.5231 61.9071 0.9989 0.3653 Tube-Side hi (BTU/ihrft 2.°F) 1,572.09 j Factor 0.0078 Air-Side ho (BTU/hr ft 2.°F) 8.67 Tube Wall Resistance (hr-ft 2-°F/BTU 0.00031430 Overall Fouling (hr'ft 2.°F/BTU) 0.02832467 U Overall (BTU/hr-ft 2'°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)6.00 905.33 11.26 61,127 0.9148 61,127** Reynolds Number Outside Range of Equation Applicability r .-1 1.Extrapolation Calculation for Row 7(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 (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hr-ft.°F)

Air-Side 77,999.05 116.38 113.83 0.0203 0.0203 115.11 108.12 3,727.50 913-*0.7277 0.0472 0.0653 0.2402 0.0156 Tube-Side 74,508.32 105.54 106.20 105.87 106.54 5.52 34,892 4.2354 1.5478 1.5372 61.9172 0.9989 0.3650 Tube-Side hi (BTU/hr-ft 2-.F) 1,565.36 j Factor 0.0078 Air-Side ho (BTU/hr-ft 2.°F) 8.66 Tube Wall Resistance (hr ft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft 2 0-F/BTU) 0.02832467 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)5.99 905.33 9.18 49,756 0.9149 49,756** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 14 of 15*** Air Mass Velocity (Lbnmihr ft 2), Tube Fluid Velocity (ftlsec);

Air Density at Inlet T, Other Properties at Average T 07:04:26 PROTO-HX 3.01 by Proto-Power Corporation (SN#PttX-0000)

CornEd -- LaSalle Calculation Report for: I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Final Benchmark

-Effective Coil Length 06/22/98 Extrapolation Calculation for Row 8(Dry)I Air-Side Mass Flow (lbm/hr) 77,999.05 Inlet Temperature (OF) 113.83 Outlet Temperature (OF) 111.76 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 112.79 Skin Temperature (OF) 107.10 Velocity *** 3,727.50 Reynold's Number 916" Prandtl Number 0.7279 Bulk Visc (lbm/ft-hr) 0.0470 Skin Visc (lbm/ft-hr)

Density (lbm/ft 3) 0.0655 Cp (BTU/lbm'°F) 0.2402 K (BTU/hr'ft'°F) 0.0155 Tube-Side 74,508.32 104.99 105.54 105.26 105.81 5.52 34,673 4.2648 1.5575 1.5487 61.9254 0.9989 0.3648 Tube-Side hi (BTU/ihr-ft 2.F) 1,559.87 j Factor 0.0078 Air-Side ho (BTU/hr' ft 2-°F) 8.65 Tube Wall Resistance (hr-ft 2 0-F/BTU 0.00031430 Overall Fouling (hr-ft 2-.F/BTU) 0.02832467 U Overall (BTU/hrft 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)5.98 905.33 7.48 40,520 0.9150 40,520** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

E Rev: A Page 15 of 15*** 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 97-200 Revision A Proto-Power Calc: 97-200

Attachment:

F Rev: A Page 1 of 8 07:18:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#IPHX-0000)

CornEd -- LaSalle Data Report for: 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Zero Fouling 06/22/98 Air Coil Heat Exchanger Input Parameters Air-Side F li-Qiii aYiiy, Thot-a- 21 179_0--acffm Inlet Dry Bulb Temp 150.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature 109.40 OF Outlet Wet Bulb Temp 84.10 OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Tube-Side.............

1-50_00 gpm 105.00 OF 115.30 OF Fresh Water 0.001500 0.000000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 750,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

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) 104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

F Rev: A Page 2 of 8 07:18:41 PROTO-HIX 3.01 by Proto-Power Corporation (SN#fPHX-0000) 6/22/98 CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Zero Fouling 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 (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) 150.00 Air Flow (acfm) 19,387.00 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 Input Fouling Factor 0.000000 Proto-Power Calc: 97-200

Attachment:

F Rev: A Page 3 of 8 07:18:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: I(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Zero Fouling 06/22/98.1 Extrapolation Calculation Summary 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 (Ibm/ft'hr)

Density (Ibm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr'ft'°F)

Air-Side 71,641.50 148.00 104.53 Tube-Side 74,586.94 100.00 110.41 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 0.00031430 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)7,242.65 779,018 779,018 ft Extrapolation Calculation for Row l(Dry)II I.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 (Ibm/ftl 3)Cp (BTU/Ibm-°F)

K (BTU/hr-ft'°F)

Air-Side 71,641.50 148.00 136.42 0.0203 0.0203 142.21 111.82 3,423.68 810"*0.7256 0.0489 0.0628 0.2402 0.0162 Tube-Side 74,586.94 107.62 110.41 109.01 111.75 5.53 36,069 4.0884 1.4988 1.4583 61.8739 0.9988 0.3662 Tube-Side hi (BTU/hr-ft 2.°F) 1,598.27 j Factor 0.0082 Air-Side ho (BTU/hr ft2.°F) 8.30 Tube Wall Resistance (hr.ft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft 2-°F/BTU)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)6.98 905.33 32.85 207,508 0.9181 207,508** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

F Rev: A Page 4 of 8*** Air Mass Velocity (Lbm/hr-ft), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:18:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Zero Fouling 06/22/98 Extrapolation Calculation for Row 2(Dry)11 Z&V , 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 (fF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbrn/ft-hr)

Skin Vise (lbmn/flthr)

Density (lbm//3f)Cp (BTU/Ibm'0 F)K (BTU/hr'ft.F) 71,641.50 136.42 127.59 0.0203 0.0203 132.01 108.73 3,423.68 820*4 0.7265 0.0482 0.0637 0.2402 0.0160 74,586.94 105.50 107.62 106.56 108.68 5.52 35,177 4.2025 1.5368 1.5040 61.9079 0.9989 0.3653 Tube-Side hi (BTU/hr flt-°F) 1,575.85 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.°F) 8.26 Tube Wall Resistance (hr-ft2-°F/BTU

0.0 0031430

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)6.94 905.33 25.19 158,199 0.9184 158,199** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)II 1.Mass Flow (Ibm/hr)Inlet Temperature

(°F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (°F)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbmn/ft-hr)

Skin Visc (lbm/ft-hr)

Density (Ibm/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hr-ft-°F)

Air-Side 71,641.50 127.59 120.85 0.0203 0.0203 124.22 106.36 3,423.68 829*1 0.7271 0.0478 0.0645 0.2402 0.0158 Tube-Side 74,586.94 103.87 105.50 104.69 106.32 5.52 34,502 4.2930 1.5669 1.5406 61.9332 0.9989 0.3646 Tube-Side hi (BTU/hr fl 2.°F) 1,558.67 j Factor 0.0081 Air-Side ho (BTU/hr ft2. F) 8.23 Tube Wall Resistance (hrft 2 0.°F/BTU 0.00031430 Overall Fouling (hr-ft2-°F/BTU)

U Overall (BTU/hr fl 2.°F) 6.91 Effective Area (ft 2) 905.33 LMTD 19.34 Total Heat Transferred (BTU/hr) 120,920 Surface Effectiveness (Eta) 0.9187 Sensible Heat Transferred (BTU/hr) 120,920 Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

F Rev: A Page 5 of 8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:18:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Zero Fouling 06/22/98 Extrapolation Calculation for Row 4(Dry)II II~II *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 (lbmrft'hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hr-ft-°F)

Air-Side 71,641.50 120.85 115.68 0.0203 0.0203 118.26 104.55 3,423.68 835**0.7275 0.0474 0.0650 0.2402 0.0156 Tube-Side 74,586.94 102.63 103.87 103.25 104.52 5.52 33,989 4.3645 1.5905 1.5697 61.9522 0.9989 0.3640 Tube-Side hi (BTU/hr'fi3"°F) 1,545.48 j Factor 0.0081 Air-Side ho (BTU/hr ft 2"°F) 8.20 Tube Wall Resistance (hr- ft 2-°F/BTU 0.00031430 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)6.88 905.33 14.86 92,611 0.9190 92,611** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)ll II I.Air-Side Tube-Side Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (°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'°F) 71,641.50 115.68 111.72 0.0203 0.0203 113.70 103.15 3,423.68 840*1 0.7278 0.0471 0.0655 0.2402 0.0155 74,586.94 101.68 102.63 102.15 103.13 5.52 33,597 4.4206 1.6091 1.5926 61.9666 0.9990 0.3636 Tube-Side hi (BTU/hr-ft 2.°F) 1,535.34 j Factor 0.0080 Air-Side ho (BTU/hr.ft 2.°F) 8.18 Tube Wall Resistance (hr-ft 2"°F/BTU 0.00031430 Overall Fouling (hr. ft 2.°F/BTU)U Overall (BTU/hr'ft 2-°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)6.87 905.33 11.43 71,038 0.9191 71,038** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

F Rev: A Page 6 of 8*** Air Mass Velocity (Lbni/hr'ft), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:18:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#tPHX-0000)

CornEd -- LaSalle Calculation Report for: I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Zero Fouling 06/22/98 Extrapolation Calculation for Row 6(Dry)II 1. *Air-Side Tube-Side 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 (lbmr/ft)Cp (BTU/Ibm-'F)

K (BTU/hrftr'°F) 71,641.50 111.72 108.67 0.0203 0.0203 110.19 102.08 3,423.68 844**0.7280 0.0469 0.0659 0.2402 0.0155 74,586.94 100.95 101.68 101.31 102.06-5.52 33,298 4.4644 1.6236 1.6106 61.9776 0.9990 0.3633 Tube-Side hi (BTU/Lr-ft 2-°F) 1,527.56 j Factor 0.0080 Air-Side ho (BTU/hr. ft 2 -F) 8.16 Tube Wall Resistance (hr-ft 2-°F/BTU 0.00031430 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)6.85 905.33 8.79 54,554 0.9193 54,554** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)11 Mass Flow (Ibm/hr)Inlet Temperature

(°F)Outlet Temperature

(°F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (7F)Skin Temperature (0 F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbrn/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hr"ft-'F)

Air-Side 71,641.50 108.67 106.33 0.0203 0.0203 107.50 101.26 3,423.68 848*1 0.7282 0.0467 0.0661 0.2402 0.0154 Tube-Side 74,586.94 100.38 100.95 100.66 101.25 5.52 33,069 4.4985 1.6348 1.6247 61.9859 0.9990 0.3630 Tube-Side hi (BTU/hr ft2-'F) 1,521.56 j Factor 0.0080 Air-Side ho (BTU/hr ft 2--F) 8.15 Tube Wall Resistance (hr-ft2- F/BTU 0.00031430 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)6.84 905.33 6.77 41,933 0.9194 41,933** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

F Rev: A Page 7 of 8* Air Mass Velocity (Lbrnihr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:18:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Zero Fouling 06/22/98 Extrapolation Calculation for Row 8(Dry)II 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 Vise (lbm/ft-hr)

Skin Visc (Ibm/ftbhr)

Density (lbm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr.ft-0 F)Air-Side 71,641.50 106.33 104.53 0.0203 0.0203 105.43 100.63 3,423.68 850**0.7283 0.0465 0.0663 0.2402 0.0154 Tube-Side 74,586.94 99.95 100.38 100.17 100.61 5.52 32,893 4.5250 1.6436 1.6357 61.9922 0.9990 0.31628 Tube-Side hi (BTU/hr'ft 2 1-F) 1,516.95 j Factor 0.0080 Air-Side ho (BTU/hr-ft 2.°F) 8.14 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr'ft 2"°F/BTU)U Overall (BTU/hr ft 2.°F)Effective Area (f11)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)6.84 905.33 5.21 32,255 0.9195 32,255** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

F Rev: A Page 8 of 8*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average T Attachment G to Proto-Power Calculation 97-200 Revision A Proto-Power Caic: 97-200

Attachment:

G Rev: A Page I of 8 07:24:04 PROTO-IIX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Data Report for: I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Design Fouling 06/22/98 Air Coil Heat Exchanger Input Parameters Air-Side Fluiid Ql-ua-ntity, Total -

Inlet Dry Bulb Temp 150.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature 109.40 OF Outlet Wet Bulb Temp 84.10 OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Tube-Side 105.00 OF 115.30 OF Fresh Water 0.001500 0.000000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 750,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)

Fin Conductivity (BTU/hr-fP-OF)

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) 104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

G Rev: A Page 2 of 8 07:24:04 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 ComEd -- LaSalle Calculation Report for: l(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Design Fouling 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 (acftm)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 (OF)Extrapolation Data Tube Flow (gpm) 150.00 Air Flow (acfim) 19,321.00 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: 97-200

Attachment:

G Rev: A Page 3 of 8 07:24:04 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Design Fouling 06/22/98 Extrapolation Calculation Summary 11 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/ftbhr)

Density (lbm/ft 3)Cp (BTU/lbm 0'F)K (BTU/hr.ft.F)

Air-Side 71,397.61 148.00 106.46 Tube-Side 74,586.94 100.00 109.94 Tube-Side hi (BTU/hr'ft 2-°F)j Factor Air-Side ho (BTU/hr'ft'°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)0.00031430

0.0 2832467

7,242.65 741,876 741,876 W -Extrapolation Calculation for Row l(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 (Ibm/ft-hr)

Air-Side 71,397.61 148.00 137.97 0.0203 0.0203 142.99 116.80 3,412.02 806**0.7256 0.0489 Tube-Side 74,586.94 107.53 109.94 108.74 111.10 5.53 35,968 4.1010 1.5030 1.4678 Tube-Side hi (BTU/hr-ft 2.°F) 1,595.06 j Factor 0.0082 Air-Side ho (BTU/hr-ft2.

F) 8.29 Tube Wall Resistance (hr-ft 2 l-F/BTU 0.00031430 Overall Fouling (hr-ft2. F/BTU) 0.02832467 U Overall (BTU/hr ft 2 .F)Effective Area (ft 2)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTUihr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.82 905.33 34.00 179,064 0.9182 179,064 Density (lbm/ft 3) 0.0626 61.8778 Cp (BTU/Ibm-°F) 0.2402 0.9989 K (BTU/hr.ft.'F) 0.0162 0.3661** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

G Rev: A Page 4 of 8*** Air Mass Velocity (Lbm/hr.ft), Tube Fluid Velocity (ft!sec), Air Density at Inlet T, Other Properties at Average T 07:24:04 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Design Fouling 06/22/98 Extrapolation Calculation for Row 2(Dry)II 119--Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature

(°F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (OF)Skin Temperature (OF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ftihr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm-'F)

K (BTU/hr'ft-'F)

Air-Side 71,397.61 137.97 129.99 0.0203 0.0203 133.98 113.03 3,412.02 815"*0.7264 0.0484 0.0635 0.2402 0.0160 Tube-Side 74,586.94 105.62 107.53 106.58 108.48 5.52 35,184 4.2016 1.5365 1.5070 61.9076 0.9989 0.3653 Tube-Side hi (BTU/hr ft 2-°F) 1,575.52 j Factor 0.0081 Air-Side ho (BTU/hr'ft 2-.F) 8.25 Tube Wall Resistance (hr- ft2-°F/BTU

0.0 0031430

Overall Fouling (hr'ft-'°F/BTU)

0.0 2832467

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)5.79 905.33 27.20 142,681 0.9185 142,681** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)11 II Mass Flow (lbm/hr)Inlet Temperature

(°F)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)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-°F)

K (BTU/hr"ft-°F)

Air-Side 71,397.61 129.99 123.61 0.0203 0.0203 126.80 110.02 3,412.02 823-*0.7269 0.0479 0.0642 0.2402 0.0158 Tube-Side 74,586.94 104.09 105.62 104.85 106.39 5.52 34,563 4.2848 1.5641 1.5395 61.9309 0.9989 0.3646 Tube-Side hi (BTU/hr.ft2-0 F) 1,559.89 j Factor 0.0081 Air-Side ho (BTU/hr'ft 2.°F) 8.22 Tube Wall Resistance (hrfft 2.F/BTU 0.00031430 Overall Fouling (hr'ft 2.°F/BTU) 0.02832467 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)5.77 905.33 21.78 113,876 0.9188 113,876** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

G Rev: A Page 5 of 8 Air Mass Velocity (Lbm/hr-ft), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:24:04 PROTO-HX 3.01 by Proto-Powver Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Design Fouling 06/22/98 Extrapolation Calculation for Row 4(Dry)I1 II Mass Flow (lbmi/hr)Inlet Temperature (fF)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 Vise (lbm/ft-hr)

Density (ibm/ftl)Cp (BTU/lbm-°F)

K (BTU/hr-ft-°F)

Air-Side 71,397.61 123.61 118.51 0.0203 0.0203 121.06 107.62 3,412.02 829**0.7273 0.0476 0.0647 0.2402 0.0157 Tube-Side 74,586.94 102.87 104.09 103.48 104.72 5.52 34,070 4.3531 1.5868 1.5664 61.9493 0.9989 0.3641 Tube-Side hi (BTU/hr'ft 2 -F) 1,547.37 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2"°F) 8.19 Tube Wall Resistance (hr-ft 2" 0 F/BTU 0.00031430 Overall Fouling (hr ft 2-FfBTU) 0.02832467 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)5.76 905.33 17.46 91,006 0.9190 91,006** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 5(Dry)II II I Air-Side Mass Flow (lbmr/hr) 71,397.61 Inlet Temperature

(°F) 118.51 Outlet Temperature (0 F) 114.44 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 116.48 Skin Temperature (0 F) 105.70 Velocity *** 3,412.02 Reynold's Number 834" Prandtl Number 0.7276 Bulk Visc (lbmi/f'hr) 0.0473 Skin Vise (lbm/ft.hr)

Density (lbm/fi 3) 0.0652 Cp (BTU/lbm-°F) 0.2402 K (BTU/hr" ft'°F) 0.0156 Tube-Side 74,586.94 101.89 102.87 102.38 103.38 5.52 33,678 4.4089 1.6052 1.5885 61.9637 0.9990 0.3637 Tube-Side hi (BTU/hr'fl 2-°F) 1,537.35 j Factor 0.0081 Air-Side ho (BTUihrft2.°'F) 8.17 Tube Wall Resistance (hr-ft 2"°F/BTU 0.00031430 Overall Fouling (hr ft 2.°F/BTU) 0.02832467 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)5.75 905.33 13.99 72,805 0.9192 72,805** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

G Rev: A Page 6 of 8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:24:04 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Design Fouling 06/22/98 Extrapolation Calculation for Row 6(Dry)BI II Mass Flow (lbm/hr)Inlet Temperature

(°F)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 (lbm/ft 3)Cp (BTU/Ibmn'F)

K (BTU/hr.ft.°F)

Air-Side 71,397.61 114.44 111.17 0.0203 0.0203 112.81 104.17 3,412.02 839-0.7279 0.0470 0.0656 0.2402 0.0155 Tube-Side 74,586.94 101.11 101.89 101.50 102.32 5.52 33,365 4.4545 1.6203 1.6063 61.9751 0.9990 0.3634 Tube-Side hi (BTU/hr'ft 2.'F) 1,529.34 j Factor 0.0081 Air-Side ho (BTU/hr.ft 2.°F) 8.16 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.02832467 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)5.74 905.33 11.22 58,294 0.9193 58,294** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)II I. *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/ft-hr)

Skin Visc (lbm/ft-hr)

Density (Ibmr/fV)Cp (BTU/lbm.'F)

K (BTU/hr-ft-°F)

Air-Side 71,397.61 111.17 108.56 0.0203 0.0203 109.87 102.93 3,412.02 842-*0.7280 0.0468 0.0659 0.2402 0.0155 Tube-Side 74,586.94 100.48 101.11 100.80 101.44 5.52 33,115 4.4916 1.6325 1.6213 61.9842 0.9990 0.3631 Tube-Side hi (BTU/hr ft2. F) 1,522.84 j Factor 0.0080 Air-Side ho (BTU/hr ft 2 0-F) 8.15 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr- ft 2.°F/BTU) 0.02832467 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)5.73 905.33 9.01 46,707 0.9194 46,707** Reynolds Number Outside Range of Equation Applicability aProto-Power Calc: 97-200

Attachment:

G Rev: A Page 7 of 8*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 07:24:04 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Margin Assessment

-- Design Fouling 06/22/98 1h Extrapolation Calculation for Row 8(Dry)II 11 Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature

(°F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (Ibm/ft-hr)

Density (lbm/fP3)Cp (BTU/Ibm'°F)

K (BTU/hr'ft4'F)

Air-Side 71,397.61 108.56 106.46 0.0203 0.0203 107.51 101.94 3,412.02 845*" 0.7282 0.0467 0.0661 0.2402 0.0154 Tube-Side 74,586.94 99.98 100.48 100.23 100.75 5.52 32,915 4.5216 1.6424 1.6333 61.9914 0.9990 0.3629 Tube-Side hi (BTU/hr-ft 2.°F) 1,517.67 j Factor 0.0080 Air-Side ho (BTU/hr'ft 2"°F) 8.14 Tube Wall Resistance (hr- ft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02832467 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)5.72 905.33 7.23 37,443 0.9195 37,443** Reynolds Number Outside Range of Equation Applicability KProto-Power Calc: 97-200

Attachment:

G Rev: A Page 8 of 8* Air Mass Velocity (Lbm/lhr-ft), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T Attachment H to Proto-Power Calculation 97-200 Revision A (Proto-Power Caic: 97-200

Attachment:

H Rev: A Page I 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 m, = Mass of Water Vapor, Ibm P = Atmospheric Pressure, lbf/in 2 Pa = Dry Air Pressure, lbf/in 2 PS = Saturated Air Pressure, lbf/in 2 Pv = Water Vapor Pressure, lbf/in 2 R, = 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 x, = Mole Fraction of Water Vapor xs= Mole Fraction of Water Vapor* = Moist Air Relative Humidity p = Moist air Density, Ibm/ft 3 Pa = Dry Air Density, Ibm/ft 3 pv = Water Vapor Density, lbm/ft3 in Moist Air in Saturated Air 2. REFERENCES (1) Proto-Power Calculation 96-069, Fluid Properties

-Moist Air -Range 8 0 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: 97-200

Attachment:

H Rev: A Page 2 of 13

3. MOIST AIR DENSITY For drv air: P. = P-P .Equation [4]Equation [51 (144) P, Pa =-R, ) (459.67 +T)where: 1a = 53.352 (fl-lbf)/(lbm-°R)

For water vapor: (1441 P, P= 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 5 (T)=a+bT+cT 2+dT 3+eT 4+ fF 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-II Proto-Power Calc: 97-200

Attachment:

H Rev: A Page 3 of 13

5. WATER VAPOR PRESSURE f(T7,) = a + bT,,. + cT,,>2 + d(TI + eT4 + fI (P. PT, T,.): =[(2T,ý -T- 2800)f(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, +(WRý,)Equation [ 11]6. MOIST AIR SPECIFIC HUMIDITY ina Pa Equation [12]Where: PvV RW, R(459.67 + T)PaV ma R .R,,(459.67

+T)Equation [13]Equation [14]7. MOIST AIR RELATIVE HUMIDITY x5 = X -Equation [15]Proto-Power Calc: 97-200

Attachment:

H Rev: A Page 4 of 13

@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 14.315 70 psia OF 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=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 2.109071E-1 1 psia psia psia Ibm/ft 3 Ibm/ft 3 Ibm/ft 3 Equation Equation Equation Equation Equation Equation Equation[8][15][4][5][6][7][12]00-I 0 0;~ Co / Aefce4~~ (oY/rt.

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 Tw F(Tw) = a+(b*Tw)+(c*Tw 2)+(d*Tw 3)+(e*Tw 4)+(f*Tw 5) =Pv = (((2*Tw-T-2800)*F(Tw))-P*(Tw-T))/(Tw-2800)

=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) =W = Rho v / Rho a =RH = Pv/Ps a=b=C=d=e=f=150 92.00 0.743918919 0.453253224 13.86174678

0.0 61367004

0.001248052

0.0 62615056

3.721743953

0.0 20337508

12.17852 2.358607E-02 1.007276E-03 1.888033E-05 3.775047E-07 4.871208E-10 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 [61 Equation [7]Equation [8]Equation [12]Equation [15]0'-i 0 CD 0;k C', I 1 13 ekk C kVV-C-4-k-('0 ~4' ~Lj ~

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 =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 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 [71 Equation [8]Equation [12]Equation [15]0 C)))ý 1-C-Sc.-Ile S Xr,-/7 ý0 r-ý-A1'Al-e-K~

C C ý'o "-t( A7 '0 A S X 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:

...cXAb-511M Given Dry Bulb and Relative Humidity T=RH =Ps = a+(b*T)+(c*T 2)+(d*T 3)+(e*T 4)+(f*TS) =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-1 0 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].0.0 0 4v 0-__a ,.00

N 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 =14.315 104.53 0.020273629 0.451874518 13.86312548

0.0 66319289

0.001344533

0.0 67663821

1.087702551 41.54394211 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 19386.84858 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]00> 16 0%0 0 L Cc) -,_ Cý c ýro rv S (C le- Cý- _ )

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: o ~ Equation Coefficients:

00 C 0 0 o C)_le 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=14.315 106.46 0.020273629 0.451874518 13.86312548

0.0 66093199

0.001339949

0.0 67433148

1.15128943 39.24942818 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 psia Inlet Air Flow 19320.75666 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15)Se~tv, U" '~LI( .

