Text

ECM95-008, Rev. 3, Ultimate Heat Sink Design Basis
	ML12023A081
Person / Time
Site:	Waterford
Issue date:	01/18/2012
From:	; Entergy Nuclear South, Entergy Operations
To:	; Office of Nuclear Reactor Regulation
References
	W3F1-2012-0004 ECM95-008, Rev 3
	Download: ML12023A081 (98)
	v • d • e

Attachment W3F1-2012-0004 Calculations ECM95-008 and ECM95-009

[] ANO-1 0I ANO-2 [: GGNS El IP-2 El IP-3 El JAF --PNPS [L RBS El VY N W3 CALCULATION (1) EC # 2918 (2)Page I of 55 COVER PAGE (3) Design Basis Calc. IZ YES [_ NO (4), Z CALCULATION

[I EC Markup-(s Calculation No: ECM95-008 7 6) Revision:

3 (7) Title: Ultimate Heat Sink Design Basis (8) System(s):

ACC, CC (9) Review Org (Department):

DE-Mech (10) Safety Class: (11) Component/Equipment/Structure Type/Number:

[ Safety / Quality Related CC MPMPOO01-A ACCMPMPOO01A I- Augmented Quality Program CC MPMPOO01-AB ACCMPMPOO01B F-1 Non-Safety Related CC MPMPOO01-B ACCMTWROO01A (12) Document Type: BI 3.18 CC MHX0001A ACCMTWROO01 B (13) Keywords (Description/Topical CC MHX0001 B Codes): Ultimate Heat Sink, UHS, ACCW, CC MTWROO01A CCW, WCT, DCT, Cooling Tower CC MTWROOO1B REVIEWS (14) Name/Signature/Date (15) Name/Signature/Date (16) Name/Signature/Date Dale Gallodoro Steven Moynan John Russo see associated EC see associated EC see associated EC Responsible Engineer Z Design Verifier Supervisor/Approval F- Reviewer El-_ Comments Attached E- Comments Attached Page ii CALCULATION CALCULATION NO: ECM95-008 REFERENCE SHEET REVISION:

3 I. EC Markups Incorporated:

I1. Relationships:

Rev Input Output Impact Tracking Doc Doc Y/N No.RI. MN(Q)9-52, Ultimate Heat Sink Performance 2 EN D_R2. MN(Q)9-3, Ultimate Heat Sink Study 2 N D--_R3. 9C2-5Y, Chillers Heat Rejections 0 N []R4. W3-DBD-4, CCW/ACCW Design Bases 3-8 [ N N Document R5. WO-00050576, Per CC/ACC Train A Flow 0 N I-Balance Per PE-04-024 R6. PE-004-024, ACCW & CCW System Flow 2-1 E [--Balance R7. EC-191-036, CCWHx Outlet Temperature (DCT Fan Control) Instrument Loop Uncertainty 1 E D Calculation R8. EC-S05-013, UHS Containment Heat Loads 0 N El R9. W3 Technical Specification 3/4.7.4 M E1 R10. MN(Q)9-65, CCW Temperature Evaluation.

1 N N N R1 1. ECM03-007, Review of UHS Atmospheric Temperature Design Parameters to Support 0 N El EPU Implementation R12. TD-ZO10.0025, Zurn Industries Tech. Document 2 N El_-R13. Spec LOU-1 564.86 -Dry Cooling Towers 8 L-- N N R14. Spec LOU-1564.114A-Wet Cooling Towers 10 El N N R15. Spec LOU-1 564.75 -CCW Heat Exchanger 9 [-- N N R20. W3-DBD-13, Containment Spray Design Basis 1-12 El Z N Document R21. MN(Q)9-50, ACCW System Resistance 1 [- N N R22. ECM95-009, Ultimate Heat Sink Fan 1 E] N N Requirements R23. FSAR -Chapter 9 13B -] N N Ill. CROSS

REFERENCES:

C1. Letter ES-LOU-87-77, Dated July 18, 1977,

Subject:

Design Meteorological Data for the Ultimate Heat Sink, File No. 14Q-B-3A C2. ASME Section III Code, Subsection NC-3611 & ND-3611, 1971 Edition including Winter 72 Addenda IV. SOFTWARE USED: STER Version 5.04 by Holtec, W3 Software Manual 460000024 Vol. 1 Microsoft Excel Version 2002 SP3 V. OTHER CHANGES: NONE Page iii Revision:

R1e~cordofRvsn 0 Original Issue Determine equivalent meteorological conditions that UHS can reject the 0-1 design basis heat load.CR 97-0777 documented that the containment heat loads for the UHS did not contain certain conservative assumptions.

The purpose of this calculation 0-2 change is to revise the UHS design bases requirements corresponding to maximum containment heat load rate determined by calculation MN(Q)-9-3.