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*.-I 0 0 o /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=14.315 109.96 0.020273629 0.451874518 13.86312548 0.0656871 0.001331716

0.0 67018816

1.274809374 35.44643829 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 19202.04338 Equation [11]Equation [41 Equation [5]Equation [6]Equation [71 Equation [8]Equation [15]0%1 0,-

/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:

Cc,! O Cf 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=14.315 108.29 0.020273629 0.451874518 13.86312548

0.0 65880243

0.001335632

0.0 67215874

1.214518345 37.20606771 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 19258.50406 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]>0 _-i 0 0 0 0 0 J"L A , , ILý C) *A ý/ 7', 1 4/'7 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:

-0> g-.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=14.315 108.08 0.020273629 0.451874518 13.86312548

0.0 65904611

0.001336126

0.0 67240736

1.207113757 37.43429442 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 19265.62742 Equation [11]Equation [4]Equation [5]Equation [6]Equation [7]Equation [8]Equation [15]W N, Cc -, 4 "A" io "'L.S.0 Attachment I to Proto-Power Calculation 97-200 Revision A Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 1 of 22 08:47:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Data Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 75 gpm Case 06/22/98 Air Coil Heat Exchanger Input Parameters FInletd-Qyi Buii-b, 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 21 -7 9_00-ffii 150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side-_1-5O0-00 gpm 105.00 OF 115.30 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-.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)

Fresh Water 0.002000 0.002000 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 2 of 22 08:47:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 CornEd -- LaSalle Calculation Report for: I(2)VYO0A

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 75 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) 75.00 Air Flow (acfm) 19,202.00 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: 97-200

Attachment:

I Rev: A Page 3 of 22 08:47:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 75 gpm Case 06/22/98 Extrapolation Calculation Summary______ I t I1 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 (Ibmn/fthr)

Skin Visc (Ibm/ftdhr)

Density (lbm/ft 3)Cp (BTU/Ibm-'F)

K (BTU/hr-ft.°F)

Air-Side 70,957.87 148.00 109.96 Tube-Side 37,293.47 100.00 118.09 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 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.03976622 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)7,242.65 675,177 675,177 W Extrapolation Calculation for Row l(Dry)II Mass Flow (lbmihr)Inlet Temperature (OF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (°F)Skin Temperature (IF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbm/ftdhr)

Density (lbm/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hr"ft-'F)

Air-Side 70,957.87 148.00 140.61 0.0203 0.0203 144.30 125.07 3,391.01 800**0.7255 0.0490 0.0623 0.2402 0.0162 Tube-Side 37,293.47 114.57 118.09 116.33 119.22 2.77 19,386 3.7764 1.3943 1.3564 61.7676 0.9988 0.3688 Tube-Side hi (BTU/hr-ft 2-°F) 953.95 j Factor 0.0082 Air-Side ho (BTU/hr ft 2 0.F) 8.26 Tube Wall Resistance (hr-ft2.°F/BTU

0.0 0031430

Overall Fouling (hr- ft2.° F/BTU) 0.03976622 U Overall (BTU/hr.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)5.22 905.33 27.78 131,195 0.9184 131,195** Reynolds Number Outside Range of Equation Applicability Proto-Power CaIc: 97-200

Attachment:

I Rev: A Page 4 of 22*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 08:47:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#fPHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 75 gpm Case 06/22/98 Extrapolation Calculation for Row 2(Dry)II 1.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 (ibm/ft-hr)

Skin Visc (lbm/ft-hr)

Density (ibm/fl 3)Cp (BTU/Ibm 0'F)K (BTU/hr-ft.°F)

Air-Side Tube-Side 70,957.87 37,293.47 140.61 134.20 0.0203 0.0203 137.40 120.67 3,391.01 807**0.7261 0.0486 111.52 114.57 113.04 115.59 2.77 18,774 3.9116 1.4398 1.4043 61.8163 0.9988 0.3676 Tube-Side hi (BTU/hr- ft2.°F) 937.48 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2..F) 8.23 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.03976622 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)5.20 905.33 24.19 113,794 0.9187 113,794 0.0630 0.2402 0.0161** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)II Mass Flow (lbm/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 (lbm/ft-hr)

Density (Ibm/fl 3)Cp (BTU/Ibm'°F)

K (BTU/hr.ft-°F)

Air-Side 70,957.87 134.20 128.63 0.0203 0.0203 131.42 116.84 3,391.01 813**0.7266 0.0482 0.0636 0.2402 0.0159 Tube-Side 37,293.47 108.86 111.52 110.19 112.44 2.76 18,249 4.0355 1.4812 1.4484 61.8573 0.9988 0.3666 Tube-Side hi (BTU/hr-ft 2 0.F) 923.12 j Factor 0.0081 Air-Side ho (BTU/hr ft 2 V.F) 8.20 Tube Wall Resistance (hr-ft 2-.F/BTU 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.03976622 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)5.18 905.33 21.08 98,800 0.9189 98,800** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 5 of 22* Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 08:47:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#tPHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 75 gpm Case 06/22/98 Extrapolation Calculation for Row 4(Dry)11 I. *1 Air-Side Tube-Side Mass Flow (lbmr/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 (lbrlft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hr-ft.F) 70,957.87 128.63 123.80 0.0203 0.0203 126.21 113.52 3,391.01 819**0.7270 0.0479 0.0641 0.2402 0.0158 37,293.47 106.56 108.86 107.71 109.69 2.76 17,797 4.1483 1.5188 1.4886 61.8920 0.9989 0.3657 Tube-Side hi (BTU/hr'ft 2"°F) 910.59 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2-°F) 8.18 Tube Wall Resistance (hr-ft 2.F/BTU 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.03976622 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)5.16 905.33 18.38 85,857 0.9191 85,857** Reynolds Number Outside Range of Equation Applicability 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 (fF)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft'hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft-)Cp (BTU/Ibm-'F)

K (BTU/hr-ft-°F)

Air-Side Tube-Side 70,957.87 37,293.47 123.80 119.59 0.0203 0.0203 121.69 110.63 3,391.01 823**0.7273 0.0476 104.55 106.56 105.56 107.30 2.76 17,408 4.2505 1.5528 1.5252 61.9215 0.9989 0.3649 Tube-Side hi (BTU/hr-fl 2-F) 899.66 j Factor 0.0081 Air-Side ho (BTU/hr~ftl 2.F) 8.16 Tube Wall Resistance (hr ft 2 X-F/BTU 0.00031430 Overall Fouling (hr-ftl-°F/BTU)

0.0 3976622

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)5.15 905.33 16.03 74,667 0.9193 74,667 0.0646 0.2402 0.0157** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 6 of 22* Air Mass Velocity (Lbmihr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 08:47:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYOlA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 75 gpm Case 06/22/98 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

(°F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbm/fthr)

Density (ibm/fl 3)Cp (BTU/lbm-°F)

K (BTU/hr.ft-°F)

Air-Side 70,957.87 119.59 115.93 0.0203 0.0203 117.76 108.11 3,391.01 828"" 0.7276 0.0473 0.0650 0.2402 0.0156 Tube-Side 37,293.47 102.81 104.55 103.68 105.21 2.76 17,071 4.3429 1.5834 1.5583 61.9466 0.9989 0.3642 Tube-Side hi (BTU/hr.-ft 2 1-F) 890.12 j Factor 0.0081 Air-Side ho (BTU/hr ft2.°F) 8.15 Tube Wall Resistance (hr-ft 2 l-F/BTU 0.00031430 Overall Fouling (hr' ft 2'F/BTU) 0.03976622 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)5.13 905.33 13.98 64,980 0.9194 64,980** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)II Mass Flow (lbm/hr)Inlet Temperature (fF)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/fl 3)Cp (BTU/lbm-°F)

K (BTU/hr-ft-'F)

Air-Side 70,957.87 115.93 112.74 0.0203 0.0203 114.33 105.92 3,391.01 832**0.7278 0.0471 0.0654 0.2402 0.0156 Tube-Side 37,293.47 101.29 102.81 102.05 103.40 2.76 16,780 4.4260 1.6109 1.5881 61.9680 0.9990 0.3636 Tube-Side hi (BTU/hr-ft 2-°F) 881.79 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2'.F) 8.13 Tube Wall Resistance (hrft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.03976622 U Overall (BTU/hr.ft2.°F)

Effective Area (t21)LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)5.12 905.33 12.20 56,584 0.9196 56,584** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 7 of 22*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average T 08:47:41 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 75 gpm Case 06/22/98 R Extrapolation Calculation for Row 8(Dry)11-re_-Mass Flow (lbm/hr)Inlet Temperature (OF)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/Ibm-'F)

K (BTU/hr'ft-°F)

Air-Side 70,957.87 112.74 109.96 0.0203 0.0203 111.35 104.01 3,391.01 835**0.7280 0.0469 0.0657 0.2402 0.0155 Tube-Side 37,293.47 99.97 101.29 100.63 101.81 2.76 16,528 4.5004 1.6354 1.6149 61.9863 0.9990 0.3630 Tube-Side hi (BTU/hr-ft

-°F) 874.52 j Factor 0.0081 Air-Side ho (BTU/hr'ft 2'°F) 8.12 Tube Wall Resistance (hr-ft2-'F/BTU

0.0 0031430

Overall Fouling (hr'ft 2-°F/BTU) 0.03976622 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)5.11 905.33 10.65 49,300 0.9197 49,300** Reynolds Number Outside Range of Equation Applicability Proto-Power Caic: 97-200

Attachment:

I Rev: A Page 8 of 22*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 08:54:01 PROTO-lIX 3.01 by Proto-Power Corporation (SNtPHX-0000)

CornEd -- LaSalle Data Report for: 1(2)VYO0A

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 108 gpm Case 06/22/98 Air Coil Heat Exchanger Input Parameters FlUidiQ-antity, ToT0l. .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 21.1-79700-id~fh 150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side.150700 gpmin 105.00 OF 115.30 OF Fresh Water 0.002000 0.002000 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

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)104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 9 of 22 08:54:01 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 108 gprn 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) 108.00 Air Flow (acfm) 19,258.50 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: 97-200

Attachment:

I Rev: A Page 10 of 22 08:54:01 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 108 gpm Case 06/22/98.1 Extrapolation Calculation Summary il U.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/ft'hr)

Skin Visc (lbrn/ft-hr)

Density (lbm/Wft)Cp (BTU/Ibm.°F)

K (BTU/hr-fV°F)

Air-Side 71,166.65 148.00 108.29 Tube-Side 53,702.59 100.00 113.17 Tube-Side hi (BTU/hr'ft 2"°F)j Factor Air-Side ho (BTU/hr'fti-°F)

Tube Wall Resistance (hr.ft 2-'F/BTU 0.00031430 Overall Fouling (hr- ft2"F/BTU)

0.0 3976622

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)7,242.65 707,030 707,030 10-- -Extrapolation Calculation for Row 1 (Dry)11 Air-Side Mass Flow (lbm/hr) 71,166.65 Inlet Temperature (0 F) 148.00 Outlet Temperature (0 F) 139.36 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (°F) 143.68 Skin Temperature (0 F) 121.18 Velocity *** 3,400.99 Reynold's Number 803*, Prandtl Number 0.7255 Bulk Visc (lbm/ftlhr) 0.0490 Skin Visc (lbm/ft-hr)

Density (lbm./ft) 0.0625 Cp (BTU/Ibm-0 F) 0.2402 K (BTUihrfi.°F) 0.0162 Tube-Side 53,702.59 110.31 113.17 111.74 114.33 3.98 26,688 3.9675 1.4585 1.4217 61.8352 0.9988 0.3672 Tube-Side hi (BTU/hr- ft 2.F) 1,246.55 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2-°F) 8.27 Tube Wall Resistance (hr-ft 2-°F/BTU 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.03976622 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)5.35 905.33.31.73 153,749 0.9183 153,749** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 11 of 22*** Air Mass Velocity (Lbmi/hr, ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 08:54:01 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 108 gpm Case 06/22/98 Extrapolation Calculation for Row 2(Dry)11 1, 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/hr'ft-'F)

Air-Side 71,166.65 139.36 132.18 0.0203 0.0203 135.77 116.99 3,400.99 811-0.7262 0.0485 0.0632 0.2402 0.0160 Tube-Side 53,702.59 107.92 110.31 109.11 111.30 3.98 25,996 4.0838 1.4973 1.4649 61.8725 0.9988 0.3662 Tube-Side hi (BTU/hr'ft 2-°F) 1,228.62 j Factor 0.0081 Air-Side ho (BTU/hr ft2.°F) 8.24 Tube Wall Resistance (hr- ft2-F/BTU

0.0 0031430

Overall Fouling (hr ft 2.°F/BTU) 0.03976622 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)5.33 905.33 26.49 127,833 0.9186 127,833** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 3(Dry)II 1.- .Air-Side Tube-Side Mass Flow (lbmihr) 71,166.65 Inlet Temperature (IF) 132.18 Outlet Temperature (IF) 126.21 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 129.19 Skin Temperature (IF) 113.51 Velocity *** 3,400.99 Reynold's Number 818*" Prandtl Number 0.7267 Bulk Visc (lbm/ft'hr) 0.0481 Skin Visc (lbm/ft-hr)

Density (ibm/ft 3) 0.0639 Cp (BTU/Ibm-°F) 0.2402 K (BTU/hr'ft'°F) 0.0159 53,702.59 105.94 107.92 106.93 108.77 3.98 25,424 4.1849 1.5310 1.5025 61.9028 0.9989 0.3654 Tube-Side hi (BTU/hr-ftl-"F) 1,213.64 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2.°F) 8.21 Tube Wall Resistance (hr-ft 2-°F/BTU 0.00031430 Overall Fouling (hr- ft 2.°F/BTU) 0.03976622 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)5.31 905.33 22.12 106,417 0.9189 106,417** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 12 of 22*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 08:54:01 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 108 gpm Case 06/22/98 Extrapolation Calculation for Row 4(Dry)II I.Air-Side Mass Flow (lbm/hr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (7F)Skin Temperature (fF)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbm/ft-hr)

Skin Visc (lbm/ftlhr)

Density (lbrn/ft 3)Cp (BTU/lbm'°F)

K (BTU/hr-ft 0.F)7 71,166.65 126.21 121.22 0.0203 0.0203 123.72 110.61 3,400.99 824**0.7272 0.0477 Tube-Side 53,702.59 104.29 105.94 Tube-Side hi (BTU/hr-ft 2.°F) 1,201.11 j Factor 0.0081 Air-Side ho (BTU/hr. ft 2-°F) 8.19 Tube Wall Resistance (hr-ft2 °F/BTU 0.00031430 Overall Fouling (hr" ft 2"°F/BTU) 0.03976622 105.11 106.66 3.98 24,952 4.2722 1.5600 1.5352 61.9275 0.9989 0.3647 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)5.30 905.33 18.48 88,681 0.9191 88,681 0.0644 0.2402 0.0158** Reynolds Number Outside Range of Equation Applicability 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 (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-fi-°F)

Air-Side 71,166.65 121.22 117.07 0.0203 0.0203 119.15 108.20 3,400.99 829**0.7275 0.0474 0.0649 0.2402 0.0157 Tube-Side 53,702.59 102.91 104.29 103.60 104.90 3.97 24,560 4.3472 1.5848 1.5634 61.9477 0.9989 0.3642 Tube-Side hi (BTU/hr-ft 2-0 F) 1,190.65 j Factor 0.0081 Air-Side ho (BTU/hr-ft2.°F) 8.17 Tube Wall Resistance (hr ft 2.°F/BTU 0.00031430 Overall Fouling (hr-fl 2.F/BTU) 0.03976622 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)5.29 905.33 15.45 73,965 0.9192 73,965** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 13 of 22*** Air Mass Velocity (Lbmihr ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 08:54:01 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 108 gpm Case 06/22/98 Extrapolation Calculation for Row 6(Dry)II~1 Air-Side Mass Flow (lbm/hr) 71,166.65 Inlet Temperature (0 F) 117.07 Outlet Temperature (OF) 113.60 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (°F) 115.34 Skin Temperature

(°F) 106.18 Velocity *** 3,400.99 Reynold's Number 833*" Prandtl Number 0.7277 Bulk Visc (lbm/ft'hr) 0.0472 Skin Vise (lbm/ft-hr)

Density (lbm/ft 3) 0.0653 Cp (BTU/Ibm-°F) 0.2402 K (BTU/hr-ft-°F) 0.0156 Tube-Side 53,702.59 101.76 102.91 102.33 103.43 3.97 24,235 4.4115 1.6061 1.5876 61.9643 0.9990 0.3637 Tube-Side hi (BTU/hr-ft2.°F) 1,181.90 j Factor 0.0081 Air-Side ho (BTU/hr"ft 2.°F) 8.15 Tube Wall Resistance (hr'ft 2.°F/BTU 0.00031430 Overall Fouling (hr- ft 2-°F/BTU) 0.03976622 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)5.28 905.33 12.92 61,737 0.9194 61,737** Reynolds Number Outside Range of Equation Applicability f-_-9zW4_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/ft'hr)

Skin Visc (Ibm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm'°F)

K (BTU/hr-ft-'F)

Air-Side 71,166.65 113.60 110.71 0.0203 0.0203 112.15 104.49 3,400.99 837**0.7279 0.0470 0.0656 0.2402 0.0155 Tube-Side 53,702.59 100.79 101.76 101.27 102.20 3.97 23,965 4.4663 1.6242 1.6084 61.9780 0.9990 0.3633 Tube-Side hi (BTU/hr-ft 2.°F) 1,174.58 j Factor 0.0081 Air-Side ho (BTU/hrVfi2.°F) 8.14 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr- ft 2.°F/BTU) 0.03976622 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)5.27 905.33 10.81 51,562 0.9195 51,562** Reynolds Number Outside Range of Equation Applicability SProto-Power Cale: 97-200

Attachment:

I Rev: A Page 14 of 22 Air Mass Velocity (Lbm/hr-ft'), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 08:54:01 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 108 gpm Case 06/22/98 42z --Extrapolation Calculation for Row 8(Dry)II RI 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 Vise (Ibm/ft hr)Density (Ibm/fl 3)Cp (BTU/lbm.°F)

K (BTU/hr'ft-'F)

Air-Side 71,166.65 110.71 108.29 0.0203 0.0203 109.50 103.09 3,400.99 840*0.7281 0.0468 0.0659 0.2402 0.0154 Tube-Side 53,702.59 99.99 100.79 100.39 101.17 3.97 23,740 4.5129 1.6396 1.6261 61.9893 0.9990 0.3629 Tube-Side hi (BTU/hr'ft 2-°F) 1,168.45 j Factor 0.0080 Air-Side ho (BTU/hr'ft 2-0 F) 8.13 Tube Wall Resistance (hr-ft 2'°F/BTU 0.00031430 Overall Fouling (hr" ft 2"°F/BTU) 0.03976622 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)5.26 905.33 9.05 43,086 0.9196 43,086** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 15 of 22*** Air Mass Velocity (Lbm/hr ft 2), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average T 09:34:42 PROTO-IHX 3.01 by Proto-Power Corporation (SN#PIIX-0000)

ComEd -- LaSalle Data Report for: I(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 115 gpm Case 06/22/98 Air Coil Heat Exchanger Input Parameters Air-Side F I bii-d -Qidfi-t i -ty-, Tt al .2 I, 79.0-afif Inlet Dry Bulb Temp 150.00 OF Inlet Wet Bulb Temp 92.00 OF Inlet Relative Humidity %Outlet Dry Bulb Temperature 109.40 OF Outlet Wet Bulb Temp 84.10 OF Outlet Relative Humidity %Tube Fluid Name Tube Fouling Factor Air-Side Fouling Tube-Side 1503JU gpm 105.00 OF 115.30 OF Fresh Water 0.002000 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 750,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

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) 104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 16 of 22 09:34:42 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 ComEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 115 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 (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) 115.00 Air Flow (acfmt) 19,266.00 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: 97-200

Attachment:

I Rev: A Page 17 of 22 09:34:42 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 115 gpm Case 06/22/98 a Extrapolation Calculation Summary II Air-Side Mass Flow (lbm/hr) 71,194.37 Inlet Temperature (OF) 148.00 Outlet Temperature (OF) 108.08 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 (lbm/ft-hr)

Density (lbm/ft3)Cp (BTU/1bm-'F)

K (BTU/hr.ft.°F)

Tube-Side 57,183.32 100.00 112.47 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 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.03976622 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)7,242.65 710,964 710,964 Extrapolation Calculation for Row l(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 (lbmn/f.hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft3)Cp (BTU/Ibm'°F)

K (BTU/hr.ft-°F)

Air-Side 71,194.37 148.00 139.18 0.0203 0.0203 143.59 120.62 3,402.31 803**0.7255 0.0490 0.0625 0.2402 0.0162 Tube-Side 57,183.32 109.72 112.47 111.09 113.62 4.24 28,236 3.9956 1.4678 1.4317 61.8444 0.9988 0.3669 Tube-Side hi (BTU/hr-ftl 2.F) 1,306.21 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2-°F) 8.27 Tube Wall Resistance (hr-ft 2-°F/BTU 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.03976622 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)5.37 905.33 32.29 157,023 0.9183 157,023** Reynolds Number Outside Range of Equation Applicability Proto-Power Cale: 97-200

Attachment:

I Rev: A Page 18 of 22*** Air Mass Velocity (Lbmhir-ft'), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 09:34:42 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: I(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 115 gpm Case 06/22/98 Extrapolation Calculation for Row 2(Dry)11 I1 I Air-Side Mass Flow (lbm/hr) 71,194.37 Inlet Temperature

("F) 139.18 Outlet Temperature (OF) 131.90 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 135.54 Skin Temperature

(°F) 116.48 Velocity *** 3,402.31 Reynold's Number 811 *4 Prandtl Number 0.7262 Bulk Vise (lbm/ft-hr) 0.0485 Skin Vise (lbm/ft-hr)

Density (lbm/ft 3) 0.0633 Cp (BTU/Ibm'°F) 0.2402 K (BTUihr'ft-.F) 0.0160 Tube-Side 57,183.32 107.45 109.72 108.58 110.70 4.24 27,532 4.1080 1.5054 1.4737 61.8799 0.9989 0.3660 Tube-Side hi (BTU/hr-ft 2.°F) 1,288.13 j Factor 0.0081 Air-Side ho (BTU/hr ft2-°F) 8.24 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr ft 2.°F/BTU) 0.03976622 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)5.35 905.33 26.78 129,763 0.9186 129,763** Reynolds Number Outside Range of Equation Applicability

1. ~Extrapolation Calculation for Row 3(Dry)______ II Air-Side Tube-Side Mass Flow (lbm/hr) 71,194.37 57,183.32 Inlet Temperature

("F) 131.90 105.57 Outlet Temperature

("F) 125.87 107.45 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 128.88 106.51 Skin Temperature

(°F) 113.06 108.28 Velocity *** 3,402.31 4.23 Reynold's Number 818** 26,955 Prandtl Number 0.7268 4.2049 Bulk Visc (lbmn/fthr) 0.0480 1.5376 Skin Visc (lbm/ft-hr) 1.5101 Density (lbm/ft 3) 0.0639 61.9086 Cp (BTU/Ibm-°F) 0.2402 0.9989 K (BTU/hr-ft-°F) 0.0159 0.3653** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hr-ft 2.°F) 1,273.11 j Factor 0.0081 Air-Side ho (BTU/hrft 2".°F) 8.21 Tube Wall Resistance (hr ft 2-F/BTU 0.00031430 Overall Fouling (hr-fl 2.°F/BTU) 0.03976622 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)5.33 905.33 22.23 107,371 0.9189 107,371 Proto-Power Cale: 97-200

Attachment:

I Rev: A Page 19 of 22* Air Mass Velocity (Lbm/hr-ft'), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 09:34:42 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 115 gpm Case 06/22/98 Extrapolation Calculation for Row 4(Dry)II 1.-Air-Side Mass Flow (lbm/hr) 71,194.37 Inlet Temperature (OF) 125.87 Outlet Temperature (0 F) 120.87 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 123.37 Skin Temperature

(°F) 110.23 Velocity *** 3,402.31 Reynold's Number 824*4 Prandtl Number 0.7272 Bulk Visc (lbm/ft-hr) 0.0477 Skin Visc (lbm/ft-hr)

Density (Ibm/fl 3) 0.0645 Cp (BTU/lbm-°F) 0.2402 K (BTU/hr-ft.°F) 0.0158 Tube-Side 57,183.32 104.01 105.57 104.79 106.27 4.23 26,480 4.2880 1.5652 1.5414 61.9318 0.9989 0.3646 Tube-Side hi (BTU/hr-ft 2.°F) 1,260.64 j Factor 0.0081 Air-Side ho (BTU/hr' f2.°F) 8.19 Tube Wall Resistance (hr-ff2.°F/BTU

0.0 0031430

Overall Fouling (hr ft 2.°F/BTU) 0.03976622 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)5.32 905.33 18.46 88,937 0.9191 88,937** Reynolds Number Outside Range of Equation Applicability 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 (0 F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (lbm/ft-hr)

Skin Visc (lbm/ftlhr)

Density (Ibm/ft 3)Cp (BTU/lbm'°F)

K (BTU/hr-ft-°F)

Air-Side 71,194.37 120.87 116.73 0.0203 0.0203 118.80 107.89 3,402.31 829**0.7275 0.0474 0.0649 0.2402 0.0157 Tube-Side 57,183.32 102.72 104.01 103.36 104.60 4.23 26,089 4.3589 1.5887 1.5682 61.9508 0.9989 0.3641 Tube-Side hi (BTU/hr fl2- F) 1,250.27 j Factor 0.0081 Air-Side ho (BTU/hr fl2. F) 8.17 Tube Wall Resistance (hr-ft2- F/BTU 0.00031430 Overall Fouling (hr ft 2-°F/BTU) 0.03976622 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 (BTUihr)5.31 905.33 15.34 73,733 0.9192 73,733** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 20 of 22*** Air Mass Velocity (Lbm/hr'ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 09:34:42 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 115 gpm Case 06/22/98 Extrapolation Calculation for Row 6(Dry)I'Air-Side Tube-Side Mass Flow (lbm/hr) 71,194.37 Inlet Temperature (OF) 116.73 Outlet Temperature (OF) 113.30 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 115.02 Skin Temperature (OF) 105.94 Velocity *** 3,402.31 Reynold's Number 834*, Prandtl Number 0.7277 Bulk Visc (Ibm/ft-hr) 0.0472 Skin Visc (Ibm/ft hr)Density (ibm/fl 3) 0.0653 Cp (BTU/Ibm-'F) 0.2402 K (BTUihr-ft'°F) 0.0156 57,183.32 101.65 102.72 102.18 103.22 4.23 25,766 4.4190 1.6086 1.5911 61.9663 0.9990 0.3636 Tube-Side hi (BTU/hr-ft 2.°F) 1,241.66 j Factor 0.0081 Air-Side ho (BTU/hr.fti 2.F) 8.15 Tube Wall Resistance (hr-ft 2.F/BTU 0.00031430 Overall Fouling (hr- ft 2-°F/BTU) 0.03976622 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)5.30 905.33 12.75 61,173 0.9194 61,173** Reynolds Number Outside Range of Equation Applicability Extrapolation Calculation for Row 7(Dry)II 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 (Ibm/ft hr)Skin Visc (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/Ibm-°F)

K (BTU/hr'ft--F)

Air-Side 71,194.37 113.30 110.45 0.0203 0.0203 111.87 104.33 3,402.31 837*.0.7279 0.0470 0.0656 0.2402 0.0155 Tube-Side 57,183.32 100.76 101.65 101.20 102.07 4.23 25,499 4.4700 1.6254 1.6106 61.9789 0.9990 0.3633 Tube-Side hi (BTU/hr ft2. F) 1,234.50 j Factor 0.0081 Air-Side ho (BTU/hr-ft 2 l-F) 8.14 Tube Wall Resistance (hr ft2. F/BTU 0.00031430 Overall Fouling (hr-ft 2.°F/BTU) 0.03976622 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)5.29 905.33 10.60 50,784 0.9195 50,784** Reynolds Number Outside Range of Equation Applicability Proto-Power Ca/c: 97-200

Attachment:

I Rev: A Page 21 of 22*** Air Mass Velocity (Lbn/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 09:34:42 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Limiting Flow Analysis -- 115 gpm Case 06/22/98 f: Extrapolation Calculation for Row 8(Dry)11 Air-Side Tube-Side Mass Flow (Ibmlhr)Inlet Temperature (fF)Outlet Temperature (fF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)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-°F)

K (BTU/hr'ft'°F) 71,194.37 110.45 108.08 0.0203 0.0203 109.26 102.99 3,402.31 840**0.7281 0.0468 0.0659 0.2402 0.0154 57,183.32 100.02 100.76 100.39 101.11 4.23 25,278 4.5130 1.6396 1.6270 61.9894 0.9990 0.3629 Tube-Side hi (BTU/hr-ft 2.°F) 1,228.54 j Factor 0.0080 Air-Side ho (BTU/hr fl 2.0 F) 8.13 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr- ft 2-°F/BTU) 0.03976622 U Overall (BTU/hr'ftV"°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)5.28 905.33 8.82 42,181 0.9196 42,181** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

I Rev: A Page 22 of 22*** Air Mass Velocity (Lbm/hrft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T Attachment J to Proto-Power Calculation 97-200 Revision A Proto-Power CaIc: 97-200

Attachment:

j Rev: A Page I of 40 Proto-HX Analytical Uncertainty Calculation S [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 eight-row Air Cooler.Governing Heat Transfer Equations Heat transfer calculations associated with a heat exchanger generally reduce to satisfying the following equations:

1) q = U A LMTD Where: q = Heat transfer rate at test conditions (BTU/hr)U = Overall heat transfer coefficient at test conditions (BTU/hr-*F-ft 2)Ao = Heat transfer surface area referenced to outside (air-side) surface (ft )LMTD = Log Mean Temperature Difference at test conditions (IF)and 2) q = ricp (T, -T,)= pQcp AT Where: q = Heat transfer rate at test conditions (BTU/hr)rn = Mass flow rate at test conditions (lbm/hr)cp = Specific heat of cooling water at test conditions (Btu/Ilbm-F)

Tci = Tube-side inlet temperature at test conditions (IF)T, 0 = Tube-side outlet temperature at test conditions (IF)p = Density of tube-side fluid at average bulk temperature at test conditions (lb,/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: 97-200

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J Rev: A Page 2 of 40 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 Tes, 3 ) R = -_ ---U q Test Where: R Overall heat transfer thermal resistance at test conditions (hr-F- f1 2/ BTU)U Overall heat transfer coefficient at test conditions (BTU/hr-°F-ft 2)A,, --Outside heat transfer surface area (ft 2)LMTD Log Mean Temperature Difference at test conditions (OF)q Heat transfer rate at test conditions (BTU/hr)and 4) R =R-h RwA .)Where: Rf Fouling resistance (hr-°F-ft2/

BTU)R Overall heat transfer thermal resistance at test conditions (hr-°F-ft 2/ BTU)ho Outside convection film coefficient at test conditions (BTUft'-F-1ft 2)rlS surface effectiveness Rw ---Wall thermal resistance at test conditions (hr-°F-ft 2/ BTU)Ao-0 Outside heat transfer surface area (1 2 A i uInside heat transfer surface area (fti)hi convection film coefficient at test conditions (BTU/hr-OF-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) 1* =__+ I w +(.ho * ., w Ai hi*Where: R* ---Overall thermal resistance at extrapolation conditions (hr-°F-ft 2/ BTU)Rf =Calculated fouling resistance (hr-[F-ft 2/ BTU)ho,, -Outside convection film coefficient at extrapolation conditions (BTU/hr-°F-ft 2)qS -Fin surface effectiveness R,,* Wall thermal resistance at extrapolation conditions(hr-°F-ft 2/ BTU)SAo Outside heat transfer surface area (ft 2)Ai Inside heat transfer surface area (ft 2)Proto-Power Calc: 97-200

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J Rev: A Page 3 of 40 Ili*= Inside convection film coefficient at extrapolation conditions (BTU/hr-°F-ft 2)and 6) q* (l/R*) Ak, LMTD* = U*Ao LMTD*where: q* = Heat transfer rate at extrapolation conditions (BTU/hr)R* = Overall thermal resistance at extrapolation conditions (lrr-F-ft 2/ BTU)U* = Overall heat coefficient at extrapolation conditions (BTU/hr-°F-ft 2)Ao = Heat transfer surface area referenced to outside surface (ft 2)LMTD* = Log Mean Temperature Difference at extrapolation conditions (1F)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: 9D dD dD AD= AA + -AB +-AC" dA OB 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 = OD AA 2 + -AB + -AC I c? A ) OB cc j 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, (Z 2AA 2 + .ýD AB l A 1 S+ +_D. -A D c' B -D- 6,C) -D-Proto-Power Calc: 97-200

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j Rev: A Page 4 of 40 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 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.

Proto-Power Calc: 97-200

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J Rev: A Page 5 of 40

1) Uncertainty in Calculation of Heat Transfer Area (A-)Goveming Equation q = U A. 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:;" NTNLLcdo(1-2 tFR)AoF. = 7TNTNLLc HFtrr + (HF+d.) (HF-d. + (jFR-tFj j Ao T.= 7rNTNLLc do(1-AtFR)+

A HFtFT+(HF+

do) j(HF d°: +(tFR t jT }where: NT = Number of tubes per row NL = Number of active tube rows Lc, = Effective tube (coil) length (in)do = Tube outside diameter (in)k. = Fin pitch (fins/inch)

HF = Fin height (in)tFR = Thickness of fin at root (in)tFr = Thickness of fin at tip (in)For the case where tFR = tFT = tF, the total area equation reduces to the following:

A.0 o hZ7.NTN LLc d. (I -A~tF) +A {H~tF +( HF+ d.)(F2 j A.,,,=) rNTNLIC d-A2dotF+

-[2HFtF+HF2 -do2}Proto-Power Calc: 97-200

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J Rev: A Page 6 of 40 Assumptions UN-f =0 UNL=0 U ) = 0 Analysis UAo Ao Ud~ 2OA. L / + 2 /o2 2. 2 Y U A O A 0 +~ 614J 0 ~ -j ~ f c A ~ K (~ A ._A 0 o -Y [k,-d 0) ,-AO ) + £- ) KA 0) K,-tF) -A ) K+)_ H AoJ where, CýO -)d.=.'rNTNLL, 1(1- AtF) -Ad.( OA,,J =TNTNL d.-Ad~tF + A 2HF t + HF 2 WEL: ) L~ 2 1 F C £9tF) ={rT I-, HF -d.1 (.9 0 t i =r O A.9H ) = r TN lL .A {tF + H F}I~d 2]Proto-Power Cale: 97-200

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J Rev: A Page 7 of 40 2)Uncertainty in Calculation of Heat Transfer Rate at Test Conditions Governing Equation q-est= nmc, (T1o -T.)= pQc, AT Assumptions Ur =0 UQSW -0 (i.e., temperature and flow rate in the governing equation are measured values with no analytical uncertainites)

Analysis F ___~2 _____ __ r 5 2 2(U~) ( 2 UA__ 2 U q 1 er _" ( test + jtles 2q U_ __I + lest _ _Uq -(~C AT) UP 2+(pQsATV~P) l 2Y tetq ( [' P q)\P(WI zq Proto-Power Calc: 97-200

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J Rev: A Page 8 of 40 3)Uncertainty in Calculation of Thermal Resistance at Test Conditions Goveming Equation R I A AoLMTD.Test U qTest Assumptions ULMTD is negligible Analysis UR = dR) UA2 R LýA, R+ (OR )2( ULNITD'~£9LMTDJ) R OR 2 U R _ ( U LM TD. UA o2 + -A oLM TD .1 ( 2J q R -, ,e ) -R ) , qts2t R)UAo (Evaluated in Section 1)Uqt, (Evaluated in Section 2)Proto-Power Calc: 97-200

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J Rev: A Page 9 of 40 4)Uncertainty in Calculation of Fouling Factor at Test Conditions Governing-Ecuation Rf = R -I h 0 qo R-wj- ')=+/-R --R, Ai~~~ Il 1 ", J_(A.) I KAi Il Where, hoierr = effective outside film coefficient

= (ho) x (is)Assumptions OoRf A R 0_U -fýdRf 2UA (i.e., the uncertainty in dimensions is negligible compared to the thermal resistance and convection coefficient uncertainties)

Analysis URC Rf fd 21 2 0 fR R UR 4-+ ) +t9R fR URr =[ (UR 2 + 21N+ (u U (U 2 (A(3IV Rf [ t, Rf) Khoe Rf) +Ai h+UR (Evaluated in Section 3)Proto-Power Calc: 97-200

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J Rev: A Page 10 of 40

5) Uncertainty in Calculation of Heat Transfer Resistance at Extrapolation Conditions Goveming Equation R*=Rf + I + R,, + (A.+_ )h, 'eff

hi Assumptions CR* A.7-0 cYAo 0 JR*J r ~ (A.~ 2 , --R* 0 (i.e., the uncertainty in dimensions is negligible compared to the thermal resistance and convection coefficient uncertainties)

Analysis__ __ (-- C____ ___2R 2 R*.(Uh. 2]Y2 UR. R ~YU.V R* + (,OR*)( R)+O*[C-Rfh ~* 2 Uh£9R ~*) I e.£9f *)R* ýRW R H U R .RU + _2 (U R )LeR* J ho. ,2 1 R*R+ C-~~ h*2 1 1 Ai (uJ)2 ] Y1 UR, (Evaluated in Section 4)URr = 0 (for extrapolation calculations only, i.e., no fouling calculation)

Proto-Power Calc: 97-200

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J Rev: A Page 11 of 40 6)Uncertainty in Calculation of Heat Transfer Rate at Extrapolation Conditions Goveming Equation q* = (l/R*) (A.) (LMTD*)Assumptions ULMTD ; 0.0 Analysis Uq_q.f~q +Ud 2

2 ( U .> 'M T *(Oc q~' A,) ) :i+ (LMTD*)JY~

q LMTD" )2 Cqý2+ CiZLMTDD 7)2]UR (Evaluated in Section 5)UA, (Evaluated in Section 1)Proto-Power Calc: 97-200

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J Rev: A Page 12 of 40 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 = q, + q 2 + q3 ...... +q, where, "n, is the number of tube rows in the unit.qtot =[( ,3q,., +1 ( dq to Uq 2 (-o2+ f0qlot (" ... ..........

Uq q,, Uq. 21112 qDtot .Iq9 'qtot .dq2. Iq,otf q, )to Assuming that the extrapolated heat transfer rates of the various rows do not depend on each other, the above expression becomes: U F to ý 2 / 2 / 2 '2 ]11/2_ (Uq 1 1 Uq 2 + (Uq +........

I q o ,qtot ' , q ,o., q tot q , qtot q '.Proto-Power Calc: 97-200

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J Rev: A Page 13 of 40 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 (BtullbmnDegF)

=UCp/Cp (%) =UCp =qtest (Btu/hr) =LMTD (DegF) =Uo =R = (l/Uo) =Rf j(hr-DegF-ft^2)/Btul

=Etas =ho [Btu/(hr-DegF-ft^2)1

=ho(eff) [Btu/(hr-DegF-ft^2)1

Uho/ho (%)Uho =hi [Btu/(hr-DegF-ft^2)

Uhi/hi (%) =Uhi=I-eat 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)

Rw j(hr-DegF-ftA2)/Btuj URw/Rw (%)=URw=Wall thermal resistance Uncertainty in wall resistance (as a percentage)

Uncertainty in wall resistance (absolute)

Proto-Power Calc: 97-200

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J Rev: A Page 14 of 40 Page 1 VY02A-AU.XLS 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: (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 (1)(2)(3)(4)(5)(5)(6)(7)(5)Measurement of 5/8" +/- 0.05" yields an uncertainty of 8.0%Measurement of 104.25" +/- 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 1.495" +/- 0.02" yields an uncertainty of 1.34%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: 97-200

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J Rev: A Page 15 of 40 VY02A-AU.XLS Page 2 PROTO-HIX Report -Model Inputs 09:09:14 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 06/22/98 CornEd -- LaSalle Data Report for: 1(2)VY01A

& 02A -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 21179 acfm 150 *F 92 'F 109.4 "F 84.1 *F Tube-Side 150 gpm 105 °F 115.3 'F Fresh Water 0.002 0.002 750000 14.315 1 0 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436" 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) 104.25 10 128 0.012 0.012 1.495 2.000 8.000 20 20 0.527 0.625 1.5 1.452 1 225 Proto-Power Calc: 97-200

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J Rev: A Page 16 of 40 Page 3 VY02A-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 Ca~c: 97-200

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J Rev: A Page 17 of 40 Page 4 VY02A-AU.XLS PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Extrapolation Calculation Summary Air-Side 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 (Ibm/ft-hr)

Skin Visc (lbm/ft.hr)

Density (Ibm/fP)Cp (BTU/Ibm'°F)

K (BTU/hr.ft.°F) 71166.65 148 108.2854 Tube-Side 53702.59 Tube-Side hi (BTU/hr-ft

'.F)100 1 Factor 113.1719 Air-Side ho (BTU/hr.ft2.

F)Tube Wall Resistance (hrhft'.°F/BTU)

Overall Fouling (hr-ftf.°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)0.000314 0-039766 7242.652 707030.5 707030.5 Air-Side Mass Flow (Ibm/hr) 71166.65 Inlet Temperature

(°F) 148 Outlet Temperature

(°F) 139.3637 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (°F) 143.6819 Skin Temperature

(°F) 121.1797 Velocity *** 3400.987 Reynold's Number 802.6572 Prandtl Number 0,725515 Bulk Visc (Ibm/ft-hr) 0.048968 Skin Visc (Ibm/ft-hr)

Density (lbmlft 3) 0.062477 Cp (BTU/lbm.°F) 0.240245 K (BTU/hr-ft.°F) , .0.016215 Reynolds Number Outside Range of Equation Applical Extrapolation Calculation for Row 1(Dry)Tube-Side 53702.59 Tube-Side hi (BTU/hr ft2-°F)110.3055 j Factor 113.1719 Air-Side ho (BTU/hr-ftf.°F)

Tube Wall Resistance (hr.ft. °F/BTU)Overall Fouling (hr-ft 2.°F/BTU)111.7387 114.3282 U Overall (BTU/hr-ft 2-'F)3.981516 Effective Area (ftW)26688.33 LMTD 3.967489 Total Heat Transferred (BTU/hr)1.45846 1.421732 Surface Effectiveness (Eta)61.83519 Sensible Heat Transferred (BTU/hr)0.99882 Latent Heat Transferred (BTU/hr)0.367165 Heat to Condensate (BTU/hr)1246.549 0.008175 8.272452 0.000314 0.039766 5.351471 905.3315 31.73459 153749.5 0.918316 153749.5 Extrapolation Calculation for Row 2(Dry)Tube-Side Air-Side Mass Flow (Ibm/hr) 71166.65 53702.59 Tube-Side hi (BTU/hr-ft 2.°F)Inlet Temperature (F) 139.3637 107.9223 j Factor Outlet Temperature

(°F) 132.1832 110.3055 Air-Side ho (BTU/hr.ftl.°F Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft 2.°F/BTU Outlet Specific Humidity 0.020268 Overall Fouling (hr.ftl.°FIBTU)

Average Temp (°F) 135.7735 109.114 Skin Temperature

(°F) 116.9946 111.2983 U Overall (BTU/hr-ftl-°F)

Velocity *** 3400.987 3.979115 Effective Area (ft2)Reynold's Number 810.7773 ** 25995.7 LMTD Prandtl Number 0.726209 4.083826 Total Heat Transferred (BTU/hr)Bulk Visc (lbm/ft-hr) 0.048477 1.497319 Skin Visc (lbrm/ft-hr) 1.464863 Surface Effectiveness (Eta)Density (Ibm/hf) 0.063235 61.8725 Sensible Heat Transferred (BTU/hr)Cp (BTU/Ibm.

F) 0.240245 0.998845 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft-*F) 0.016037 0.366218 Heat to Condensate (BTU/hr)*" Reynolds Number Outside Range of Equation Applicability

=))1228.617 0.008146 8.238629 0.000314 0.039766 5.330976 905.3315 26.48671 127832.8 0.918616 127832.8 Air-Side Extrapolation Calculation for Row 3(Dry)Proto-Power Ca~c: 97-200

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J Rev: A Page 18 of 40 VY02A-AU.XLS Page 5 PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Mass Flow (Ibmrhr) 71166.65 Inlet Temperature (IF) 132.1832 Outlet Temperature

(°F) 126.2057 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp ('F) 129.1941 Skin Temperature

(°F) 113.5129 Velocity *°° 3400.987 Reynold's Number 817.7239 Prandtl Number 0.726741 Bulk Visc (Ibm/ft-hr) 0.048065 Skin Visc (Ibm/ft hr)Density (IbrrVfl')

0.063881 Cp (BTU/Ibm-°F) 0.240245 K (BTU/hr-ft.'F) 0.015889** Reynolds Number Outside Range of Equation Applicab 53702.59 Tube-Side hi (BTU/hr-ftl'.F) 105.9385 j Factor 107.9223 Air-Side ho (BTU/hr.ft2.°F Tube Wall Resistance (hr-f12-°F/BTU)

Overall Fouling (hr-ftl.°F/BTU) 106.9309 108.7712 U Overall (BTU/hr-ft'-F) 3.977169 Effective Area (ft')25424.42 LMTD 4.184867 Total Heat Transferred (BTU/hr)1.530964 1.502521 Surface Effectiveness (Eta)61.90278 Sensible Heat Transferred (BTU/hr)0.998873 Latent Heat Transferred (BTU/hr)0.365416 Heat to Condensate (BTU/hr))1213.64 0.008123 8.210501 0.000314 0.039766 5.313799 905.3315 22.12061 106416.7 0.918865 106416.7 Extrapolation Calculation for Row 4(Dry)Tube-Side Air-Side Mass Flow (Ibm/hr) 71166.65 53702.59 Tube-Side hi (BTU/hr-ftt.°F)

Inlet Temperature

(°F) 126.2057 104.2853 j Factor Outlet Temperature

('F) 121.2244 105.9385 Air-Side ho (BTU/hr-ftl'.F Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ftl.°F/BTU Outlet Specific Humidity 0.020268 Overall Fouling (hr-ft1.°F/BTU)

Average Temp (°F) 123.7151 105.1112 Skin Temperature

('F) 110.6127 106.6611 U Overall (BTU/hr-ff2.*F)

Velocity **" 3400.987 3.975581 Effective Area (ft')Reynold's Number 823.6471 ** 24951.62 LMTD Prandtl Number 0.72715 4.272217 Total Heat Transferred (BTU/hr)Bulk Visc (Ibm'ft-hr) 0.04772 1.559974 Skin Visc (Ibm/ft-hr) 1.535208 Surface Effectiveness (Eta)Density (Ibm/ft 3) 0.064428 61.9275 Sensible Heat Transferred (BTU/hr)Cp (BTU/lbm.°F) 0.240245 0.998902 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft.'F) 0.015766 0.364737 Heat to Condensate (BTU/hr)** Reynolds Number Outside Range of Equation Applicability

=))1201.114 0.008103 8.187088 0.000314 0.039766 5.299401 905.3315 18.48393 88680.63 0.919073 88680.63 Extrapolation Calculation for Row 5(Dry)Air-Side Tube-Side Mass Flow (Ibm/hr) 71166.65 53702.59 Tube-Side hi (BTU/hr.ftl-°F)

Inlet Temperature

('F) 121.2244 102.9065 j Factor Outlet Temperature

('F) 117.0697 104.2853 Air-Side ho (BTU/hr-ftt.°F)

Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft2-OF/BTU)

Outlet Specific Humidity 0.020268 Overall Fouling (hr-ftI-°F/BTU)

Average Temp (°F) 119.1471 103.5958 Skin Temperature

(°F) 108.1955 104.8999 U Overall (BTU/hr-ft2.°F)

Velocity *** 3400.987 3.974283 Effective Area (ft2)Reynold's Number 828.6851 '* 24560.25 LMTD Prandtl Number 0.727467 4.347231 Total Heat Transferred (BTU/hr)Bulk Visc (lbm/t.hr) 0.04743 1.584832 Skin Visc (Ibm/ft.hr) 1.563402 Surface Effectiveness (Eta)Density (Ibm/ft3) 0.064893 61.94772 Sensible Heat Transferred (BTU/hr)Cp (BTU,,bm-'F) 0.240245 0.998929 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft-'F) 0.015664 0.364166 Heat to Condensate (BTU/hr)Reynolds Number Outside Range of Equation Applicability Pr At R(Extrapolation Calculation for Row 8(Dry)1190.652 0.008086 8.167578 0.000314 0.039766 5.287339 905.3315 15.45193 73965.21 0.919246 73965.21 oto-Power Catc: 97-200 tachment:

J-v: A Page 19 of 40 Air-Side Mass Flow (Ibm/hr)Inlet Temperature

('F)Outlet Temperature

('F)Tube-Side 71166.65 53702.59 Tube-Side hi (BTU/hr-ft'-'F) 117.0697 101.7556 j Factor 113.6019 102.9065 Air-Side ho (BTU/hr-ft'-°F) 1181.899 0.008071 8.151309 VY02A-AU.XLS Page 6 PROTO-HX Report -- Extrapolation Calculation Output for Limiting Flow Case Inlet Specific Humidity Outlet Specific Humidity Average Temp ('F)Skin Temperature

(°F)0.020268 0.020268 115.3358 106.1782 Tube Wall Resistance (hr-ft"°F/BTU)

Overall Fouling (hr.ftl.°F/BTU) 102.3309 103,4274 U Overall (BTU/hr.ftl-°F)

Velocity-3400987 3.9 Reynold's Number 832.9599 **Prandtl Number 0.727713 4.4 Bulk Visc (Ibm/ft-hr) 0.047186 1.6 Skin Visc (Ibm/ft-hr) 1.5 Density (Ibm/ft 3) 0.065285 61.Cp (BTU/Ibm'°F) 0.240244 0.9 K (BTU/hrft-F) 0.015578 0.3** Reynolds Number Outside Range of Equation Applicability 73217 11482 06085 67634 96434 98954 63684 Effeclive Area (ftl)24235.25 LMTD Total Heat Transferred (BTU/hr)Surface Effectiveness (Eta)Sensible Heat Transferred (BTU/hr)Latent Heat Transferred (BTU/hr)Heat to Condensate (BTU/hr)0.000314 0.039766 5.277229 905.3315 12.92208 61737.04 0.91939 61737.04 Extrapolation Calculation for Row 7(Dry)Tube-Side Air-Side Mass Flow (Ibmlhr) 71166.65 53702.59 Tube-Side hi (BTU/hr-ftf-*F)

Inlet Temperature

(*F) 113.6019 100.7945 j Factor Outlet Temperature

(*F) 110.7056 101.7556 Air-Side ho (BTU/hr~ftl.°F Inlet Specific Humidity 0.020268 Tube Wall Resistance (hr-ft2-°F/BTU Outlet Specific Humidity 0.020268 Overall Fouling (hr-ft 2 1-F/BTU)Average Temp (*F) 112.1537 101.2749 Skin Temperature

(°F) 104.4937 102.1964 U Overall (BTU/hr-ft 2.°F)Velocity **" 3400.987 3.972339 Effective Area (ft')Reynold's Number 836.5802 ** 23965.08 LMTD Prandtl Number 0.727905 4.466304 Total Heat Transferred (BTU/hr)Bulk Visc (Ibm/ft-hr) 0.046982 1.624191 Skin Visc (Ibm/ft-hr) 1.608373 Surface Effectiveness (Eta)Density (lbrmft 3) 0.065617 61.97803 Sensible Heat Transferred (BTU/hr)Cp (BTU/lbm-*F) 0.240244 0.998977 Latent Heat Transferred (BTU/hr)K (BTU/hr-ft.°F) 0.015506 0.363278 Heat to Condensate (BTU/hr)** Reynolds Number Outside Range of Equation Applicability

=))1174.576 0.008059 8.137733 0.000314 0.039766 5.268757 905.3315 10.80974 51562.15 0.919511 51562.15 Air-Side Mass Flow (Ibmlhr) 71166.65 Inlet Temperature

(°F) 110.7056 Outlet Temperature

(°F) 108.2854 Inlet Specific Humidity 0.020268 Outlet Specific Humidity 0.020268 Average Temp (°F) 109.4955 Skin Temperature

(°F) 103.0865 Velocity *** 3400.987 Reynold's Number 839.6409 Prandtl Number 0.728057 Bulk Visc (Ibm/ft-hr) 0.04681.1 Skin Visc (Ibm/ft-hr)

Density (Ibm/ft3) 0.065696 Cp (BTU/lbm-°F) 0.240244 K (BTU/hr-ft.=F) 0.015447** Reynolds Number Outside Range of Equation Applical Extrapolation Calculation for Row 8(Dry)Tube-Side 53702.59 Tube-Side hi (BTU/hr-ft 2."F)99.99134 j Factor 100.7945 Air-Side ho (BTU/hr-ft 2-°F)Tube Wall Resistance (hr.ff2-°F/BTU)

Overall Fouling (hr-ft 2-°F/BTU)100.3927 101.1668 U Overall (BTU/hrft 2.F)3.971615 Effective Area (ftW)23740.2 LMTD 4.512945 Total Heat Transferred (BTU/hr)1.639576 1.626064 Surface Effectiveness (Eta)61.98934 Sensible Heat Transferred (BTU/hr)0.998987 Latent Heat Transferred (BTU/hr)0.362937 Heat to Condensate (BTU/hr)1168.449 0.008049 8.126396 0.000314 0.039766 5.261658 905.3315 9.045035 43086.43 0.919611 43086.43 Air Mass Velocity (Lbm/hr.ft 2). Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 20 of 40 VY02A-AU.XLS Page 7 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 1)I. PROTO-HX Output -Fouling Calculation di (ft) =Al (ft'22)Ao (ftA2) =AoIAI =do (ft)Udoldo n%)Udo (It)Nt =NI =Lambda (finslft) f L (ft)=UL/L (%) =li. PROTO-HX Output -- Extrapolation Calculation di (ift) = 0.043916MO67 Al (ft^2) = 23 97108819 Ao (ftA2) = 905.3314736 Ao/Ai 37.70622391 do (ft) 0 052083333 Udoldo (%) = 8 Udo (ft) = 0.004166567 Nt = 20 NI 2I" Lambda (finslft) 120 L (ft) a8 675 ULIL (%) =0.24 UL(ft) =tfin (ft) =Utfln/ttin(%

blhii/fn (%)) -Mdotc (Ibm/hr)0 (Ft'13/hr)

DT (DegF)=rho (!bmrdftA3)=

Urhof rho (%) =Cp (Btuflbm~l~egF)=

UCPICp (%)=Utfin (ft)Uhfln (it) =Urho =Ucp=tfin (ft) =Utfinitfin M%)bu n (ft) =Ilhfin/hrin

%Mdotc* (Ibm/hr)=Q* (FtA3/hr)DT* (Deg F)rho* (IbM/ftA3)

Urho'frho*

(%)Cp* (BtuI~brnIegF)=

UCpl/Cp* (%) ;X q* (Btu/hr)=LMTD* ( DogF)Uo, R'=(1/Uo*)

RI [(hr-DegF-ft,'2)IBtu]

Etas=ho" [BtuI(hr-DegF-ftA2)j ho*(eff) (5tuI(hr-DagF-ftA2)]

Uhotlhol M%=hi* [Stu/(hr-DeqF-ft112)j=

Uhirlhi (%I) =Rw* ((hr-DegF~ttA2)/Btu]

URwlRw' (%)Utfin (ft) =0.1245813331.Th ran (ft) 0.00j~16694171 53jiOZ59431 61.351479J Urho* 1.37086 0.9900251 UCp* 001978405 153749.4783 31.7345SM8 5.351471122 0.188864505

0.0 39766224

0.918116031 8-27245205 7.596725335 15 Uho, = 1.1395088 Uhl*=10 URw* j.26jj-q (Btuthr) =LMTD (DegF)=Uo=R = (IUo)=Rf j(hr-OegF-ftA12)/Rtuj E~tasc ho [BtuIjhr.OegF-ftA2)]

=ho(ffM [StuI(hr-DegF-ft^2)1 Uho/ho {/%)=hi [Btu/(hr-DegF-ftA2)]

Uhil/h (%) =Rw [(hr-OegF-ftA2)/Btul URw/Rw (%) =Uho =Uhi =URw =Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 21 of 40 VY02A-AU.XLS Page 8 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 1)I Analytical tlncertaintv in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAoIAo UAo 905.33147 0.05208 0.00417 8.68750 0.02085 0.00100 0.00004 0.12458 0.00167 0.04067 36.82236 Derivatives:

-5862.45 104.21 9497.82 16451 97 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*0.18686 7.59673 1.13951 1246.54875 186.98231 0.00031 0.00001 0.03977 .0O.0*0 0.10843 0.02026 6 Analytical Uncertainty in Extranolated Heat Transfer q* R° UR* Ao UAo LMTD* Uq'lq° Uq°153749.4783 0.18686 0.02026 905.33147 36.82236 31.73459 0.11581 17805.20662 Proto-Power Caic: 97-200

Attachment:

J Rev: A Page 22 of 40 VY02A-AU.XLS Page 9 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 2)I. PROTO-HX Output -Fouling Calculation di (ft) =Al (ftA2)AO (Wft2)Ao/Al =do (if) =Udo/do(%)Udo (ft)=Nt =NI =Lambda (finsift)

=L (%) =UL/L M%II. PROTO-HX Output --Extrapolation Calculation di (ft) = 0.043916667 Ai (f-2) = 23.97198819 Ao (ftA2) 905.331473r)

Ao/A= 37 76 4122301 do (ft) 0.052683'3M Udo/do (%) = 8 Udo (ift) = 0.004166,60?

Nt = I I NI = f2]Lambda (finsift)

=12 L (ft) = '"- -UL/L (%) = 0.241 UL(ft)tfln (ft) =Utfinltfin

(%)hfin (ft) =LImhinlfian

(%)=Mdotc (Ibm/hr) =o (FtA3/hr)

=DT (DegF) =rho (IbnmftA3)

Urho/rho (%) =Cp (Btu/Ibm/DegF)

=UCpICp (%) =Utfin (ft) =.Ilhin (ft) =Urho =UCp =tfm (ft) =Utfinlffin

(%) =hIn (ift) =llhfli=lhfln

(%.) =Mdotc* (Ibndhr).=

Q* (FtA3/hr)

=DT* (DegF)rho* (IbMftA3)

=Urhcf/rho-(%)=Cpt (BtusIbnmdDegF)

=UCp*/Cp* (%) =q (Btuihr) =LMTD' (DegF) =Uo* =R* = (1/Uo*)Rf [(hr-DegF.ftA2)/Btu]

Etas =ho* [Btu/(hr-DegF-ftA2)]

=ho*(eff) [BtuI(hr-DegF-itA2)]

Uho'/ho* (%) =hi* [BtuI(hr-DegF-ftA2)j

=Uh*/hr (%) =Rw' ((hr-DegF-ftA2)/Btu1

=URw*/Rw* (%) =0.001 4.17I Utfin (if) = 0X04f7 0.124583333 (Thfin (ft) [ .00169417 5 3702.5941 867.9558527I 61.87249518 ffi Urho° = .237449904 UCp 0019j976901 127832.8305 26.4867136 5.3309758 O 187682919 0.03976e224 0.918615579 8.238628585 7.568132571 151 Uho" 1.1'3,12198861 Uhl* 184.2925779w F- 6000314-31 URw* = q (Btulhr) =LMTD (DegF) =Uo=R = (1U1o)Rf [(hr-DegF~ftA2)Btuj

=Etas =ho [Btu/(hr-DegF-ftA2)1

=ho(eff) [Btu/(hr-DegF-ft^2)]

=Uholho (%) =hi [Btu/(hr-DegF-ftA2)]

=UW/hi (%) =Rw [(hr-DegF-ftA2)/Btu]

URw/Rw (%) =Uho =Uhl =URw =Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 23 of 40 VYO2A-AU.XLS Page 10 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 2)I Analytical Uncertainly in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin 905.33147 0.05208 0.00417 8.68750 0.02085 0.00100 0.00004 Derivatives:

-5862.45 104.21 9497.82 hfin Uhfin UAoIAo UAo 0.12458 0.00167 0.04067 36.82236 16451.97 2 Analytical Uncertainty in Test Heat Transfer Rate 3 Analytical Uncertainty In Observed Heat Transfer Resistance (R): 4 Anahlical Uncertainty In Observed Rf 5 Analhtical Uncertainty in Overall Extrapolation Heat Transfer Resistance:

R* ho° Uho* hi* Uhi* Rw*0.18758 7.56813 1.13522 1228.61719 184.29258 0.00031 URw* Rf URf UR'IR* UR*0.00001 0.03977 0.00000 0.10848 0.02035 6 Analhtical Uncertainty in Extrapolated Heat Transfer q. R' UR' Ao UAo LMTD* Uq.lq" Uq" 127832.8305 0.18758 0.02035 905.33147 36.82236 26.48671 0.11586 14810.09844 Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 24 of 40 VY02A-AU.XLS Page 11 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 3)I. PROTO-HX Output -rouling Calculati di (ft) =Ai (ftA2) =Ao (itA2) =AolAi =do (it)Udo/do (%) =Nt NI =Lambda (finsift)

-L (ft) =ULUL (%)tfin (ft)=Utfin/tfin

(%I hfln (It) =Uhfin/hfln

(%) =Udo,(ft)=UL(ft) =II. PROTO-HX Output -- Extrapolation Calculation di (it) ________Ai (ftA2) = 2397108819 Ao (fit^2) 905.33147,U; AoIAI =37.76622391 do (ift) = (0.052083333 Udo/do (%)Udo (tt)= 0.004166007 Nt. =2 NI = 2 Lambda (fins/ft)

[- 120 L (ft) = 8s.6 ULUL (%) = L ~3)= --UL(ft)0.02085 tfin (it) =0.0 Utfinitlin

(%)4 Wtin (ft) = 0.00047 Kin ift)- 0,14533 UIhfln/hfjn

(.) 34 l lhfin (ft) 0.001669417 Mdotc* (Ibm/hr) 53702.59431 Q* (Ft^3/hr)

= 8751211 DT* (DegF) =134 rho* (Ibrn/ift3)

=61.902707 Urho/rho (%) = 21 Urho* 1.238055614 Uffin (ft)'I:ih fin (it)Mdotc (ibrrhr) =0 (Ft^3/hr)DT (DegF)rho (IbIfftA3)

=Urho/rho (%)Urho Cp (Btu/lbm/DegF)

UCp/cp M =UCp =q (Btulhr) =LMTD (DegF)Uo =R -(1/1.o)Rf [(hr-0egF-ft112)/Btuj Etas =ho [BtuI(hr-DegF-ftA2)I ho(eff) [B~tu/(hr-OegF-ftA2)j Ulholho (%)hII (Btu/(hr-DegF-ftt2)1 Uhi/hi (%)=Rw [(hr-OegF-ft^2)IBtuJ LIRw/Rw M%)=Cp* jBtuIlbmVDegF)

UCp*/Cp* (%)q* (Btufhr) =LMTD* ( DegF)Uo*R*= Olljol" Rf [(hr-DegF-ftA2)JBtuj Etas =ho' [Btu/(hr-DeqF-ft42)]

ho*(eff) CBtuI(hr.DegF-ftA2)1 Uho'/ho* (%)=hi' (BtuI(hr.DegF-ifA2)J Uhi/lhI (%) =Rw' [(hr-DegF-ft^2)jBtu]

URw*/Rw* (%) =0.998873053 106416.891D 22.120600653 5.313798755 0.188189287

0.0 39766n24

0.91886488 8.210500587 7.544340639 1s Uho* 1.131F351096 Uh'= 182.459679 URw* 315~Uho =UhI =URW =Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 25 of 40 VY02A-AU.XLS Page 12 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 3)1 Analytical Uncertainly in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hin Uhfin UAolAo UAo 905.33147 0.05208 0.00417 8.68750 0.02085 0.00100 0.00004 0.12458 0.00167 0.04067 36.82236 Derivatives:

-5862.45 104.21 9497.82 16451.97 2 Analytical Uncertaint' 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*0.18819 7.54434 1.13165 1213.63979 182.04597 0.00031 0.00001 0.03977 0.00000 0.10852 0.02042 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R' UR" Ao UAo LMTD* Uq*/q* Uq" 1064166914 0.18819 0.02042 905.33147 36.82236 22.12061 0.11590 12333.18129 Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 26 of 40 VY02A-AU.XLS Page 13 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate J (Row 4)I. PROTO-HX Output -- Fouling Calcula di (ft) =Al (ft^2)Ao (ftM2)Ao/Ai do (ft)Udoldo (%) =Udo (ft)Nt =NI =Lambda (fins/ft)

=L (ft)ULIL(%) =II. PROTO-HX Output -Extrapolation Calculation di (ft) = 0.043q16C,67 Al (ftA21 Ai(t2) =23.57 M88 101 Ao (ftA2) 90S.&.1431 I AoIAI 3r7c.O223011 Udo() LiI Udo (ft) = 0.004166667 Nt -=2 NI = 2, Lambda (finslft)

= 120I L (ft) = ULLL =%)0=2 0.245 ULMff 0 .020851 UL(ft) : timn (ft) -Utfinltfiui

(%)hffn W()t1hrin/Whifg(%

Utfln Ift)t.Ihrin (ft)Mdotc (ibmnhr)Q (Ft^3Ihr)

=DT (DegF) =rho (IbmtA3) =Urho/rho )Urho -.Cp (Btu/ibmIDegF)

UCpICP 4%)UCp A tfin (ft) =Utfinltfin(%

hifln (ft) -tLfhrnnhflii M%) -Mdotc* (lbmlthr)=

Q* (Ft'i1hr)DT* (OegF)=rho* (lbmiftA13)=

U~rhalfrhov N% -Cp* (Btu~lbmlDegF)

UCp*ICP* (%) =qr (Btu/hr) -LMTO* ( DegF)U0, R*= (lIUo')=Rf [(hr-OegF-ftA2)lBtuJ Etas=ho* [Btui(hr-DegF~ftA 2)J =ho*(eff) CBtuI(hr-DegF-fttA2)j UholIho' N%=h1* [BtuI(hr-DegF-ft^2)j Uhi'lhi (%) =Rw' [(hr-DegF-ft112)/Btuj URwAJRw' (%) =F 1453333 E.Win (ft)= -S .894 53702.59431 867.MMJ 1.6523721 Urhio* ,35W UCP= 0.097 80,3 88M.83.39 18.48393207 5.29W4128 0.188700562

0.0 39766224

0.91907252, 8.187087026 7 524527651 15 Uho* 1.128079133 12011~3142]77 Uhr~ 11 URw'=q (Btufhr) =LMTD ( OegF)=Uo=R = (/Uo)Rf [Qhr.OegF-RA2)/BtuJ Etas : ho [BtuI(hr-OegF-ftA2) ho(eMf [BtuJ(hr-0egF-ftA2fl Uho/ho (%) =hi [BtuI(hr-DegF-ftA2)1 Uhi/hl (%)=Rw ((tlr-DegF-ftA2)IBtu1 URwIRw (%) =Uho Uhi URw Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 27 of 40 VY02A-AU.XLS Page 14 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 4)I Analytical Lincertainty in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 905.33147 0.05208 0.00417 8.68750 0.02085 0.00100 0.00004 0.12458 0.00167 0.04067 36.82236 Derivatives:

-5862.45 104.21 9497.82 16451.97 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* RI URf URIfR* URf 0.18870 7.52453 1.12868 1201.11428 180.16714 0.00031 0.00001 0.03977 0.00000 0.10856 0.02049 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R° UR* Ao UAo LMTDO Uq./q* Uq*88680.6339 0.18870 0.02049 905.33147 36.82236 1848393 0.11593 10280.57880 Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 28 of 40 VY02A-AU.XLS Page 15

-Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 5)I. PROTO-HX Output -- Fouling Calculation di (ft) =Ai (ftA2) =Ao (ftA2)Ao/Ai =do (ft)Udo/do (%) =Udo (ft) =Nt =NI a Lambda (fins/ift)

L (ft)ULJL (%) =I1. PROTO-HX Output -Extrapolation Calculation di (ft) = 0.043916A47 A! (ftA 2) [ 2397198819 Ao (ftA2) 905.3314736 AoAi =37.7%22391 do (ift) 0.052083333 Udoldo (%)Udo (ft) = 0.0041667 Nt= 0 NI -Lambda (fins//t)

=L (ft ).687 UUL() 0024 ULMf) =70 002085 UL(ft)=tfin (ft) =Utfinitfin

(%I =hn (ft.) -11hea/Iheln

(%) -Utfin (ft).=Uhfin (ft)=Mdotc (Ibmlhr) =Q (FtA3/hr)DT (DegF)rho (Ibmrftf3)

Urho/rho (%) =Urho Cp (Btuflbm/VDegF)=

UCpICp (%) =UCp tfin (ft) =Utfinitfln

(%)4 hrin (ft) -UWifin/hIfin M%)Mdotc* (lbmlhr)Q' (Ft'A3ihr)=

DT*(OegF)rho* (ibmfftA3)

=Urho~lrho*

MV =Cp* (Gtuflbmt/OegF)

UCP*/Cp* (%)q* (Btufhr) =LMTD* ( DeqF)=~o* =R'= 011.1o')RI [(hr.OegFftA 2)/Btul Etas ho* [Btui(hr4:DogF-ftA2)1 ho*(eff) [Btui(hr-DegF-ft'2)j Uho~iho* (%) =hi' IBtuI(hr-DegF-ftA'2)]

Uhi~fhf (%) =Rw* C(hr-DegF-ftA'2)/Btuj URw*iRwl (%) =Lhfin (ft) 0.0000417 66.918227 1j.37817728 61.9772338 Urho* 28048.0.99892833 UCp* = 0.1787 73965.20571 1 5.45102966 S .287338658 0.189131067

0.0 39766224

0.919245643, 8 167578221 7.50801691 15 Uho* 1.126201504 1190.52195 URw 6.801E0 q (Btulhr) =LMTD ( DegF)U0 =R =(litlo)RIF [(h,.DegF-ftA2)IBtul Etas =ho CBtuI(hr-DegF-ftAI2)]

ho(eff) (BtuI(hr-DegF-ftA2)j=

Uholho (%) =hi jBtuI(hr4OegF-ft-%2)j Uhilhi (%) =Rw [(hr-OegF~ttA 2)IBtu]URw/Rw (%)=Uho Uhi =URw D Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 29 of 40 VY02A-AIJ.XLS Page 16 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 5)I Analytical Uncertaintv in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAoIAo UAo 905.33147 0.05208 0.00417 8.68750 0.02085 0.00100 0.00004 0.12458 0.00167 0.04067 36-82236 Derivatives:

-5862.45 104.21 9497.82 16451.97 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*0.18913 7.50801 1.12620 1190.65220 178.59783 0.00031 0.00001 0.03977 0.00000 0.10859 0.02054 6 Analytical Uncertainty in Extrapolated Heat Transfer q" R' UR° Ao UAo LMTD" Uql/q. Uq.73965.2057 0.18913 0.02054 905.33147 36.82236 15.45193 0.11596 8576.66300 Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 30 of 40 VY02A-AU.XLS Page 17 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 6)I. PROTO-HX Output -- FoulingCalculation dI (if) =Ai (ft^2) =Ao (ftA2)Ao/Ai =do (Yt) =Udo/do (%)Udo (ft) =Nt=NI=Lambda (finslft)

=L (ft)=UL/L (%)II. PROTO-HX Output -Extrapolation Calculation di (ft[ = 0 0430, 56667 Ai (ftA2) 23 W 7198819 Ao (fta2) o905.3314736 Ao/Ai 37,76622391 do (ft) 0 052083333 Udo/do (%) =Udo (ft) 0.0041667 Nt 20ZI~NI: :j j Lambda (fins/ft)

=12 L (ft) 8.67s5 ULIL (%)=.24 UL(ft) =tfin (ht)=Utflnitfin(%

hfin (ft) =IUhrin/hriin()

Utfin (fl)Uhflo (if)Mdotc (Ibmlhr)0 (Ft'3/hr)S DT (OeqF)rho (Ib~m/ftA3)

Urtiorho (%) =Urho =Cp IBtuflbmnIIegF)=

UCp/Cp (%) =UCp =tfin (ft)=Utfiniftin(%

hrMi (fl) -tihOndhIln(%

Mdotc, (lbrrvhr)Q* (Ft^3/hr)=

DT' (DegF)rho* (lbrnlff 3) =Urholfrho*

(1/) =Cp' (BtuIlbrnJDegF)=

UCp*ICP (%)q* (Btu/hr)LMTD* ( DegF)Uo* =R = (lIUo*)Rf [(hr43egF

_tA 2)/Btul Etas =ho* [BtuI(hr-DegF-ftA2)J=

ho*(eff) [1BtuI(hr-OegF-ftA2fl U ho/ho' (%) =hI' [BtuI(hr-DOegF-ftA2)]

Uhr/hi (%) =Rw'[(hr-DegF-fi1A2)IBtuj URw~fRw* (%)=WinIIIIl=0.124583333 Ult~n (t) =t1 0.001669417 8L6.693232 1.1082416 Urho* .32W UCpz 0.1996 61737.04355 12.02207564 5.277228882 0.189493392

0.0 39766224

0.919390072 8.151309092

= ~7.494232&%6 151 Uho 1 1124134808 Uhl* = jja~s URW* = E ~q (Btuthr) =l-MTD ( DegF)UO =R = (I/Uo)Rf [(hr-DegF-fta2)IBtuI

=Etas =ho [BtuI(hr-DegF-ft,2)1

=ho(eff) [Btu/(hr-DegF-ft^2)J Uho/ho, (%)=hi [Btu/(hr-DegF.ft'12)j Uhilhi (%) -Rw [(hr-DegF-ft^2)jBtu]

URw/Rw (%) =Uho =Uhi =URw=Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 31 of 40 VY02A-AU.XLS Page 18 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 6)i Analytical Uncertainty in Ileat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAoIAo UAo 905.33147 0.05208 0.00417 8.68750 0.02085 0.00100 0.00004 0.12458 0.00167 0.04067 36.82236 Derivatives:

-5862.45 104.21 9497,82 16451.97 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*/R* UR°0.18949 7.49423 1.12413 1181.89904 177.28486 0.00031 0.00001 0.03977 0.00000 0.10861 0.02058 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R" UR* Ao UAo LMTD* Uq./q* Uq.61737.0435 0.18949 0.02058 905.33147 36.82236 12.92208 0.11598 7160.13511 Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 32 of 40 Page 19 VY02A-AU.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 7)I. PROTO-HX Output -Fouling Calcul;di (fi) =At (ft12) -Ao (ft-2) =AotAi =do (ft)z Udotdo (%0/)Udo (t) =Nt=NI=Lambda (fins/ft)L (t) =ULIL (%)It. PROTO-HX Output -- Extrapolation Calculation di (ft) = 0.0439166T7 At (ftA2) 23.07198819 AO (ftA2) = [ 05.314736 Ao/Ai 37 76622391.do (ft) = o0s52DW .Udoldo (%a =Udo (ft)= 00o416667 Nt =20 Lambda (flnslft)

=12 L (t) 8.6875 UL/L (%) = 0,224 UL(ft) 0.02085, UL(ft) =tfln (ft) =Utfin/tfin

(%) =huni (1i) =1:hifin/hfilb

(%)=Mdotc (Ibmlhr) =Q (Ft^3fhr)DT (DegF)rho (IbrndftA3)

=Urho/rho (%) =Cp (BtudIbmnDegF)

=UCp/Cp (%) =UWfin (ft)!In (ft) =Urho =UCp =tfin (ft)=Utfinitfin

%=hflin (ft)11fiihfin/(%)11 Mdotc' (bmlhr)=0' (Ft"3Ihr)=

DT* (begF)rho* (lbrrdftA3)=

Urhofrto*

M%)=Cp* (BWI~bm/DeqF)

UCpI/Cp (%I) =q* (Btuihr)=LMTD* ( DegF)Uo* =R*= (I/Uo*)=RI [(hr-DegF41A2)/Btuj Etas ha' jBtuI(hr-DegF-ftA2)j ho*(eff [Btu/(hr-DegF~ftA2)J Uhollho M%)a hi* [Btu1(hr-DeqF-U'A2)]

Uhl~'hI' N% =Rw* j(hr-DegF-fta2)!9tuj URw*/Rw* (%)=Utfin (ft) .041[ 5370.543 Urho' =1 .35M 10.80974049 5.2667570ig 0.189798086

0.0 39766224

00119510644 a.i37732S39

-7.482731685 15 Uho'= 1.122409753 Uhi*URW =' .80E0 q (Btulhr) -LMTD ( Deg F)Uo =R =(111,1o)=

Rf [(hr43egF

_ftA 2)/Btul Etas =ho (BtuI(hr-OegF-ftA 2)11 hojeff) [BtusI(hr-DegF-ftA12)l Uho/ho M%) =hi (Btu/(hr-DegF-fl"2)J UhINh (%)=Rw I(hr-O%3gF~ftA 2)Btul URWw/R M) =Uho w Uhi =URw : Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 33 of 40 Page 20 VY02A-AU XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 7)I Analytical Uncertainty in Iieat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 905.33147 0.05208 0.00417 8.68750 0.02085 0.00100 0.00004 0.12458 0.00167 0.04067 36.82236 Derivatives:

-5862.45 104.21 9497.82 16451.97 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 UIt/R* UR*0.18980 7.48273 1.12241 1174.57650 176.18647 0.00031 0.00001 0.03977 0.00000 0.10863 0.02062 6AnalytclUncertaintvin Extraplated HeatTransfer

q. R' UR* Ao UAo LMTD* UqIq° Uq" 51562.1547 0.18980 0.02062 905.33147 36.82236 10.80974 0.11600 5981.03791 Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 34 of 40 VY02A-AU.XLS Page 21 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 8)I. PROTO-HX Output -- Fouling Calcuh di (ft) =Al (ftA2) =Ao (ft^2)=AoIAI do (ft) =Udoido (%) =Udo (ft) =Nt NI =Lambda (finsfft)L (ft)UL/L(%)H1. PROTO-HX Output -Extrapolation Calculation di (ft) = 0.01396667 Ai (ftA2) = 23.97198819

.Ao (ft^2) = 90 331.7j AofAI= 37 766223131 do (ft) = 0.052083333 Udo/do (%) 8 Udo (ft) = .004166,67j Nt =NI=Lambda (flnsfft) 1 L (f) = .AV5 ULJL (%)= 0.24 UL(ft) 0n.o02085s UL(ft)tffin (ft) =Utflintfln()=

MIDi (ft) =Mdotc jIbmlhr)Q (Ft'A3Ihr)

DT (DegF)rho (IbmiftA3)

Urholrho (%) =Cp (Btu/lbmIOegF)=

UCp/Cp (%)Utfin (ft)LUhfli (It)f Urho UCp tMin (ft) =Utflnitftn(%=

hrini (ft) -Uhfiln/hifn

(.Mdotc* (Ibml~hr)Q* (Ft'131hr)

DT* (DegF)rho* (IbmIftR3)

Urho*'/rho'

(%)=Cp* (BtuIlbin/OegF)=

UCp*/Cp (%) =q* (Btu/hr)=LMTDI( DegF)=Uo* =R*= (1/Uo*)Rf j(hr-DegF-ftA2)/Btu)

Etas =ho* [Btu/(hr4DegF-ftA2)]

ho*(eff) rBtu/(hr-DegF-ftA 2)]Uho*/ho* (%)=hi* [BtuI(hr-DegF-iftA2))

Uh~lfhi M%=Rw* f(hr-DegF-ftA 2)/BtuI URw*/Rw* (%) =Utfln (ft) =L O.OOZ1 j1341 tJhrtw (ft)530259431 Urho' = .378 UCP, 0.01997741 430868.42909

9.0 45035U83

5.2616557907 0.190054165

0.0 39766224

0.919611352 8.12596117

-7.47-312612 16 Uhl* 17.2G738932 0.000343 URvt=q (Btulhr)=LMTD ( OegF)Uo =R = (1Uo)=III [(hr-DegF-ft^2)IEtuj Etas =ho (BtuI(hr-DegF-ft-2)J ho(eff) [Btu/(hr-DegF-ftA2)J Uho/ho (%)=hi [BtuI(hr-DegF-ftA2)]

Uhf/hi (%) =Rw [(hr-DegF~ftA 2)IBtu]URwIRw (%) =Uho =Uhl =URw Proto-Power Calc: 97-200 Attachment-J Rev: A Page 35 of 40 Page 22 VY02A-AU.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate (Row 8)i Analytical I Incertaintv in Heat Transfer Surface Area Ao Do Ud L UL tfin Utfin hfin Uhfin UAo/Ao UAo 905.33147 0.05208 0.00417 8.68750 0.02085 0.00100 0.00004 0.12458 000167 0.04067 36.82236 Derivatives.

-5862.45 104.21 9497.82 16451.97 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*/R* UR*0.19005 7.47313 1.12097 1168.44929 175.26739 0.00031 0.00001 0.03977 0.00000 0.10865 0.02065 6 Analytical Uncertainty in Extrapolated Heat Transfer q. R* UR° Ao UAo LMTD* Uq./q. Uq°43086.4291 0.19005 0.02065 905.33147 36.82236 9.04504 0.11601 4998.55238 Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 36 of 40 VY02A-AU.XLS Page 23 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate Extrapolated Heat Transfer (Btu/hr)Calculated Uncertainty (Btulhr)(Uq/q)A2 Row1 153749.4783 17805.2066 0.000634 Row2 127832.8305 14810.0984 0.000439 Row3 106416.6914 12333.1813 0.000304 Row4 88680.6339 10280.5788 0.000211 Row5 73965.2057 8576.6630 0.000147 Row6 61737.0435 7160.1351 0.000103 Row7 51562.1547 5981.0379 0.000072 Row8 43086.4291 4998.5524 0.000050 707030.4672 qtot 31300.9119 SRSS 0.044271 SRSS 4.43%Uqtot/qtot

=Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 37 of 40 VY02A-AU.XLS Page 24 Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate Extrapolated Heat Transfer (Btu/hr)Calculated Uncertainty (Btulhr)(Uq/q)A2 Rawl 131195.3801 15103.9427 0.000500 Row2 113794.4455 13105.2568 0.000377 Row3 98799.9660 11381.9018 0.000284 Row4 85856.6718 9893.4811 0.000215 Row5 74666.9011 8606.0900 0.000162 Row6 64980.1137 7491.1472 0.000123 Row7 56584.3908 6524.4468 0.000093 Row8 49299.5662 5685.3828 0.000071 675177.4352 28850.9888 SRSS 0.042731 SRSS qtot Uqtotlqtot

=4.27%(75 gpm case)Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 38 of 40 VY01A-AU.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate Extrapolated Heat Transfer (Btulhr)Calculated Uncertainty (Btulhr)(Uq/q)A2 Row1 157023.2342 18206.8532 0.000656 Row2 129762.6061 15052.6614 0.000448 Row3 107370.6351 12459.6780 0.000307 Row4 88936.6170 10323.5976 0.000211 Row5 73732.6242 8560.8359 0.000145 Row6 61173.2629 7104.0420 0.000100 Row7 50784.0800 5898.5258 0.000069 Row8 42180.9535 4899.9514 0.000047 710964.0130 31661.4879 SRSS 0.044533 SRSS qtot Uqtot/qtot

=4.45%(115 gpm case)Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 39 of 40 VY02B-AU.XLS Analytical Uncertainty Calculation for Extrapolation Heat Transfer Rate Extrapolated Heat Transfer (Btulhr)Calculated Uncertainty (Btulhr)(Uq/q)A 2 Row1 179064.4002 22100.0999 0.000887 Row2 142681.0988 17616.1725 0.000564 Row3 113876.2648 14063.8438 0.000359 Row4 91005.7384 11241.8723 0.000230 Row5 72805.1411 8995.1889 0.000147 Row6 58293.7569 7203.3185 0.000094 Row7 46706.6938 5772.1632 0.000061 Row8 37443.1718 4627.7663 0.000039 741876.2658 qtot 36200.1472 SRSS 0.048795 SRSS Uqtotlqtot

=4.88%(150 gpm case)Proto-Power Calc: 97-200

Attachment:

J Rev: A Page 40 of 40 VY02C-AU.XLS Attachment K to Proto-Power Calculation 97-200 Revision A Proto-Power Calc: 97-200

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.{~~ifl Is.---'L~~~Li L5;ýJF 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 frdrd0= 2 r(r2 -ri )Where: ro = 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: 97-200

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:

f (cosa 0 The ratio of the two areas becomes: A~f = (cosaD Acf Angle ct is approximated by the expression:

-(fin separation) 1 tan a =44 r.4r.a = tan-'-I where: X = fin pitch Substituting fin height into the expression yields the following:

a = tan'1 = tan-'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 a.For the case of the VY cooler fin geometry: a = = I A) = tan-' (0.033625)

= 1.93°Hf 2(l.487)(10))

Proto-Power Calc: 97-200

Attachment:

K Rev: A Page 3 of 4 The resulting area ratio is then: A~f :4 1)I~j~~ 1.00057 A csf ==cos(1.9 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 0)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: 97-200

Attachment:

K Rev: A Page 4 of 4 Attachment L to Proto-Power Calculation 97-200 Revision A Proto-Power Calc: 97-200

Attachment:

L Rev: A Page 1 of 6 FR.um: CENTAL FILE FPAX NO.- 8i5 357 162 -.06-1'ý-98 02:27P P.01 CornEd A Unicorn Company LASALLE STATION FAX TRANSMITTAL FAX: (815) 357-1262 or (815) 357-6761 EXT. 2268 TO: LL--%4O DEPARTMENT:

PHONE NUMBER: FAX NUMBER: C&~z) A4c 4 5 -4XC FROM: DEPARTMENT:

PHONE NUMBER: FAX NUMBER: Z -7 1, 1 EY 7 _ 2 NUMBER OF PAGES FAXED § (including cover sheet)NOTES: DIRECT TELEPHONE LINE: 815-357-6761

/ TIE LINE 8-527-DESIRED EXT.p:\wprdocs~coir'adniin\faxcs.doc Proto-Power Calc: 97-200

Attachment:

L Rev: A Page 2 of 6 1-1. 1.- -"I -_vo_'- -r r-.V.COMED NUCLEAR DESIGN INFORMATION TRANSMITTAL fK SAFETY-RELATED Onginating Organization rl NON-SAFETY-RELATED Section: SEB REGULATORY RELATED Comoany: CornEd Station: LaSalle County Units: 1 Design Change Authority No N/A

Subject:

Dimensional Verification for Tubing and Fins for Cooler 1VY02A NDIT No.! LS-0835 Upgrade 0 Page I Of 2 To: Lloyd Philot. Proto-Power Ayer. Robert A. Engineer Friedrich, Rich Engineer Hal. Rich DE- Mech. Supv.A~prnow poeoto 1 6/`19196 0Mi.05119/96 Date 6u¶ gigS Oslo Status of Information

.Approved for Use [EjUnverifled UEngloseoing judgement Verification Method NIA Schedwie: Purpose of Issuance Transmittal of Dimensions to Proto-Power for Heat Exchanger Analysis Source of Information Watkdown performed on the IVY02A cooler by R. Ayer (System Engineering) and R. Fnedrich(Oesign Engineenng) on 6)19/98.Description of Information The following measurements were obtained for the IVY02A room cooler at the request of Proto-Power Corporation via fax on 1131/g8.These measurements were obtained at ambient conditions with the system shutdown.

Attached is a hard copy of the request and measurements obtained in the eiOd.Tube Outside Diameter 0.630 4/- 0.05 in.Fin Height: 1.495 D1- 0.02 in.Transverse Tube Pitch: 1 452 4/- 0.02 in.Effective Finned Tube Length: 104,25 +1- 0.25 in.The first three of these measurements were taken with a calibrated set of calioem (MMD Id. No. 8049. cal due date 9/98). The tube length measurements was taken with a metal tape measure. The listed above are engineering best estimate.

based on lhe the measuroment techniques used.Distribution:

S.E-G Willwimncn.

Cicorgc R. -CumEd. SES-BOP Millet. William J. -CornEd. SE Szumski. Daniel R. -CornEd. SES-EBOP WIN No.Proto-Power Caic: 97-200

Attachment:

L Rev: A Page 3 of 6

ý ý -I I ý I A ý Q COMED NUCLEAR DESIGN INFORMATION TRANSMITTAL SAFETY-RELATED Originatig Organization NDIT No.: LS-0835 C NON-SAFETY-RELATED Section: SEB Upgrace: 0 E] REGULATORY RELATED Company CornEd Page 2 of 2 it is not possibIl to a measurement for longitudinal tube Drtch without partial disassembly of the cooler. thus (his information is not included n this transmittal.

It was. however, verified that succetsive rows of tubes/fins are offset as shown on page two of Attachrnent 1 of this NDIT.Aaachrrents:

Proto-Power for Information and Associated Measurements

-2 pages CornEd -Nuclear Operations Disivion Proto-Power Caic: 97-200

Attachment:

L Rev: A Page 4 of 6 IROM: CE.N1TL FILE Jul- 1 3 -g 98 '1 : Gs Nr vL-, L S t-" .04 P:.o2 Co^£ lX -io.n ,I-q /;,,-e ,a ,'., -J;~~ Ae//t~Cv'r~/~ !L%(1,00"isi.d-L OPO!9'3r)4 t .r4 0 .- A SL Im f-4 -fcitio4IldC

/c-r-,l/i..

Coe*/(C,.,--ý 4,r, ýv"/ /4yd7 vf1 4 L h6 -2'tm Proto-Podwer Cac: 97-200

Attachment:

L Rev: A Page 5 of 6

-KJUM 1 ; l-0ttf L P10Lt*Junl- 13-913 1,1.:013 r $ .' t4 U. : ) ý'i, Iý?-r,:4 D°0 I4~S, I'-e~vg~zogqzz1 I I (*!f t I I, I 4j'3 p 4,ý f=1 41 11 1 c34- ~ -/1 1~4~~~Calc: 97-200

Attachment:

L Rev: A Page 6 of 6 Attachment M to Proto-Power Calculation 97-200 Revision A Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 1 of 32 Sheewart 4 Thermal Margin as a function of Tube-Side Fouling 1(2)VY01A at 75 gpm and 1(2)VY02A at 108 gpm 50.00%40.00%.E 30.00%20.00%4 1 20t 0 04 10 C)0 10.00%-0.00%------ 1(2)VYOIA 1(2)VY02A; 0.0000 0.0005 0.0010 0.0015 0.0020 0.0025 0.0030 0.0035 0.0040 Tube-Side Fouling Factor Page 1 17:25:53 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Data Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.000 06/22/98 Air Coil Heat Exchanger Input Parameters F1 tiY-Q-ianitfify, TT ...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 2_-17179.-0-0-ggfffh-150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side..1-50700 gpm-105.00 OF 115.30 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/hrIPt-.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)Fresh Water 0.002000 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Cale: 97-200

Attachment:

M Rev: A Page 3 of 32 17:25:53 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 ComEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.000 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) 75.00 Air Flow (acfrn) 19,289.00 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 Cale: 97-200

Attachment:

M Rev: A Page 4 of 32 17:25:53 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.000 06/22/98 Extrapolation calculation Summary II 1.Air-Side Mass Flow (ibm/hr) 71,279.36 Inlet Temperature (IF) 148.00 Outlet Temperature (OF) 107.40 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 (lbm/ft-hr)

Density (lbm/ft 3)Cp (BTU/lbm'°F)

K (BTU/hr.ft.

0 F)Tube-Side 37,293.47 100.00 119.41 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 0.00031430 Overall Fouling (hr- ft 2-F/BTU) 0.00200000 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)7,242.65 723,937 723,937 Extrapolation Calculation for Row l(Dry)II U.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/ftihr)

Skin Visc (lbm/ft-hr)

Density (lbrm/ft3)

Cp (BTU/Ibm.'F)

K (BTU/hr"ft-°F)

Air-Side 71,279.36 148.00 139.38 0.0203 0.0203 143.69 121.12 3,406.37 804**0.7255 0.0490 0.0625 0.2402 0.0162 Tube-Side 37,293.47 115.28 119.41 117.34 120.72 2.77 19,575 3.7364 1.3809 1.3374 61.7524 0.9988 0.3691 Tube-Side hi (BTU/hr-ft2-°F) 959.48 j Factor 0.0082 Air-Side ho (BTU/hr-ft7 2-F) 8.28 Tube Wall Resistance (hr*ft2-°F/BTU

0.0 0031430

Overall Fouling (hr- ft 2-F/BTU) 0.00200000 U Overall (BTU/hr.ftV-°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)6.51 905.33 26.07 153,767 0.9182 153,767** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 5 of 32 Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 17:28:31 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Data Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.00l 06/22/98 Air Coil Heat Exchanger Input Parameters I Fl i-Q-uantity,To-

........Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperatur Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side.......21,I-79.-00 fffi 150.00 OF 92.00 OF e 109.40 OF 84.10 OF Tube-Side.. .507U00gpm 105.00 OF 115.30 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.°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)

Fresh Water 0.001000 0.002000 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 6 of 32 17:28:31 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 ComEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpmn at f=0.001 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) 75.00 Air Flow (acfrn) 19,244.00 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: 97-200

Attachment:

M Rev: A Page 7 of 32 17:28:31 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Calculation Report for: I(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.001 06/22/98 M&Extrapolation Calculation Summary ii 1.Mass Flow (lbrn/hr)Inlet Temperature (OF)Outlet Temperature

(°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 (lbm/ft 3)Cp (BTU/lbm-°F)

K (BTU/hr-fV-'F)

Air-Side* 71,113.07 148.00 108.73 Tube-Side 37,293.47 100.00 118.75 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-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)0.00031430

0.0 2088311

7,242.65 698,599 698,599 TI 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 Air-Side 71,113.07 148.00 140.05 0.0203 0.0203 144.03 123.30 3,398.43 802**0.7255 Tube-Side 37,293.47 114.96 118.75 116.85 119.96 2.77 19,483 3.7557 Tube-Side hi (BTU/hr ft 2.0 F) 956.76 j Factor 0.0082 Air-Side ho (BTU/hrift2.°F) 8.27 Tube Wall Resistance (hr-ft 2 0.F/BTU 0.00031430 Overall Fouling (hr ft 2..F/BTU) 0.02088311 Bulk Visc (lbm/ft-hr) 0.0490 1.3874 Skin Visc (Ibm/ft hr) 1.3469 Density (lbm/ft 3) 0.0624 61.7598 Cp (BTU/Ibm-°F) 0.2402 0.9988 K (BTU/hr-ft-°F) 0.0162 0.3690** Reynolds Number Outside Range of Equation Applicability 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)5.79 905.33 26.95 141,344 0.9183 141,344 Proto-Power CaIc: 97-200

Attachment:

M Rev: A Page 8 of 32*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 17:30:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Data Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.002 06/22/98 Air Coil Heat Exchanger Input Parameters FI 1 i-drQy Tetmapr 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....21-,-797009-fiui 150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side I507 gp -m-105.00 OF 115.30 OF Fresh Water 0.002000 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 750,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

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) 104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 9 of 32 17:30:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 ComEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.002 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 (acftn)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) 75.00 Air Flow (acfm) 19,202.00 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: 97-200

Attachment:

M Rev: A Page 10 of 32 17:30:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.002 06/22/98 Extrapolation Calculation Summary II Air-Side Mass Flow (lbm/hr) 70,957.87 Inlet Temperature (IF) 148.00 Outlet Temperature (IF) 109.96 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 (ibm/ft-hr)

Density (Ibm/fl 3)Cp (BTU/lbm-'F)

K (BTU/hruftV.F)

Tube-Side 37,293.47 100.00 118.09 Tube-Side hi (BTU/hr-ft 2"°F)j Factor Air-Side ho (BTU/hr-ft 2.F)Tube Wall Resistance (hr-ft2.°F/BTU

0.0 0031430

Overall Fouling (hr- ft 2-°F/BTU) 0.03976622 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)7,242.65 675,177 675,177 ME;Extrapolation Calculation for Row l(Dry)ii Mass Flow (lbrm/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 (lbm/ft-hr)

Skin Vise (lbm/ft-hr)

Density (IbM/fl 3)Cp (BTU/Ibm.0 F)K (BTU/hr.ftl-F)

Air-Side 70,957.87 148.00 140.61 0.0203 0.0203 144.30 125.07 3,391.01 800*4 0.7255 0.0490 0.0623 0.2402 0.0162 Tube-Side 37,293.47 114.57 118.09 116.33 119.22 2.77 19,386 3.7764 1.3943 1.3564 61.7676 0.9988 0.3688 Tube-Side hi (BTU/hr-ft 2.°F) 953.95 j Factor 0.0082 Air-Side ho (BTU/hr'ft2.

F) 8.26 Tube Wall Resistance (hr-ft2. F/BTU 0.00031430 Overall Fouling (hr- ft2.°F/BTU)

0.0 3976622

U Overall (BTU/hrft 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)5.22 905.33 27.78 131,195 0.9184 131,195** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 11 of 32*** Air Mass Velocity (Lbm/hr'ft), Tube Fluid Velocity (ft/sec):

Air Density at Inlet T, Other Properties at Average T 17:33:10 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Data Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.003 06/22/98 Air Coil Heat Exchanger Input Parameters

-1T .o.tal .Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side......2-I.1797 0 1iif 150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side-50700 gpm 105.00 OF 115.30 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.°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)

Fresh Water 0.003000 0.002000 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 12 of 32 17:33:10 PROTO-IIX 3.01 by Proto-Power Corporation (SN#PttX-0000) 6/22/98 ComEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils_l Fouling Sensitivity:

75 gpm at f=0.003 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 (OF)Air Dry Bulb Temp Out (OF)Relative Humidity In (%)Relative Humidity Out (%)Wet Bulb Temp In (°F)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) 75.00 Air Flow (acfmi) 19,160.00 Tube Inlet Temp (OF) 100.00 Air Inlet Temp (OF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (°F) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 13 of 32 17:33:10 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1 (2)VYO LA & 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.003 06/22/98.1 Extrapolation Calculation Summary 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 (lbmI/Wf)Cp (BTU/lbm-°F)

K (BTU/hr-fi'°F)

Air-Side 70,802.66 148.00 111.21 Tube-Side 37,293.47 100.00 117.53 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.°F/BTU 0.00031430 Overall Fouling (hr'ft 2.°F/BTU) 0.05864934 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)7,242.65 651,570 651,570 Extrapolation Calculation for Row l(Dry)11 Mass Flow (lbm/hr)Inlet Temperature (OF)Outlet Temperature (IF)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.°F)

K (BTU/hr-ft.°F)

Air-Side 70,802.66 148.00 141.09 0.0203 0.0203 144.55 126.60 3,383.59 798**0.7254 0.0490 0.0623 0.2402 0.0162 Tube-Side 37,293.47 114.25 117.53 115.89 118.59 2.77 19,303 3.7942 1.4003 1.3646 61.7743 0.9988 0.3686 Tube-Side hi (BTU/hr-ft 2.°F) 951.56 j Factor 0.0082 Air-Side ho (BTU/hr1ft2-°F) 8.25 Tube Wall Resistance (hr-ft2.°F/BTU

0.0 0031430

Overall Fouling (hr-ft 2-°F/BTU) 0.05864934 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)4.74 905.33 28.49 122,373 0.9185 122,373** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 14 of 32*** Air Mass Velocity (Lbm/hrft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 17:35:11 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Data Report for: I(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.004 06/22/98 Air Coil Heat Exchanger Input Parameters FIletiDQrfianttyB , Totma Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 2-1 f79M-- afiff-150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side 150. 0- gpm 105.00 OF 115.30 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-.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)

Fresh Water 0.004000 0.002000 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 15 of 32 17:35:11 PROTO-IIX 3.01 by Proto-Power Corporation (SN#IPHX-0000) 6/22/98 CornEd -- LaSalle Calculation Report for: 1(2)VY01 A & 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.004 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 (TF)Tube Temp Out (°F)Condensate Temperature

(°F)Extrapolation Data Tube Flow (gpm) 75.00 Air Flow (acfmn) 19,123.00 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: 97-200

Attachment:

M Rev: A Page 16 of 32 17:35:11 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

75 gpm at f=0.004 06/22/98 Extrapolation Calculation Summary It II *Air-Side Mass Flow (lbm/hr) 70,665.94 Inlet Temperature (0 F) 148.00 Outlet Temperature (0 F) 112.31 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/fl hr)Density (Ibm/ft 3)Cp (BTU/Ibm'°F)

K (BTU/hrftf'°F)

Tube-Side 37,293.47 100.00 116.92 Tube-Side hi (BTU/hr'ft 2"°F)j Factor Air-Side ho (BTU/hr'ft2-°F)

Tube Wall Resistance (hr-ft 2"°F/BTU 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.07753245 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)7,242.65 630,961 630,961.ff Extrapolation Calculation for Row l(Dry)II I.Air-Side Tube-Side Mass Flow (Ibm/hr) 70,665.94 37,293.47 Inlet Temperature (0 F) 148.00 113.83 Outlet Temperature (0 F) 141.49 116.92 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (0 F) 144.74 115.38 Skin Temperature (0 F) 127.86 117.92 Velocity *** 3,377.06 2.77 Reynold's Number 796** 19,208 Prandtl Number 0.7254 3.8149 Bulk Visc (lbm/ft-hr) 0.0490 1.4073 Skin Visc (lbm/ft'hr) 1.3733 Density (Ibm/fl 3) 0.0623 61.7819 Cp (BTU/lbm'°F) 0.2402 0.9988 K (BTU/hr'fP'F) 0.0162 0.3684** Reynolds Number Outside Range of Equation Applicability Tube-Side hi (BTU/hr ft 2 -F) 948.87 j Factor 0.0082 Air-Side ho (BTU/hr-ft2.'F) 8.24 Tube Wall Resistance (hr-ft2. F/BTU 0.00031430 Overall Fouling (hr'ftl 2.F/BTU) 0.07753245 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)4.35 905.33 29.23 115,100 0.9186 115,100 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 17 of 32*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 16:48:25 PROTO-IIX 3.01 by Proto-Power Corporation (SN#ItX-0000)

CornEd -- LaSalle Data Report for: I(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.000 06/22/98 Air Coil Heat Exchanger Input Parameters F I 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 150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side.50_00J gpm 105.00 OF 115.30 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 (BTUihri-.f°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)

Fresh Water 0.002000 750,000 14.315 1.00 0.000 Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 18 of 32 16:48:25 PROTO-HX 3.01 by Proto-Power Corporation (SN#PH4X-0000) 6/22/98 ComEd -- LaSalle Calculation Report for: 1(2)VY01A

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.000 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 ('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) 108.00 Air Flow (acfm) 19,347.00 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: 97-200

Attachment:

M Rev: A Page 19 of 32 16:48:25 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: I(2)VY0I A & 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.000 06/22/98 a I Extrapolation Calculation Summary 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 (ibm/ftlhr)

Skin Vise (lbm/ft.hr)

Density (lbm/ft 3)Cp (BTU/Ibm.°F)

K (BTU/hr-ft.°F)

Air-Side 71,493.69 148.00 105.73 Tube-Side 53,702.59 100.00 114.11 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 0.00031430 Overall Fouling (hr ft 2.°F/BTU) 0.00200000 U Overall (BTU/hr. ft 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)7,242.65 756,011 756,011 Extrapolation Calculation for Row 1(Dry)II I. 'I Mass Flow (Ibm/hr)Inlet Temperature (fF)Outlet Temperature

(°F)Inlet Specific Humidity Outlet Specific Humidity Average Temp (fF)Skin Temperature

(°F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ftlhr)

Skin Visc (lbm/ft-hr)

Density (Ibm/fl 3)Cp (BTU/lbm-°F)

K (BTU/hr.ft--F)

Air-Side 71,493.69 148.00 137.73 0.0203 0.0203 142.87 115.96 3,416.62 807*-0.7256 0.0489 0.0626 0.2402 0.0162 Tube-Side 53,702.59 110.69 114.11 112.40 115.49 3.98 26,863 3.9391 1.4490 1.4058 61.8257 0.9988 0.3674 Tube-Side hi (BTU/hr-ft 2 F) 1,251.72 j Factor 0.0082 Air-Side ho (BTU/hr-fti 2.F) 8.29 Tube Wall Resistance (hr ftfZ.F/BTU

0.0 0031430

Overall Fouling (hr-ft 2.F/BTU) 0.00200000 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)6.72 905.33 30.16 183,607 0.9181 183,607** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 20 of 32 Air Mass Velocity (Lbl/hrft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 16:51:50 PROTO-ItX 3.01 by Proto-Power Corporation (SN#PIIX-0000)

ComEd -- LaSalle Data Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.001 06/22/98 I1 Air Coil Heat Exchanger Input Parameters Air-Side Tube-Side Fliiid-QuantiidiTty.

2T,[79_0-0-ffii

.... ..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 109.40 OF 115.30 OF Outlet Wet Bulb Temp 84.10 OF Outlet Relative Humidity %Tube Fluid Name Fresh Water Tube Fouling Factor 0.001000 Air-Side Fouling 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 750,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

LOG(Re)]Coil Finned Length (in)Fin Pitch (Fins/Inch)

Fin Conductivity (BTU/hrift-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 fri.F)104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 21 of 32 16:51:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 CornEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.001 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 (°F)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) 108.00 Air Flow (acfm) 19,301.00 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 2 Proto-Power Cale: 97-200

Attachment:

M Rev: A Page 22 of 32 16:51:50 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

ComEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.001 06/22/98 ffi Extrapolation Calculation Summary 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/tf3)Cp (BTU/Ibm'°F)

K (BTU/hr-ft-°F)

Air-Side 71,323.71 148.00 107.03 Tube-Side 53,702.59 100.00 113.64 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 2'0 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)0.00031430

0.0 2088311

7,242.65 731,028 731,028 Extrapolation Calculation for Row l(Dry)1 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 (Ibm/ftV)Cp (BTU/Ibm'°F)

K (BTU/hrift-°F)

Air-Side 71,323.71 148.00 138.63 0.0203 0.0203 143.32 118.84 3,408.49 805**0.7255 0.0489 0.0626 0.2402 0.0162 Tube-Side 53,702.59 110.52 113.64 112.08 114.90 3.98 26,780 3.9527 1.4535 1.4139 61.8302 0.9988 0.3673 Tube-Side hi (BTU/hr-fV 0-F) 1,249.18 j Factor 0.0082 Air-Side ho (BTU/hr-ft 2.°F) 8.28 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft 2-°F/BTU) 0.02088311 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)5.96 905.33 30.98 167,164 0.9182 167,164** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 23 of 32*** Air Mass Velocity (Lbn/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 17:08:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Data Report for: 1(2)VYOlA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.002 06/22/98 Air Coil Heat Exchanger Input Parameters Fl n-ik -Qi tii-. , -t-a. .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-2-71[l79T.-OO c-f .....150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side.500-0gpm 105.00 OF 115.30 OF Fresh Water 0.002000 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 750,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

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)104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 24 of 32 17:08:55 PROTO-IHX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 ComEd -- LaSalle Calculation Report for: 1(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.002 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) 108.00 Air Flow (acfrn) 19,258.50 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 CaIc: 97-200

Attachment:

M Rev: A Page 25 of 32 17:08:55 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: l(2)VYO1A

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.002 06/22/98 m Extrapolation Calculation Summary 11 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 (lbm/ft3)Cp (BTU/Ibm-°F)

K (BTU/hr.ft'F)

Air-Side 71,166.65 148.00 108.29 Tube-Side 53,702.59 100.00 113.17 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 0.00031430 Overall Fouling (hr-ft2- F/BTU) 0.03976622 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)7,242.65 707,030 707,030 Extrapolation Calculation for Row l(Dry)II 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/ft-hr)

Skin Visc (lbm/ft-hr)

Density (lbm/ft3)Cp (BTU/Ibm-°F)

K (BTU/hr ft-°F)Air-Side 71,166.65 148.00 139.36 0.0203 0.0203 143.68 121.18 3,400.99 803**0.7255 0.0490 0.0625 0.2402 0.0162 Tube-Side 53,702.59 110.31 113.17 111.74 114.33 3.98 26,688 3.9675 1.4585 1.4217 61.8352 0.9988 0.3672 Tube-Side hi (BTU/hr-ft 2-°F) 1,246.55 j Factor 0.0082 Air-Side ho (BTU/hr.ft 2'-F) 8.27 Tube Wall Resistance (hr-ft2.°F/BTU

0.0 0031430

Overall Fouling (hr f 2 0 1.F/BTU) 0.03976622 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)5.35 905.33 31.73 153,749 0.9183 153,749** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 26 of 32*** Air Mass Velocity (Lbm/hr ft2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T 17:15:47 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Data Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.003 06/22/98 Air Coil Heat Exchanger Input Parameters FIhnld-t n fDy , Temp Inlet Dry Bulb Temp Inlet Wet Bulb Temp Inlet Relative Humidity Outlet Dry Bulb Temperature Outlet Wet Bulb Temp Outlet Relative Humidity Air-Side 21 7 970tf-aii Th 150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side..1500o gpm 105.00 OF 115.30 OF Fresh Water 0.003000 0.002000 Tube Fluid Name Tube Fouling Factor Air-Side Fouling Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 750,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

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)104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 27 of 32 17:15:47 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 CornEd -- LaSalle Calculation Report for: 1(2)VY0I A & 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.003 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 (°F)Tube Temp Out (OF)Condensate Temperature (OF)Extrapolation Data Tube Flow (gpm) 108.00 Air Flow (acfrn) 19,216.50 Tube Inlet Temp (OF) 100.00 Air Inlet Temp (OF) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (°F) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 28 of 32 17:15:47 PROTO-HX 3.01 by Proto-Power Corporation (SN#PIIX-0000)

ComEd -- LaSalle Calculation Report for: 1(2)VYO0 A & 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.003 06/22/98 Extrapolation Calculation Summary II II- *1 Mass Flow (lbm/hr)Inlet Temperature (IF)Outlet Temperature (OF)Inlet Specific Humidity Outlet Specific Humidity Average Temp (°F)Skin Temperature

(°F)Velocity ***Reynold's Number Prandtl Number Bulk Visc (Ibm/ft-hr)

Skin Vise (lbm/ft'hr)

Density (lbmr/ft)Cp (BTU/Ibm 0'F)K (BTU/hr-ft-°F)

Air-Side 71,011.45 148.00 109.53 Tube-Side 53,702.59 100.00 112.75 Tube-Side hi (BTU/hr-ftl 2"F)j Factor Air-Side ho (BTU/hr'ft 2 -F)Tube Wall Resistance (hr-ft2.°F/BTU

0.0 0031430

Overall Fouling (lhrft 2'°F/BTU) 0.05864934 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)7,242.65 683,298 683,298 Extrapolation Calculation for Row l(Dry)I.Air-Side Mass Flow (Ibm/hr) 71,011.45 Inlet Temperature

(°F) 148.00 Outlet Temperature (IF) 139.98 Inlet Specific Humidity 0.0203 Outlet Specific Humidity 0.0203 Average Temp (IF) 143.99 Skin Temperature

(°F) 123.15 Velocity *** 3,393.57 Reynold's Number 801*'Prandtl Number 0.7255 Bulk Visc (lbm/ft-hr) 0.0490 Skin Vise (lbm/ft-hr)

Density (lbm/ft 3) 0.0624 Cp (BTU/lbm-°F) 0.2402 K (BTU/hr-ftf.F) 0.0162 Tube-Side 53,702.59 110.10 112.75 111.42 113.82 3.98 26,605 3.9812 1.4630 1.4288 61.8397 0.9988 0.3671 Tube-Side hi (BTU/hr ft 2-.F) 1,244.16 j Factor 0.0082 Air-Side ho (BTU/hr'fit 2-F) 8.26 Tube Wall Resistance (hr-ftl.°F/BTU

0.0 0031430

Overall Fouling (hr-ft2.°F/BTU)

0.0 5864934

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)4.86 905.33 32.39 142,406 0.9184 142,406** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 29 of 32*** Air Mass Velocity (Lbm/hr-ft'), Tube Fluid Velocity (ftlsec);

Air Density at Inlet T, Other Properties at Average T 17:18:53 PROTO-HtX 3.01 by Proto-Power Corporation (SN#PItX-0000)

ComEd -- LaSalle Data Report for: l(2)VY0IA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpmn at f"0.004 06/22/98 Air Coil Heat Exchanger Input Parameters F liiid-Q-a.itii

,-i-To tal..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-2-r- -I79.-0W-ffffii-150.00 OF 92.00 OF 109.40 OF 84.10 OF Tube-Side............

00 gpm 105.00 OF 115.30 OF Fresh Water 0.004000 0.002000 Design Heat Transfer (BTU/hr)Atmospheric Pressure Sensible Heat Ratio Performance Factor (% Reduction) 750,000 14.315 1.00 0.000 Heat Exchanger Type Fin Type Fin Configuration Counter Flow Circular Fins LaSalle VY Coolers 01A/02A j = EXP[-2.5088

+ -0.3436

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) 104.250 10.000 128.000 0.0120 0.0120 1.495 2 8 20.00 20.00 0.5270 0.6250 1.500 1.452 1.000 225.00 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 30 of 32 17:18:53 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000) 6/22/98 ComEd -- LaSalle Calculation Report for: l(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.004 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 (°F)Tube Temp Out (IF)Condensate Temperature (IF)Extrapolation Data Tube Flow (gpm) 108.00 Air Flow (acfm) 19,177.00 Tube Inlet Temp (IF) 100.00 Air Inlet Temp (°F) 148.0 Inlet Relative Humidity (%) 12.76 Inlet Wet Bulb Temp (IF) 0.00 Atmospheric Pressure 14.315 Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 31 of 32 17:18:53 PROTO-HX 3.01 by Proto-Power Corporation (SN#PHX-0000)

CornEd -- LaSalle Calculation Report for: 1(2)VYOIA

& 02A -CSCS Equipment Area Cooling Coils Fouling Sensitivity:

108 gpm at f=0.004 06/22/98 P -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

(°F)Velocity ***Reynold's Number Prandtl Number Bulk Vise (lbmr/fthr)

Skin Visc (Ibm/ft hr)Density (lbm/ft3)Cp (BTU/Ibm-0 F)K (BTU/hr-ft'°F)

Air-Side 70,865.48 148.00 110.71 Tube-Side 53,702.59 100.00 112.33 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-ftt 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)0.00031430

0.0 7753245

7,242.65 660,999 660,999 Extrapolation Calculation for Row 1(Dry)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 (lbm/ft)Cp (BTU/Ibm-°F)

K (BTU/hr-ft--F)

Air-Side 70,865.48 148.00 140.51 0.0203 0.0203 144.25 124.81 3,386.59 799**0.7255 0.0490 0.0624 0.2402 0.0162 Tube-Side 53,702.59 109.85 112.33 111.09 113.33 3.98 26,517 3.9957 1.4679 1.4357 61.8445 0.9988 0.3669 Tube-Side hi (BTU/hr.ft 2-°F) 1,241.70 j Factor 0.0082 Air-Side ho (BTU/hr ft2.°F) 8.25 Tube Wall Resistance (hr-ft 2.°F/BTU 0.00031430 Overall Fouling (hr-ft2.°F/BTU)

0.0 7753245

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)4.44 905.33.33.01 132,834 0.9185 132,834** Reynolds Number Outside Range of Equation Applicability Proto-Power Calc: 97-200

Attachment:

M Rev: A Page 32 of 32*** Air Mass Velocity (Lbm/hr-ft 2), Tube Fluid Velocity (ft/sec);

Air Density at Inlet T, Other Properties at Average T Attachment N to Proto-Power Calculation 97-200 Revision A Proto-Power Calc: 97-200

Attachment:

N Rev: A Page 1 of 2 Proto-HX Model Database Saved on attached disk as: Name: vy-O I 02a.phx Size: 1,146,880 bytes Date: 6/24/98 Time: 2:25:30 pm Proto-Power Calc: 97-200

Attachment:

N Rev: A Page 2 of 2 PROTO-POWER CORPORATION CALCULATION TITLE SHEET CLIENT: PROJECT: Commonwealth Edison / LaSalle County Station COMED / LaSalle Station GL 89-13 Program CALCULATION TITLE: CALCULATION NO.: FILE NO.: Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers97-195 31-003 COMPUTER CODE & VERSION (if applicable):

PROTO-HX ver 3.02 REV TOTAL NO. OF ORIGINATOR/DATE VERIFIER/DATE APPROVAUDATE PAGES A 7-3 S. t____~~D __ _ __ _ _ _ _ __ _ _ __ _ _ S.I~g all Is pot__ _ __ _ __ _ _Page i of v Form No.: P1050101 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION -n Njo.97-195 Pm, A PAGE ii OF V GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 VRIFIED BY S. Ingalls JOB NO 31-003 CLIENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers 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 L No.97-195 PAV A AE i OF V GROTON, CONNECTICUT D. Phyfe OATE 6/29/98 EIFIE S. Ingalls JOB NO.31-003 CLIENT COMED / LaSalle County Station .ROJFCT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers CALCULATION VERIFICATION FORM REVIEW METHOD: EXTENT OF VERIFICATION:

Approach Checked: N/A E] Complete Calculation:

--Logic Checked: N/A LII Arithmetic Checked: N/A E] Revised areas only: LI Alternate Method El N/A j'(Attach Brief Summary)Computer Program Used fj N/A f 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 CONCLUSIONS TO BE CORRECT AND REASONABLE:

IDV Signature:

Printed Name: M.-i Initials:

W Date: ý/2/119 Form No.: P1050103 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWERCORPORATION c -- 97-195 REv A PAGE iv oF v GROTON, CONNECTICUT ORIGIATOR D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls JOB No.31-003 COMED / LaSalle County Station pRojEct COMED / LaSalle Station GL 89-13 Program TITME Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers TABLE OF CONTENTS CALC TITLE SHEET ...............................................................................................

I REVISIO N H ISTORY ....................................................................................................

II CALC VERIFICATION SHEET ..................................................................................

III TABLE OF CONTENTS .........................................................................................

IV LIST OF ATTACHMENTS

.......................................................................................

V Total number of pages in Preface of Calc 5 1. PUR PO SE .........................................................................................................................

I 2. BACKGROUND

......................................................................................................

1 3. DESIGN INPUTS .....................................................................................................

1 3.1 .LASALLE STATION REFERENCE CONDITIONS

.............................................................

2 3.2.CONSTRUCTION D ETAILS ..........................................................................................

2 3.3 .PERFORM ANCE D ETAILS ..........................................................................................

3 4. APPRO ACH .....................................................................................................................

4 4.1 .PROTO-HXTm PARAMETER CALCULATION

..........................................

4 4.2.PROTO-HXTM FLOW RATE INPUTS .........................................................................

4 4.3.PROTO-HXTm EXTRAPOLATION METHOD ..............................................................

5 5. ASSUM PTIONS ...............................................................................................................

5 6. AN ALYSIS ........................................................................................................................

5 6.1.PRO TO -HX Tm M ODEL ............................................................................................

5 6.2.HEAT EXCHANGER FOULING FACTOR LIMIT ............................................................

6 6.3.FOULING SENSITIVITY

.................................................

7 6.4.THERMAL M ARGIN ASSESSMENT

..........................

.........................................

8 6.5.MINIMUM SERVICE WATER FLOW RATE ..................................................................

9 7. C O NC LUSIO N ...............................................................................................................

11 7.1 .PRO TO -H XTh M ODEL .......................

.......................................................

11 7.2.HEAT EXCHANGER FOULING FACTOR LIMIT ..........................................................

11 7.3.FOULING SENSITIVITY

................................................

11 7.4.THERMAL MARGIN ASSESSMENT.

......................................

1 7.5.MINIMUM SERVICE WATER FLOW RAT ..................................

I 8. REFEREN C ES ...............................................................................................................

12 Total number of pages in Body of Calc 12 Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION --97-195 FE A WCE v OF v GROTON, CONNECTICUT OoGIN,,ToR D. Phyfe DATE 6/29/98 S. Ingalls "0- 3o 31- 00 3 COMED / LaSalle County Station COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED I LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers LIST OF ATTACHMENTS Attachment Subject Matter Total Pages A Proto-Power Calc.97-195, Rev. A; 3 Vendor Supplied Hx. Information B Proto-Power Calc.97-195, Rev. A; 3 Sargent & Lundy Specification J-2544 C Proto-Power Calc.97-195, Rev. A; 7 Form N-I Manufacturer's Data Report for Nuclear Vessels D Proto-Power Calc.97-195, Rev. A;LaSalle Station UFSAR Sections: 9.2.1.1.1, 9.5.5.1.1, FSAR Q40.92 5 y9mm E Proto-Power Calc.97-195, Rev. A;PROTO-HXrm Calculation Reports and Model Data Sheets 13 F Proto-Power Calc.97-195, Rev. A; 6 PROTO-HXThm Calculation Reports for Fouling Sensitivity G Proto-Power Calc.97-195, Rev. A; 17 PROTO-HXTm Calculation Reports for Minimum Service Water Flow H Proto-Power Calc.97-195, Rev. A; 2 PROTO-HX T M Version 3.02 Model (and disk)73 Complete Calc (total number of pages)Form No.: P1050104 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWERCORPORATION -NO 97-195 REv A PAGE 1 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 ,ERIPIED BY S. Ingalls JOB NO.31-003 cLINT COMED / LaSalle County Station PR""C- COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers 1. PURPOSE The purpose of this calculation is to develop a thermal performance analysis model for the Commonwealth Edison (CornEd) LaSalle Station, Standby Diesel Generator heat exchanger.

This model is to be used for the analysis of heat exchanger thermal performance test data as part of the LaSalle Station heat exchanger testing program.Once developed, the model is used to evaluate the thermal margin of the heat exchanger at the LaSalle Station Reference Conditions as currently defined in the LaSalle design and licensing basis.The thermal performance model documented in this calculation has been created and used with PROTO-HX, Version 3.02. The model can be used with previous versions of PROTO-HX and produce identical results as long as the following restrictions are upheld:* Versions prior to version 3.02 will not calculate a negative fouling factor when calculating the fouling factor based on test data.* Shell and tube heat exchangers analyzed in Version 3.0 or earlier must have a tube-side Reynolds Number greater than 10,000 (i.e., fully developed turbulent flow).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:* Water (fresh and salt): 32-500'F 2. BACKGROUND LaSalle Station is in the process of implementing a heat exchanger thermal performance monitoring program in response to the requirements of NRC Generic Letter 89-13 (Reference 8.2). Development of an analytical model in PROTO-HXTM, Version 3.02, will allow timely analysis of data resulting from the test program.3. DESIGN INPUTS The PROTO-HXTM program 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, 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-HXTM Version 3.02 was verified and approved for use as documented in Reference 8.10.The design inputs for this calculation consist of the heat exchanger design basis requirement (Section 3.1), construction details (Section 3.2), and performance specifications (Section 3.3)provided by the Hx manufacturer data sheets or design documents as referenced.

Construction Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION -o.97-195 REV A PAGE 2 OF 12 GROTON, CONNECTICUT ORI'G,,,,R D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls "0B "0- 31-003 CLET COMED / LaSalle County Station PRojECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers details give the necessary information for model construction while performance specifications provided by the manufacturer are used to benchmark the model.Thermal performance of the Standby diesel generator heat exchanger is assessed in this calculation at the LaSalle Station Reference Conditions of Section 3.1 with all tubes active at 100% and 110% of rated load. No tube plugging margin is considered.

3.1. LASALLE STATION REFERENCE CONDITIONS Table 3-1 describes the performance requirement of the jacket water cooler. These conditions ensure that the engine operating temperature range will not be exceeded.Table 3-1 LaSalle Station Reference Conditions 3.2.Parameter Value Reference Heat Load at 100% power/I 10% power (BTU/hr) 7,800,000

/ 8,600,000 8.1, 8.4 Shell-Side Flow Rate (gpm) 1,100 8.4 Shell-Side Inlet Temperature (0 F) 190 8.4 Tube-Side Flow Rate (gpm) 800 8.1, 8.4 Tube-Side Inlet Temperature (0 F) 100 8.1 CONSTRUCTION DETAILS Table 3-2 Construction Details Parameter Value Reference Heat Exchanger Type AEW 8.11 Total Effective Area per unit (ft 2) 479 8.11 Number of Shells per unit I 8.11 Shell Velocity (ft/sec) 5 8.11 Tube Passes per shell 2 8.11 U-Tubes (yes or no) No 8.11 Total Number of Tubes 188 8.11 Tube Length (ft) 13 8.11 Tube Inside Diameter (in) 0.652 (18 BWG) 8.11 Tube Outside Diameter (in) 0.750 8.11 Stationary Tubesheet Thickness (in) 0.938 8.3 Floating Tubesheet Thickness (in) 1.875 8.3 Tube Wall Conductivity (BTU/hr-ft-°F) 1 12 (Arsenical Cooper) 8.9, (8.11)Tube Pitch (in) 0.750 8.11 Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION GROTON, CONNECTICUT REV A CA-LC 0.97-195 I REV A PAGE 3 OF 12 OR.IGIATOR D. Phyfe DATE 6/29/98 VERIFIED BY s Ingalls JOB NO.31-003 cLIEIT COMED / LaSalle County Station -COMED / LaSalle Station GL 89-13 Program T :ITL Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Table 3-2 Construction Details Parameter Value Reference Pitch Type Triangle 8.11 The vendor data sheet shows the effective area as 479 ft 2 , however, based on tube diameter and tube length, this value is a gross area (A,,) approximation:

A gr = (number of tubes). (L, 1 te). (tube outside circ.)Agr = 188.13ft .50in. 479.878ft2 12 iy// )The effective area (Aefr) can be approximated as follows: Alf = (numberof tubes). (L,u 1 -Tfed -Tfioatig). (tube outside circ.)A f- = 188.(13ft-(0.938 in + 1.875 in)).,, ,(0.750in 471.225112 A~ =88.j~ft12*

~ J~i .t =47.221n/the outside Equation 1 Equation 2 where: A9T -Heat Exchanger Gross Area,ft 2 A eff -Heat Exchanger Effective Area, ft 2 L tube -Tube Length, ft TCIxed -Fixed End Tubesheet Thickness, ft (0.938" per Reference 8.3)Tnoating -Floating End Tubesheet Thickness, ft (1.875" per Reference 8.3)The data sheet value for the effective area will be used in the model benchmarking process. However, for PROTO-HXTM runs of the Standby heat exchanger model the above calculated effective area will be used.3.3. PERFORMANCE DETAILS Table 3-3 Performance Details Parameter Value Reference Shell Side Fluid Type Jacket Water (Fresh) 8.11 Total Fouling Factor (Design) 0.00285 8.11 Shell Side Fluid Flow Rate (lb/hr) 550,000 8.11 Shell Side Inlet Temperature

('F) 190 8.11 Shell Side Outlet Temperature

('F) 174.4 8.11 Tube Side Fluid Type Service Water (Fresh) 8.1/8.7 Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I.5-1 PROTO-POWER CORPORATION cALc ,o.97-195 REV A PAGE 4 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls JOB NO.31-003 CLET COMED / LaSalle County Station COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Table 3-3 Performance Details Parameter Value Reference Tube Side Fluid Flow Rate (lb/hr) 388,000 8.11 Tube Side Inlet Temperature

('F) 100 8.11 Tube Side Outlet Temperature (0 F) 122.2 8.11 Hx. Design Q -Service (BTU/hr) 8,600,000 8.11 Hx. Design U -Service (BTU/hr-ft 2-°F) 255.2 8.1 I 4. APPROACH This calculation utilizes plant/vendor fabrication specifications provided in Attachment (A) to develop a thermal performance prediction model for the LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers. The calculation then benchmarks the model by comparing the heat transfer rate calculated by PROTO-HXTM Version 3.02 with the manufacturer's specifications for thermal performance.

4.1. PROTO-HXTM PARAMETER CALCULATION Minimum Shell Area The minimum shell area is calculated using either the shell side velocity or a shell geometry.

The preferred method of calculation is using the shell side velocity.

Reference 8.11 gives the shell side velocity to be 5 ft/sec at a flow rate of 1100 gpm. Based on this velocity and flow rate the minimum shell side area is calculated by PROTO-HXTM to be 0.490 ft2.Outside H Factor (Hoff)The Outside H Factor is a multiplier, with value less then 1.0, used to reduce the ideal shell side film heat transfer coefficient.

The Outside H Factor accounts for inefficiency in the heat exchanger.

Using the back calculation method, based on the design overall heat transfer coefficient, the Outside H Factor was calculated by PROTO-HXTM to be 0.780.4.2. PROTO-HXTM FLOW RATE INPUTS Volumetric flow rates are converted to mass flow rates based on a set temperature of 60OF in PROTO-HX T M.Therefore, the actual PROTO-HX T M inputs have to be adjusted to give the correct mass flow rate. The PROTO-HXTM input is adjusted using the ratio of the actual water density and the density of water at 60'F.Q phix = Qtenp Ptemp Equation 3 P60-F Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 1 PROTO-POWER CORPORATION 97.-19.i5

.. ,.Ev A PALE 5 OF 12 GROTON, CONNECTICUT .GrR D. Phy"f.e. 6/2 9/98 VERIFIED" BY JB nga .s NO .31-003 CLMIEN COME I aaleCunySato COMED /Lasalle Station GL 89-13 Proga TI""E Thermal Model of COMED./ LaSalle Station Unit 0, and 2 Diesel .Generator Jacket Water Coolers Table 4-1 PROTO-H-XTM Flow Rate Inputs _________Parameter Density (Ib/e)ý'.

Actual Flow (gpm) PROTO-HXTM Input (gpm):.Tube-side, 100'F 61.994::%:

(8.12) -.800 795.25'ShelIside,.

l90F 60.349 (8.12) 1,100 1 064495 PROTO -.60 .F 62.364 4.3. PROTO-1XTN EXTRAPOLATION METHOD.All: calculations perform.ed for this calculation are based. on. a constant cold inlet temperature.

This allows the comparison of the heat transfer,.

outlet temperatures.

log mean temperature difference (LMTD), and overallheat transfer.coefficient.

There. is no:.c" ompia.son of the overall heat transfer coefficient in the design ease since PROTO-HX "" used the data sheet.value of the overall het transfer coeficien to.tcalculate the shell side film, heat transfer.

coefficient.

.5..... ASSUMPTIONS 5.1. The vendor data sheet (Reference 8..1) is considered.

an accurate reflection of the vendor's expectation for the heat exchangers outside. film heat:. transfer coefficient.-Therefore, the benchmAkihg::of the.PROTO-HX Tmdel -to the:vendor data sheet will ensure that the PROTO-HXXTM calculated outside film. heat..transfer coefficient is consistent with the vendor's expectation.

The.pROTO..HXTm model.is benchmarked with the vendor data sheet effective area. However, calculations pdformed with the model use the effective area determied in Section 312. Futurevalidation of this assumptioniisnnot require~d.

6.. ANALYSIS 6.1. PROTO-HXT.

MODEL Tadble 6.4 shows the PROTO-HXrm benchmarking of the Jacket Water Cooler for the.. .Standby Diesel:Generator.

The:PROTO-HX T M reports :can be found in Attachment E.Table &.I Model:1Benchmark

Parameter.

PROTO-HXTM Data Sheet Percent Difference Effective Area,: ftW.:: 479 47.9 0.00 %Shell Side Outlet Temp,:OF 174.4 1.74.4" 0.00 %Tube Side Outlet.Templ.

F 122.2 122.2 0.00 %Heat. Transferred, BTU/hr..:.:!

8,589,000

' 8,600,000

-0.13 %.Corrected LMTD 70.3 70.2 0.14%corm No;: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&l 5-1 PROTO-POWER CORPORATION

-NO- 97-1.95 REJ A PAGE OF 12 GROTON, CONNECTICUT ORIG I 3NATOR D. Phyfe DAT 6/29/98 VERIFIED BY S. Ingalls JOB NO.31-003" COMED / LaSalle County Station PR-.JEC- COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Table 6-2 shows the PROTO-HXTM results for the heat exchanger design conditions using the corrected effective area, Section 3.2. The PROTO-HXTMl reports can be found in Attachment E.Table 6-2 Model Design Correlation Parameter PROTO-ltXTMI Data Sheet Percent Difference Effective Area, ft 2 471.2 479 -1.63 %Shell Side Outlet Temp, 'F 174.6 174.4 0.11 %Tube Side Outlet Temp, 'F 121.9 122.2 -0.25%Heat Transferred, BTU/hr 8,481,000 8,600,000

-1.38%Corrected LMTD 70.5 70.2 0.43 %All PROTO-HX T M calculations performed with the Standby Jacket Water Cooler model will use the effective area of 471.23 ft 2.This change is made to the PROTO-HXTM heat exchanger data sheet as shown in Attachment E.6.2. HEAT EXCHANGER FOULING FACTOR LIMIT In order for the jacket water cooler to meet the Reference Conditions (Table 3-1) the fouling must be limited from the values listed on the vendor's data sheet (Reference 8.11). The overall fouling factor limit was determined by iterating on the overall fouling factor, a PROTO-HXTM input, until the required heat load was matched.Table 6-3 shows the results of the PROTO-HXTM runs for the limited fouling factor case, see Attachment E.Table 6-3 Fouling Factor Limit Parameter Design Fouling Limited Fouling Overall Fouling Factor 0.00285 0.002782 Overall Heat Transfer Coefficient 255.2 259.7 Heat Transfer Rate 8,484,000 8,600,000 Required Heat Transfer Rate 8,600,000 8,600,000 Thermal Margin -116,000 0.0% Thermal Margin --1.35 % 0.00%The limitations on the fouling factor are placed on the tube-side fouling factor, since the tube-side is the most controllable via periodic tube-side cleaning.

To be consistent with the HPCS Diesel the shell-side fouling factor will be set to 0.0005 hr ft 2 °F/Btu for this analysis.

The tube-side fouling factor is calculated from the overall fouling found from the PROTO-HXTV iteration process.Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION CAIL NO.97-195 RE' A PAGE 7o 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls JOB No.31-003 cLIN COMED / LaSalle County Station POJECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers The area ratio is used to convert the overall fouling factor to a tube-side and shell-side fouling factor f.o,--"= fshetl + (Area Ratio). ftube Equation 4 Area Ratio = TubeOD Equation 5 Tube ID 0.750 in_AreaRatio

= -- -1.150 0.652 in From the vendor datasheet the design overall fouling factor is fTotal = 0.0 0 2 8 5 0 hr 1 F/B3tu From the PROTO -HX iteration the adjusted overall fouling factor is found: fadj.,ed = 0.0 0 2 7 8 2 hrft 2F Btu From the new overall fouling factor the new tube -side fouling factor is calculated:

8 -.0005)hr ft 2 /_(fa djusted _(0.002782 oF!Booos)t f = -_____)_ =_ /Btu = 0.0 0 1 9 8 4 hrrft 0 tube Area Ratio 1.150 The PROTO-HXTM heat exchanger data sheet is changed to reflect the adjusted design fouling as calculated above. Like the effective area change in the heat exchanger data sheet, this change is made without recalculating the Hoff factor.Attachment E includes a final model calculation report for the Reference Conditions and the adjusted tube-side fouling entered into the PROTO-HXTM data sheet.6.3. FOULING SENSITIVITY The fouling sensitivity of the jacket water cooler is shown in Figure 6-1. The fouling sensitivity was developed at 800 gpm CSCS flow, 100°F CSCS inlet temperature, 1100 gpm jacket water flow, and 190'F jacket water inlet temperature.

The tube-side fouling factor was varied from 0.0000 to 0.001984 (hr ft 2 °F/Btu) by increments of 0.0005 (hr ft 2°F/Btu). As in Section 6.2, the shell-side fouling factor is held constant at 0.0005 (hr ft 2°F/Btu). The PROTO-HX T M Calculation Reports for the fouling sensitivity can be found in Attachment F.Form No.: P1050105 Rev.: 10 Date: 10/21/97.Ref.: &5-PROTO-POWERCORPORATION A.97-195 REVA PAGE 8 OF 12 GROTON, CONNECTICUT ORIG11ATR D. Phyfe DATE 6/29/98 VERIIED EY S. Ingalls JOB "0.31-003" COMED / LaSalle County Station PRCY' COMED / LaSalle Station GL 89-13 Program TITLE Tliermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Figure 6-1 18,000.000

--.-.." _16.000,000 -aktLtrCot Standby DG -Ja ket Water Cooier 14,000.000

...... .. .12,000.000 10,000.000-.

____ __ ___ ____110%oDC Power 8,000,000 I I 4,000,000 j _ L _2.000,000 0.000000 0.000198 0.000397 0.000595 0.000794 0.000992 0.001190 0.001389 0.001587 0.001786 0.001984 6.4. THERMAL MARGIN ASSESSMENT The clean thermal margin is assessed by a comparison of the reference condition performance requirements to the heat exchanger performance capability with a zero (0)fouling factor. Using a zero (0) fouling factor shows the maximum available performance of the heat exchanger.

Likewise, the service thermal margin is assessed by comparing the reference condition performance requirements to the heat exchanger performance capability with the design fouling factor.The margin is calculated directly and as a percentage compared to the required heat rate to perform the component's safety function.

The PROTO-HXTM reports can be found in Attachment E.margin=Heat Rate -Heat Raterequired

%margin = 100. margin Heat Rate required Equation 6 Equation 7 Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&l 5-1 PROTO-POWERCORPORATION --97-195 REv A PAGE 9 OF 12 GROTON, CONNECTICUT ORIGINTOR D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls JOB "0.31-003 COMED / LaSalle County Station ""' COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Table 6-4 Thermal Margin Parameter Service (Design Fouling) Clean (0 Fouling)Overall Heat Transfer Coefficient 259.7 955.9 Heat Transfer Rate 8,600,000 18,850,000 Required Heat Transfer Rate 8,600,000 8,600,000 Thermal Margin 0.0 10,250,000

% Thermal Margin 0.00% 119.19%6.5. MINIMUM SERVICE WATER FLOW RATE The minimum service water flow rate for the adjusted design fouling condition is calculated with the shell-side inlet temperature at 190'F and a flow rate of 1,100 gpm.Iterating using the service water flow rate and inlet temperature, the minimum acceptable flow rate is found for each inlet temperature (Attachment G). The heat load for each iteration must be equal to or slightly above the required heat load of 7,800,000 BTU/hr and 8,600,000 BTU/hr, the diesel heat load at 100% and 110% power, respectively (Reference 8.1). Figure 6-2 shows the results of this iteration process.The results of the model iterations are summarized in Table 6-5 and Table 6-6 along with Figure 6-2. Density corrections of the PROTO-HXTm flow rates are made in accordance with Equation 3. Values for fluid density are obtained from Reference 8.12.Table 6-5 Minimum CSCS Flow Rate at 100% Power CSCS Inlet Density at Inlet PROTO-HXrM Density Corrected Temperature Temperature Input Flow Rate Flow Rate (OF) (Ibm/fi9) (gpm) (gpm)35 62.41903 161.1 161.0 40 62.42184 169.8 169.6 50 62.40595 190.5 190.3 60 62.36445 217.5 217.5 70 62.30034 254.2 254.5 80 62.21603 307.0 307.7 90 62.11349 389.3 390.9 100 61.99437 534.5 537.7 Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION

--'97-195 REVA PAGE 10 O 12 GROTON, CONNECTICUT D. Phyfe DATE 6/29/98 VERIFIED BY S. Ingalls JOB No.31-003 CLIENT COMED / LaSalle County Station PROJECT COMED / LaSalle Station GL 89-13 ProgramThermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers Table 6-6 Minimum CSCS Flow Rate at 110% Power CSCS Inlet Density at Inlet PROTO-HXTm Density Corrected Temperature Temperature Input Flow Rate Flow Rate (OF) (Ibm/ft 3) (gpm) (gpm)35 62.41903 193.5 193.3 40 62.42184 204.8 204.6 50 62.40595 232.2 232.1 60 62.36445 269.1 269.1 70 62.30034 321.0 321.3 80 62.21603 399.3 400.3 90 62.11349 530.9 533.1 100 61.99437 795.3 800.0 Figure 6-2 Minimum Service Water Flow 900.00 800.00 700.00 600.00 4 500.00 0 400.00 L)110 DislPoe________~100 Diesel____

Power F..0UU.0U -200.00 100.00 0.00 30 40 50 60 70 80 90 100 CSCS Inlet Temperature

(*F)Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION C-LC NO.97-195 REv A PAGE 11 OF 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DATE 6/29/98 V"IEDbY S. Ingalls JO"'O.31-003 c COMED / LaSalle County Station PPO"'cr COMED / LaSalle Station GL 89-13 Program TIMhE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers 7. CONCLUSION 7.1. PROTO-HX T NI MODEL The Standby Jacket Water Cooler model was developed using PROTO-HXTM, Version 3.02. The model was benchmarked to the vendor data sheet. The benchmark model correlation to the vendor data sheet is -0.13 %. The benchmark model is for reference only based on the non-conservative approximation of heat exchanger effective area as discussed in Section 3.2 and Assumption 5.1. Calculations performed with the Standby Jacket Water Cooler model are to use the effective area developed in Section 3.2.This model should be considered suitable for use in the analysis of thermal performance test data.The model database is saved under file name dg0Ia.phx, with a file size of 640 KB, and a file date and time of 6/29/98 at 1:50:34 PM. The saved database is set up to run the Reference Conditions with design fouling factor selected, the design fouling factor is a shell-side fouling of 0.002782.

The database file is included as Attachment H.7.2. HEAT EXCHANGER FOULING FACTOR LIMIT For the Standby Diesel Generator Jacket Water Cooler to provide adequate heat removal at the specified LaSalle Station Reference Conditions the overall fouling factor must be equal to or less than 0.002782 hr ft 2 °F/Btu. This overall fouling factor is entered in the model as the shell-side design fouling factor.7.3. FOULING SENSITIVITY Given a constant shell-side fouling at the model design value, the sensitivity of the jacket water cooler to tube-side fouling effects is shown on Figure 6-1.7.4. THERMAL MARGIN ASSESSMENT Assuming the adjusted heat exchanger effective area and maximum overall fouling factor, the clean and service available thermal margins are 119.19 % and 0.00 % respectively.

7.5. MINIMUM SERVICE WATER FLOW RATE As shown in Figure 6-2 the service water flow can be throttled down to account for lower service water inlet temperature conditions.

The heat exchanger can remove the design heat load for the diesel at 100% (7,800,000 BTU/hr) and 110% (8,600,000 BTU/hr) rated power, by reducing service water flow rates as the service water temperature decreases.

Form No.: P105010 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 PROTO-POWER CORPORATION -c, ';0.97-195 REvA PACE 12 o" 12 GROTON, CONNECTICUT ORIGINATOR D. Phyfe DArE 6/29/98 VERIFIED BY S. Ingalls JOB NO.31-003 CLINT COMED / LaSalle County Station PROECT COMED / LaSalle Station GL 89-13 Program TITLE Thermal Model of COMED / LaSalle Station Unit 0, 1, and 2 Diesel Generator Jacket Water Coolers 8. REFERENCES 8.1. LaSalle Station UFSAR, Sections:

9.2.1.1.1, 9.5.5.1.1 (Attachment D)8.2. NRC Generic Letter 89-13 8.3. The National Board of Boiler and Pressure Vessel Inspectors, Form N-1 Manufacturers' Data Report for nuclear Vessels (Attaclunent C)8.4. LaSalle Station FSAR Q40.92 (Attachment D)8.5. Stewart & Stevens Vendor Manual, VM J-152 through VM J-157 8.6. LaSalle Station Drawing, D-22079 8.7. Sargent and Lundy Specification J-2544 (Selected Pages, Attachment B)8.8. Not used 8.9. Standard of the Tubular Exchanger Manufacturers Association 8.10. Heat Exchanger Thermal Performance Modeling Software Program PROTO-HXTM Version 3.02 Software Validation and Verification Report (SVVR) SQA No. SVVR-93948-02, Revision F, dated 2/17/98 8.11. American Standard Heat Exchanger Data Sheet for the LaSalle Station Standby Diesel Generator Jacket Water Coolers. (Attachment A)8.12. Proto-Power Calculation 93-048, "Fluid Properties

-Fresh Water -Range 32°F to 500'F", Rev. A Form No.: P1050105 Rev.: 10 Date: 10/21/97 Ref.: P&I 5-1 Attachment A to Proto-Power Calculation 97-197 Revision A Proto-Power Calc: 97-195

Attachment:

A Rev: A Page 1 of 3 I I- .I j I , .I/ , IJlJ4 -5 iY STEWART & STEVENSON SERVICES, INC.RECIPROCATING ENGINE SALES 8631 EAST FREEWAY HOUSTON. TEXAS 77029 WE AR TRANSMITrING lZ PAGE(S) INCLUDING COVER. IF INCOMPLETE, PLEASE cAl., 713(671-6218 OR 7131671-6152 PLEASE DELIVER TO: DATE: 9 , 1'NAME: 0 Ln Ca $I 'h 11 FROM: r7Oi ,u%.FIRM:_ At_-_ 0 PHONE: 713/671-6 (3 -FAX: -FAX: 713/671-6127 REF: If zL- J/e-&U{~Z~-&u-~Yk Proto-Power Calc: 97-195

Attachment:

A Rev: A Page 2 of 3 JUN 04 '98 19:o0 r fm I" L~STIDARD HEAT TIANSf A-DIVlSIQK

&JPALO, X. 14240, ~ 'mY-~,Y~.,

T~GER SPEC CA77ON~ SHEET Kirdli L Z"%140=jW 2 2 P. ~~OAR.0 F-68633-773339 Stexvart & Stevenson for Commnorwealth Edison REFERENCE NO. H-74-.11A a...CUSTCOMER I a 13 it Ir -20 2?22 24 26 27 20 2, 30 31 32 Ano AOESS aals ontStto nt IaiZ_ INQUIRY HID, Jun 27.17 PLANT LOCATION OATC SEIVCE or UNIT jak- Wr~ ITK4m NO. 01 A)&ISE1IS6 CPK TV PE TENa AE.Xl* f~f,1 CONNECTED 114 SO. FT. SUaF./U~aiT 47 SHELLS/UNIT One SO. F1T. SURP./SHELL~

479 PF-RFORMANCE OF ONE UNIT SHELL. SIDI[ TIU1519SIM

FLUID CIACUL.ATCD Jacka t ~Jter Re& Water TTLFUDErLN2550,000

/Hr 388. 00o #IH r* VAPOR LIQUID 550,000. #/Hr 288.000 #/Hr SYAMC5FOEAM IE spCCIFIC MEAT iBr/5lr TU/LaB-rl T)4CRAL CODUCTIITY GU/NIP-FT-IV OPRTN PRESUII CC PRESSURE DOP .PSI PSI FOULING INISISTANC4 (MIN .028 o.1 ItEAT EZC14A NG6O-BTU/HQ 3.6 x0_ MT 702~rO~j TPAANSPRR RATE-SEPRVLCE 2552 CLEAN CONSTRUCTION OF ONE SHELL D15SION PRESSUR( 150 PSI 750ps TEST PRCSSAIUE 225 PSI L225 S TIJIBEs ARS Copper -A)loy 142 No.8 3/.411%11 7i 1 LENaTH j "1 PrrC*4 3 4" Ti SHC..Sel1.0.

a.m. 1611 SH EL.L COVUR Noney!G (ACKOV)CHANNEL-XX3M=W tlUntz CHAN'NEL COVeR Stee TU SESP4ET -STATIONARY Munt M-w5~T~~AI untZ BArFLES-CROSS Steell TYPE FLOATIIJG HEAD COVER i3AF.FLCS-LONQ Tr9imOINCEMIENT PROTECTION No Tu98 SUPOORTS Steel TUBE TO TWOES'4EET JOINT Rolled 6ASKIarS Corip. Asbesto.5 Packing -Neogrene CONNECTIONS-SHE6L 313E 114 )off OUT 1011 5~IO104 ANS I CH4ANNEL.

SIDE IN 81OUT si RATING 150# ANSI COROSION ALLOWANIE-SMELL 510K 1/16" an~ C. Suzy).JOEMiO 1/1611 on C_ Ste-rL-CODE MELIIREMENTS AIME--Code III -3 Starmnqd T)L LS Jlci WE' GHTSEACjW SHELL 12 60 BUNDLE 1860 FUL-L OF WATEAk 4410 NOTE: INDICATE AFTER EACH D3A~t W$E.TJOIL-j STRESS RELIEVEOA.M.

I ANO WHETMER flADlOGRAPHCD J)C-R)REMARKS- cWTErrovable Ilube 15undle Ari-ericin Standard P/N 5-046-15-56

nl Frot-Power Mei: 9 7- 195 AirrjanStand ad Serlal No. 8-20-005---

Attachmenit A 35 36 38 59 40 41 A'2 42 47 44 40 so S2 52 I.I..'a*I.1 U- JU N a4 '98 19:3'.. Rev: A Page -3 of 3 qi 13 .0E t3 Attachment B to Proto-Power Calculation 97-195 Revision A Proto-Power Calc: 97-195

Attachment:

B Rev: A Page 1 of 3 SARGENT & LUNDY ENGINEERS CHICAGO PEFeKtENCE 9.7 J-2544 CA, 11-09-76 include a shell and tube heat exchanger which will be supplied with cooling water from the Purchaser's cooling water system.b. The closed cooling water system pump shall be of the centrifugal type and shall be driven by the. engine.C.The shell and the tube heat exchanger shall be of the capacity required for 110 percent of rated power with a fouling factor of 0.0005 on shell side and .002 on the tube side. The heat exchanger shall be in accordance with the requirements of ITEN A, TE4A (Tube Exchanger Manufacturers' Association)

Class C and the ASHE Code Section III.The type bundle shall be removable without removing shell from its mounting.

The tubes shall be 5/8 inch minimum and be of ad-miralty metal..d. The circulating water system shall be provided with controls which will sense and maintain optimum jacket water temperature.

e. Cooling water supply for the heat exchangers will inlet temperature of 1000F and a minimum of 320F.be designed for a 150 psig water working pressure hydraulic pressure of 225 psig.be at a maximum The coolers shall and tested at a F. Starting System a. Each engine shall be equipped with an independent pneumatic start-ing system complete with all valves, integral piping, controls, etc.b. The reliability of the starting system is paramount and no compromise of the starting capability shall be made with other basic require-ments of the equipment design. Any special devices or auxiliaries required to insure successful starting shall be provided, except any equipment of an experimental type will be unacceptable.

Contractor shall describe in his proposal what occurances are possible to pre-clude successful starting, and what remedies would be necessary that are not already provided for in the equipment design.c. The compressed air starting system shall consist of two redundant sets of equipment, each completely independent of the other for successful operation.

A cross-connecting line with a normally closed valve shall, be provided between sets. The accumulator fur-nished with each set of equipment shall have the capacity for a minimum of three normal cranking cycles in rapid succession without the use of its air compressor.

Each accumulator shall be furnished with a shut-off cock, pressure gauge drain valve, safety valve, and sensing element for low pressure alarm. Proto-PowerCaic:

97-195

Attachment:

B 2-9. Rev: A Page 2 of 3 Proposal Technical Data for Diesel Engine-Generator Sets, Cont.La Salle County Station -Units 1 and 2'RelFe ENCE J-2544 CA., 11-09--76 of Biddetr: Stewart & Stevenson Services, Inc.Nam(ENGINE-GENERATOR DATA, Cont.I (Insert all data in these columns)BASE BID ALTERNATE 1.DIESEL GEN. DIESEL GEN.DIESEL GEN.O IA AND 2A OIA AND 2A (Contractor to furnish complete infor-mation for starting system furnished)

E. Engine Cooling System: a. Cooling system capacity.(gal)

b. Pipe size for cooling water connections

.............. (in)c. Heat exchanger dimensions:

(1) Length ............... (in)(2) Diam ................. (in)(3) Height ............... (in)_____ d. Quantity of cooling water at rated load, required at 80*F ................ (gal/min)-at 95 0 F............. (gal/min)at 1000F ............ (gal/min).m e. Tube material ................

f. Diameter and thickness of tubes .................... (in)g. Total tube cooling surface...

........................ (ft 2)h. Water box material ...........

545 8 179.5 16" 19.5" 550 750 840 Arsenical Copper (SBl 3/4" x 18 BWC 479 Carbon Steel Weights: 3050 lbs Dry 4350 lbs Wet 0 11)PTD-I5 Proto-Power Calc: 97-195

Attachment:

B Rev: A Page 3 of 3 Attachment C to Proto-Power Calculation 97-195 Revision A Proto-Power Caic: 97-195

Attachment:

C Rev: A Page 1 of 7 Ref.: P&I 5-1 Form No.: P1050104 Rev.: 10 Date: 10/21/97 5- 04(0$-157-/54G-00 FOl1B1 N-I MAINUWACTUVE1S' DATA IlIPORT FORl NtCLE'AAh

"'TSj.JS1 As requaired ksy the I'rovk~isiui of ihe AS'I Ci(r idculev 1. byJ= CX_,AD 0-D.UAT. -RANS Ul& DIVLS IONFA OJW.~XJ4l..*J iodd,.ga ofPhe- q9-g 3. Typei4.ORXX.a. ,zjnd.9tC1L4;tU.Vc

'Let N4.e1 , ZDQL5-P1=zL_.., Nagel id. N a,_ Yr. Built...LL.1%

(11*ri#. or Vvtt.) (UASHEa.lL) (i4jrs. beftlt #$..) (Sloes h Staigt No.)3a. Applicable ASMr rode: Section III, EdniionL/_1A._d'Z Addenda dae~k7 ./ -7121 a~ o.....lem. 4-8 mncI. to be completed lot single wall travel$. jadlrts of jacketed vessels, a- shell& of head czchiaresers.

4. 9ieI V Sgtril 44 ST- cotesion oG 9~o 14..o 4.Sel Mtral CG ~.AIlowencet.-in.

il..f.. n. Lang~h_...

ft. _____ire.(Kintd a SpC.ite.N.) (mi.t. at rt5O. op*.thfidl LSea .: i Ls 5... II.T.' 40. .. T.....JO.NE

....Efficiency Oc %Girth -i.T.' R. fT. _________ .ofCourmee I 6. Heed. (a) Material T.S. (b) Matecial __________T.

S._______________

Lo~tacroeor Kr..hl,eF 111i~tti-ae cewresi 1t.eslophetricai Flat Side.t Press.ffope. beottom eadg4 Thickness Viedlet. Rodts. Usti&l Apes Agler Radius D'iagserfei (Contact Caegovio)If remnovable*ai.

Won d.... Na. gTS Off.N. icer foolening 7. laciret Closufe_______________________________(Deescribi.

or#ea.hv d, best,~ oe. 31-4or-give

~. skul Drop Weight P It-Ilogi 9. Dsig' PessareS~p&

~Clierpy lmptec:......

it-lb Hydrostatic af Te at a.Dei n r asae R eiofa ttemnp. of .. f- C)* t "116inon Pressure e...~ pi forms 9 ond 10 to be completed roe tube sections..

9i. Tubc Sheets: Stistionary.

bfatevisi~pg wj4TL:17.aWZSQZ i.v Ttne.. L%38:: Lin:At iscehmeo pSbet: oVradet.)

40. 4uP.5 Axse. COPPER 10. Tubes. Mattenlal

%5 O.O.:42in.

Thcmea. JZ.ge _Nuimeberjaa

.~Type smeal&iff (Kind & Upse. tefi.) t~rih soV Inemes 11 so 14 incl. to be completed tot imnner chambers of jacketed vessels, or channels of he&@ exclianges..

N A N M El 01 Corrosin 4%0041M II.-S~wlt Mteral O(PT.. .~O iibl h~cne a.'.in. Allaqwenc'!._

in. Died-. -it---.. in. Lcusth. ...t-in.....12. -Sea=&a? Long ~ L .It.. 40 1 T... E~J 11fi ci en c 7 y CVI'ielic.

Died., S~ndoLi) (Y-4 .s Not Girth____

I .No. of Cots frq. 4l..13. flicidst (a) MitonS U drs ISSp00 (6) Ateeri~ii_____

I,.. (c) material _______ .s. _____Crown Knuciete ritipti, as Conical flticieei'hoicsie Flat Side to Pesos.Locmatio Th~sielaee Ra~dium Radium Nat in ^I-&a Anibe Rtadium Dia..e..le (Core.etm of Coeaeias.(h) Channel -(c) Flol~oeisg--.-

If temavable, balsa used (s)t 0O...'~6b c.... ____OhtIaeis (Mal etot5. Spec..ame..

S.S~ m~)(Describe or *.wsaa sheich)rop Wright ___ esrmtic Charpy Imp.acg ft-lh Hydrzostatic gt T* eto£4. Dsian p ..mire4.5.#L Psi 69 U 0-1 Go damp. Pi rt L144e~ $"MO$s of ostewmel Frosaa~es.

Wilk valffuiideag l~.thSMl~IAj

.....-...

-.D -. A fl1_ _

1*a if .Z. 1 1)1 tteant below Robe 1 1111`1904 fo laytll areol il wulitet applicataIr.

1~. .t~~ VI~cOlttitNftaabvg.......

eas. ~________t6~Afteche:

S~UJN ~ T 1 _5~fIP~F4JSJOG

& 3W2 --%~'hi 41 Opesiaaat Hoodhols., No.-- Size-.yhcea.jt.,l Sire._ _____Locatit on Locatjion Ia. Siaqqiouuu Shift-.1bJ0. -Lta. ssea --r? -- ..Oth ar .1. MLES Attached .U D)!Lb =~ SUVA IV** do Not c(s'.m.) (H4ooit- to-aerib*) (Wh~ra Ill ffogv 1N'fi.f d..r'.plii, ct aleritc. fear which .eee01 %age doui'thad)

(:rFJ11IFU II:Af(IJ (IF DEIGAitN Delagia d.owto.. file a o e~ 10 tttis ai t S ia iats top-(t reelecteld h ---- .. Prof. Knc. state. _ Roe. Nfo.We carciii iha mh is at ude in ctui¶ atM uw correct find iliac this nucea toal.cwfm 1 that rule@ of construc.Rion of sthe A. E l:,~c i i. AC iCAN STANDARD HUY F//(Usnuiactum)X..

D ceatifictae of aiiih.al caltion Expijve, _.AUgjUSt_4't_._127$

_Cart~ilscie of Authotiiatjoa o.-1 6 CI:I11IFI(:AiE OF SHOP INS'EMION VESSEL AI NAOMwnjRlCAN STANDARD RUAT TtLAMSFLR DIVIS ION Nowff~ .e York 1. 41ea W040el61441.

%*1idli. a valid aumecentaed by 41.0 Natiwil Meand of $last-* got.@ 111*40Wj.

V*al**f Inspectors Eid/oC lho Seat*hw lodaalete the poosscuw voesse deteleta~d in Ohi. UaA^u1fctsui..e nota Revertan oio. 2 ..end Wofte thaft to the boot of ety litiolslaidir and belief. the iawwtvhop constno'tct-d

%ki proat sewe ua lot eaccardate with Rho ASUR Call. leetlaft pit.u, faggeitu this earlifteul.

a^*fiber the Iu..gpelow her hie a.-player E.h.d a~n wevtarty.

caup..avedt~

or lueptled.

oaeeneeting the peswesu,~.e~vot daterrtboo in Otiole iattuisttwevgs IOut. lPeve. f unthermatt, "t.labor th* In'poieoi nor his em.ployee siotetbig flame lu*Wji "aftea top wy pearweeillle Ouf.~ P#"A p'pfld.ah.

of a- of say Lc ind furon~ te w. roanegted ths .npca...'P~s.....A44-'-A4 11 ~ -~,-$ýA-- Commilssions

..1 4 27 ':-Z ./ egs .r ~ ~~(icic IllI-'W la IT OF- ii Fi.11 ASSI.%!ILY lNSPElCI'tON 1, II, ad.,rIiald.

hoiddit.g -l*aid -,4aian. i.,- §--f.. tt the N.linl lon -4 Val'hiI end Prv@emie Vessel Inapeatets tittder the Steah of Pjse.lr.*

4f hy ...ad-r~~ i ... --o ___________

______harve cao,.~,ai.'u We s tet-..a in til ttd4 .e. l* w~ith, ii.The de..I,bvd p*eie.*Gol and stale that partc refeftal.

to .9 dot. ee. -.-.- .-- i.ec 1rrt...td Ut. the r.Atilleats of elhop lftspeuli"tnh..*

Seen bi*i relt? i.- In lti. 1. Sirt n,.t .4l -1i., 4-i~ at1,1.f ihi nn.ei he. .n.om,uiod and asiair-tid thisl pressure wc..got In a, roetei.tc lab1 the ASi4 ..l. S1, a:, ra 1A. The. .l..isi..

.**a fte -a* 90,f.d andi eubjeCuad

'lo a hydrobatitl twat o.*et*Vftveeeilc Trot .P- .-_ .- .- -j'i.Bly oaigning.:h ah -rititcete neither ibv Malvtei r it r has ettptaa .r n,.&ee Env weartnlv. .a.empota or imla~itd, cEnerattrig the ptCC Blue Ie~. deniLbed t- lhi-i Men.,(e1tUi.,i 11I. F~i..r -.nt-g., noti~heft, IN nsectior not his emnployer shall be Itltivb In ene, matioenae tor any pe'lonol lnpva. ps.. Waec I.~ a e f *nv hInSd oheinig born of c .nnenlv4 with thise intepralwiuo.-

Prtnlaliir

d. l~A. (7/7 1) TMia f--i.1 (? 01f as muhsalntble traf. the, ANMB. 14S K. 4 7th III., Now Ywat, Nf.Y. 14411 Proto-Power Cabc: 97-195

Attachment:

C R RPagse 3 of 7 FORMt N-1 MANUFACIAIRERS' DATA IILIETIIT 111u1NI!CIIArI VE~SSELS Anm required by the Provisionri a theC AS-tE Cuic flulen 11IU2.:4WYETýTAS9 JZ... JJOXn.&AMO ya sxf.S flI.. fl.2 rU.. wt. (5M-6*Wa9E. (Mile.. SarleS No.)~ (Stale 46 stao N6.), 3.Applicablm ASUE Cod.. Seciaan III, I.iL.fY.-,A'd~nda datek1 L4/Z Ca be No.[coma 4-0 Endt. to be eoiv 4 ieue (Of tingle wall 'bestelo, jackets of jackoietl veosrI4, or *hella of licat exchaneuu.

Nomianl -315 Corrosion

/O(A9 14000 I~l3 4. $bell& U~ttedaIGAIO!6 T.S. "AC10O..Thickr net+/-.Lin.

Allowane:_cin.

Via- fr... -in. Lettish-...ft.

-go.............w (10011 Veto. MO.) (Kill. Of10 0 en. POC411411 4;'1Se1.m., Loog"ML1 -lf.T." N 0l R.T.....bW..J...........

Eficiency.-

Lf.....Ginh__= H.IT.5 R.T._______

No'.of Cotuace 6. Hirids (a) Materia -T.S. (b I.a~ _________TAS

______________

Looetcc...

Knuckle Elliptical Cacfti~ iHmisph.eleei Fis Stide to Press.(To.p boqttom *ad*) Thickness 119diga Radio* Ratio Apes And34 Radiusa OVsoilo~ (Coo-on W Congo")II ie~v~b~~ beie 1 1a8aLOI. Spote. NO.. T.S. .. Sm, Member) (06Dcalib.

at etleah sktebeh 7. Jacket Closer ~ ~ i i. ~ ~ ~~ h d~aee,4.r~i hlh Drop Weight n~t~i Cheipy lmnpct..........flib, Iydroolotic at Test a. Design Pveesitte&jS pd-in ep. of ..~___~Cvu~eo rau~.2a~a*' lieani 9 0111d to to be. coatileteo 4 for tube sections.P. Tube Slicersi Staion~aery.

Muu iialfNNIJ 1 C..tlsjL -a.1 In. Th.c 033 :~in.' AImACQhmmnu (Kin IRN 1peQ. I. (I~jett to pt.84.) (edd csd ARS. COPPME 10. Tesbetr macedit. 66% O.D4ýa~. T~tckness..

vL..oittlest Nqamble, 1j5 T.Tp.....$

irQJ&&Mailad spec. its.) (UILlhl rU Items II to 14 (act,. to be coespleterd for inner cheanluirs of jeckelej vessels. of channelm al hedet Wtudaseafes.

11. -9yhv hatra51BTS Moulisf.WiIGIA Allowance!..

is. fc n Lengith..s....(iWnd& spo.eK. N M.e aepcljd 12.de Sett.. Long.a %E60 Efficenc)Gld._______

IIT'.....x

j. ~ .of core* 13. Heed,,I (a) k~ttSIA s r. s.3 I'aeis 7.h. L!) meetde _ _ a.5I cc*". Kumnehiw 11Ii0gm1C..

Conical -fi4..1 1 h*.lcqI Vial side t.o scf s.4 86,..Lesi. hickowas Radium. Reals. R.t t Apes As%4ia KadiUS Pio"Woor. (C*^..% 04 coa. s) 0* (a) Out .lwm% r-endi2Q -__ --. ---- -1L EkflI3 (b) Channel ALLPU(M.,SAVO5'

~'It lornvah'ebelo W u.se.d C QI t.4; 000-59: 16 1 he (a lk 4 I gIUI 'A j tkaIXi61ilos,Se.e Nom.. as.1118.Rb.d II Cc~~ ueaue!5. pi ~ Choupy ianrart-_

Jt.lb Ifil~o~sstic 94 } wa W:0~1 4 D s g n P e oie= P i l 4 40 -t .o fT r c i s ei mI S 1 1 ~d i if r lotora g ec mmensed pema iheP4ete.ew

h. ~~ml,~as oeo o vaetr4wtcdiwo

.-. , IT / t.VINd1 (kL)tW% b tao 5 Ile foe a1 tg aehshame merikee.tL 1' výil OsSutsi Wfueybe ... ._____...____

_ _ _ ', " No --~o Sie --Lctin -t p6 juato 11-"h'hlr, No -'. .Siretea Loction, 114tr,,Act, .i e.. .L c io ... ..'._ -_;wunsetw.

ft -W s -1. *.=7' L- Is Matles thge CatR=id5 Ac Acanne(K" Mbe (Numbiler) (Deotcrltbe) (ilta e. & Hew)CEIIIFICATION OF I)ESIGN Egess ign llstkresWpa e -0 wbrts, 0-1 2~VrI t 1 C'Design aaloteaticlna entitledbA.J...tS4JZ Prf Fretfg. SlateL....

Rrg. Ns.CZ.SZLZ.

Stress ,-epS ., ,. rc -rtiller .t .,.tate Pole. No. -We ccgtih cbs' ale a tbito ritr 'rearerrecit atoe that this rtcjear v~aw sorath~oae ivies of canlofcac; of the AS&F. -~ e. .S ,e. A M RIR CAN STA NM ARD H EA T / / * */i 2--t- a_7ASFEFLDIVXSbON

^I00 Cervi~est teue hBu ilutFion V'opires ,ur 14...., 1973 --Certificate of Asehowidzed No.1 cFriTIFICATh; OF SMO1' INSPECHON v~tZMADC 0 A&RICAPL STAKDARD BEAT TCAKSTFl DIVISIO a I Iev York i. 1160 wwds*614dl a wl1d4 esnfntsi ci slasuid by it t I ons t(Rof Wai eand Postsias e Vesseljepsieroa 5ns/lr tthe liSte-. rea~k.t.~tk___

e.1eaiio~4 t,,tJ~~ilU!2 4 JtMAl 9OlU£L Qp. "Cbtcago. .t1111noal hemp I" ep&Ad ols. arissaw veasel d.esrlbed in Ihule Manuafartutut' Dole Repaal et -ie.2 .one7 sleot Mhat 14 the bast o may bnowliedg.

ni4 belie. the iMenufaetwer has tcwssirtuctad 1oeat "s$ase I lots in r eeeedaose t waicthe AIMS cage. leasetle it.uIp eLgartfsg this -n firs at. 01"ther he Ihmaint w .ini has employer m a smih eneor .sepressed at soid4% clwaduag ftih proseeue ceded10* 0-escrihed In this M.tauldaeigwrse Dais Report. rtte oraih heinspeacisefsee is ermployeeshaltu b le te in'eav~jaueantee ote any Igiewsae lalir or Jdialge or a ltes of emy kind ariling from or -ocente td t U.,. ._ , ,,?a....t..

,., .7n'.___I. *po. o ili Retorts, Ctw', t sro ' No.:lirlrJ:l;A'T-;

or I 'INI) ASCE'II.A INF!5"E1ION

1. ihe amdevt-irnd, holdin e vaiit 1 r m9iban Ilaaie. by tlie Hadat of boater end Priessre Ve Ina I suspect*?*

i.oid/tn 11%g Pets re Pi Awi ns¢* .Aland .nld .jtLy .o hat r..'a~ .4 1% -*reir"r-nls

.~ 'I., M Menwd. I 1raa ice 4e.n

j i'. m hhe d'.raIa%-Ao r-sa .a 0at1S.and a1sl1 th-t parts00, l rtrned Peel d1 I taw .r...... 0 ............

..... ... ... ., ie" fcl..4ed In the r.rilflrt r ot shop In peraito" hatea t.*.u" nlet. .rlI " hhe -3 en .0, b- a".,et ,f -r..t Itmlit 4Th. rn..mi ara..ni l rvi tda4 s m ii thl preseuse vwa**.I it i ra trhe SI,. ASIlt C .lr, ;I. IT, ibeti ices -.. i-..u'.rled e..4 subjected

to a lses p"ra t.T-1ta. ' .(et, ...----i,...m#y srli.ialIias 4h..n .%t- ,,.tshtn fli* lth .-a'-r n-- hit enfi-v'r n..I..............arI-

rr..afr or -mpie- -oroe-w.rruing tha suse ,.slei dlel rrtbd I!i sii D &nlds a 11.4. le k':-'l 1/4'l.'rr-tur., neislia the l ap-eovas noe his emlFoyer shall ho libl in manerl tl. anv p.rsail Iru).1 , Ot cat oety p'Q# .iaia Ci C * <1 Iny Uai. -Itimat4 from ea iu.otad ikth tbiainepar-tacp.

', .-..'!, )sle- .- -------. i- 0.. ' ' "...... ...... .... ...... ..............

.*c m m l. c..Yeunicdjn .lS.A. f7/tl) Thia f1.rm (1:j0) 1 estainabis lovab the AP&W, 1C97-195.

4 lj", H Y LY. tool?Pr~oto-11owe'r Clio 97-195

Attachment:

C Rolv. A Dan- C -PS '7 F010~1 N-11 AIANUI'ACTUHIElS' I)A'rA ltwt'owL FOR) NUCL1EAf VEL5SELS An realuirre4l ly ike Prii'%arton car iihe AMsII Gpl ltilew 2.~Ns' lid.~i No..XA.I&. Appliclldec ASMIE Code: Staton Ill, EdiF14pnL.5VS.__..

Addc44a CateN.- -Iltrw 4-9 incl. to be compl.eted fas singte WallI vessels. jaiclets ofi jacketed vessels. or &bell* of heat cichansets.

PAL N.Orninau SI Coryosion oa_! 14i-00 4. Shall% Mat~t,.iJQU0GLj-B T.S. ",,sJCnL..Thac~kneseL*..

in. Aloincr n Die.-.. I,--.. in. Lenitth.-.... (I. -IA.IVV da $Fave No.) (but. of Iatag *p.clfi.d)

I., saimII La~ -fhu5 If. T.' It~ -.T. Eff~El~icincy.

I QI~Gittla R I.' -T. -.NO. of Coasts I 6. Heads (0) Material T.S. (6) ussieciaI________

T.S. _____________

£.sett..s Clew,, Knuchiel Elliptical Cilate S Notmlsphoricsil P1.4t 11140 so Ill a..STep. boattS...l

00) Thickness Rosadita Radius. Ratio Apes Angie Red hase Dunimaite (Coolas wClafeswr)(a)_ _11 elfilivb,11 butt% Used O a~ .lther fastening (eei.ais kia 7. acetCImag

~ eerspeca.

ati.. Eli w si~ao t. wit ball giDescrib.a, e weates s~c Diu latliet Pneumat 8. Design Persso-S Epio 'A0 OF ~at ep.O OFrc.~...........f-1bKdýmei at esw 22 Te lions 9 isadl 10 mo be completed (or tube sections.

Di.ii 3 i~icmn 9. Tog; Shcets: Statelnauir.

Aisireais.

494MJ't2 -!.Ihcta n. Attahmen VS.). of

U)lives It to 14 toal, to be Completed for Inner Chatlem" of jacketed V*suels, of channel.4 of beets eackhsaeus.

IZStYtb 4.I~~Ig6AOG2BT.. .GI LUnick",es;

ý0. AllowencetZf.

iA ..Via- It.-In. Lesgsth-11...AL...j

12. Sameat Laa-SAO H I.T.t x(- R ... 1 .~dup~7 (weuldd. alal.. glfingS) (Ye a. W& or Gitdsb ý If.r. tT N'o. of coause 13. Nedsf~Iasa.~j~rSE.Q=~ ( b) IMetei ial _____T.S.

(- c) Matta;a &I_______Laaalai Thiba.. Ndluie 3.h. USe AesAb.Ieh laa...iee (C *.a o 0 Clalso (6-t10 (a) Walybem. EL812~ -___iaC (b) Charnel --___Iremovable., hailti used (e~ttsjqO.5.I (h e 0hlesmvau tmlg, f~co Pa~iwId !Nat-Tselie

'11.411p sMPS63 ItMCUI Hemo46J 9hi4; TVaete 64~aile 4,eai. E. <~hbs 0~0 4 .Itema belovw to V~v ar"Ie~c..

tow all varsaris where~.~ah.

A'Is. Saktefy valve Ota'lemi Nambary- S...... .aai 16. Hotlu 01 "la, lit.tse Tqf Motoritl rwtthLaktat

'.,euaqn.

K.28~-JS&JL~41 E~RI~~ZTt

-~-ThtteaJeJ, ble.____ Size -Location~.

19. Supp~o.'u:

S&Lat -N~...Lugs

___.. Lci; a -.=-=---Other JUAD -Attached AI PI = Sr~4tIAEU-(Yelof me) (Hunt.bf) lteambot) (Deagribal) (Whwet a mona 19. e.___________

_(13'S-f Wo'cvuiaicn of aer.1co for %HIjctt vessel was .611a~irnd)

V.isae nsirvnaio.

rpagon fit* 'iot l/~ ' A Darmi.a Grcii c-l.. eons a- iit hyonIj. -Pof Emg.stte6Z5He

.. " .6Z,= j....Uralsn ar!Vaisie.'iona Co"flofhd by..,eV..Ai.

Prof. En O. fit t. _. iet .Me I I re ceral). hv the stata si mode in tJis Iret lif *orc nlta h ul F 0 m she tales of constirti-(w~afta~cqu,,)

To. ..-ara .R.11 .1 h14 ro~iricare of *..h,.rvat.i.n

'.rc a. -, r.Careificage of Aalhotittation o.13U ClnrwFICIrE, OF SHOP INSPIEcTION VESSEL MADE ffl&QCR.LC1;N sThAnDfD mt 'T TzAImTE DIVISION at Euffejo, WJv York Is that mostrIrnp4ne hotdin4 a valid bentari..I..n issue.d Ity the NalfInIoe, nooanl at $Oiler end FIVOSCOP" Vesw.I.ow l*apeCt 811110'se 0%* Shtat..p.~ d'York _,.,,d ampordb;gir=n 14i.tua1 Casualty Q0. --Chiago, '1ll1MOIS howsp Iaoap,.rqd The proalswowavs..]

described in this Dt.ee~-r ata 111o"A cro-A l1A-j_ 4Ms Carter Ueatican III.111.019mical shim *.Flfliroe4 nerithwa, tho ina.1 ectve nor his ompi.l~ar mob..l &tny worrenty.

6 "rto:*d or imollalfd.

the.ram Sb. FSOrs, cadieol do sreibed In OIoI Mieoufc.,tuto r a Data Kept,. Vurlh.v,e,.,.

nethar the Inspelf tw ne"' lha siployev eltell be Udibli in', 1 1 v"knino lot any irees&net tnitey or propvrl V dome.ar or. aI-s a o anty kind &-;G ng ftrom at connected witthi. IN ajolorijon,..I--APlo' tanl'1 Notrnia oi.honal Boar. djttrorovince saJ We.. -&P4--r.d rhwi,...a

.%..-,d bVh, ~ N- ~io.a 4e1 of Soilar and PI*.sswo Vesase [noepetotoe staiw the ill or Prota"r. 'i.........

-- vr-1 p*Vyr' .I I- -. ' -______hay.raraa 1h. trmr In this Da,.e.sI.ama Nor r.0 hh ihe ,In~%dptf.G.,w vessel and staqe that parts reaf*otd to am data VI. a. ne * ... .-t Lncloided In 1%. conhlarti.is of ahep Inspection ha.'.be.n 4-A.hcftCIi L; -1 n that 1. it,&.i 4-1 ..l~~ .14 I.eber IN. n ..reeraar- ha. tonarruai-ad and assembled this pressure ws-a ae n c-datirmec.

1¶~h th* ANXIl ..ie 1'r 1.i i. 1 %-. de.-ltý-J

.c-1 -r s. t.partod and *a.b).c%.4 a.* -ydroasttic i-tra eind/o PA.-.611iC Tuna __... _. *. p1ý%.Irv *ia-I-s this. t.I~ Y.,.eI. liar "- V!,. la .: *;. r ~ .'sy _srv.NtVy nharuieva@4 of. Imlarlle, con..er..hg Oits pt.aout*y....a 41icielbit 114 fhA. MNen.tUfarm-ll-m. 1'*aVj F rfILtr'i'#ve i~r Its' I-reetoc itna; his earploy.;i laheil be Liabla in sany mno,,e for any p.'..-9~ nir.ai~ -propalrl y daosK. I, :,so '.1 1ý. is~a- ~fawn cc conoci with titinpciao.

Data_ q__(_ act~asi e~i. rt-o e ai:9-9 01 li.~~~~~~~~~~.~o Is-n tootm Nltoiinr.

a:.PoIn...

o Pointed .1.. i4.5.A. (1/71)Proto-Power Calc- 97-1 95 TF I at (k: 141 c ilq .%~he A V. SI R.I 1 41 1 % S' .it " taw Yasuo 1.Y. 940 II Attac ment: 7 Rev: A Page 7 of 7

RS-12-154, Attachment 2 - Heat Transfer Calculations Used to Develop Attachment 5 and Table A5-1 in the July 12, 2012, License Amendment Request

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