This is a complete rewrite; therefore no revision bars are used.Provides justification for use of hot air recirculation values and adds computation of the ACCW System design temperature in response to the recommended dispositions of Design Basis Review Open Items: OI-CCW-296-C and OI-CCW-297-C.

Adds Keywords to Section 3. Replaces Reference 3.3 and removes references to the FSAR. Corrects typographical errors. This is a complete rewrite; therefore no revision bars are used.Modified UHS Design Basis as a result of Total Heat Duty input changes at 3716 MWt. A methodology change was made in section 5.4 to ensure Tech Spec 3/4.7.4 compliance.

Calculation and Attachment changes have been made accordingly.

Added page 2 of 2 to Attachment 7.3 to include the regression analysis for the DCT. This analysis was referenced in section 6.1.1 of the calculation.

Section 6.6.4 was added to address Met tower DRN conditions from Calculation ECM03-007 (Ref. R22).03-509 The basis for the heat load from emergency diesel generators and the LPSI/HPSI/CS pumps in circular.

Calculation ECM95-008 references calculation MNQ9-3 for this heat load and MNQ9-3 references ECM95-008 for the same heat load. ECM95-008 now references Calculation MNQ9-65 which develops the basis for these heat loads.DRN Added Assumption 4.7 to clarify that containment heat loads were determined assuming 112°F CCW temperature (ECS01-005).05-766 This revision incorporated all outstanding changes and DRNs. ECS05-013 was changed to the new input for containment heat loading and all calculations were revised accordingly.

CR-WF3-2005-0230 documented that 2 the CCW flows used in the calc did not bound the As-Built flows determined during flow testing. The CCW accident flow has been increased to a bounding 6900 gpm.Corrected transposition errors in paragraphs 5.3 and 5.4, math operator in paragraph 6.3.1, and copy and paste error in Attachment 7.1, identified on 3 CR-WF3-2007-1420.

The errors did not affect the results of the calculation.

Therefore, this is an administrative change only.

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page iv NMyRqf TABLE OF CONTENTS 1.0 PURPOSE ............................................................................

1

2.0 CONCLUSION

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

2 3.0 INPUT CRITERIA .................................................................

3 4.0 ASSUMPTIONS

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

5 5.0 METHODS OF ANALYSIS ...................................................

6 6.0 CALCULATION

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

8 7.0 ATTACHMENT

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

24 EFFECTIVE PAGES Rev. 3 -ALL WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 1 of 24 mElayt 1.0 PURPOSE 1.1 The purpose of this calculation is to determine the Ultimate Heat Sink design basis under LOCA conditions using the worst combination meteorological design parameters.

1.2 This calculation also determines the ACCW System design temperature.

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 2 of 24

2.0 CONCLUSION

2.1 The UHS is capable of dissipating the LOCA heat duty requirements for both worst combination meteorological design parameters, 102°Fde78°Fwb and 9 8°Fdb/8 3°Fwb. The 102 0 Fdb/7 8°FWb meteorological condition would allow less fouling in the CCW heat exchanger in order to maintain a CCW outlet temperature of 115'F, therefore is chosen as the UHS design point. The design conditions for the UHS are given below.Dry Bulb Temperature (Tdb)Wet Bulb Temperature (TWb)DCT CCW Inlet Temperature DCT CCW Outlet/CCWHx Inlet Temp.DCT Heat Duty WCT ACCW Outlet/CCWHx Inlet Temp.CCWHx CCW Outlet Temperature CCWHx ACCW Outlet Temperature CCWHx Allowable Fouling Factor CCWHx Heat Duty WCT ACCW Inlet Temperature WCT Heat Duty WCT Cooling Range*As discussed in section 5.4, these values temperature to the CCWHx of 89.31F in maximum ACCW temperature of 89 0 F.-102 0 F-78 0 F-164.56 0 F-131.11OF-113.38 x 106 BTU/Hr-89.3 0 F*-115.0°F-113.77 0 F*-0.00159*-54.62 x 106 BTU/Hr-111.79 0 F*-59.72 x 106 BTU/Hr-22.49 0 F are calculated using an ACCW inlet order to maintain the Tech. Spec.As discussed in section 6.6.4, the meteorological condition of 91.3°Fdb/8 4.9°Fwb from Reference R1 1 is not more limiting than 102°Fdb/7 8°FWb case above.2.2 Using the limiting historical meteorological parameter, 10 2 0 Fdb/7 8°Fwb, a relationship (See Attachment 7.3) was developed to provide equivalent dry bulb temperature/corresponding wet bulb temperature required to maintain overall UHS design heat duty capacity.

The linear relationship demonstrates that for a dry bulb temperature increase/decrease of 1.0°F, the corresponding wet bulb temperature can decrease/increase approximately 1.7 0 F and maintain the UHS design heat duty capacity.

The relationship also demonstrates the UHS can dissipate its design heat load for any dry bulb temperature below 93 0 F, regardless of wet bulb temperature, since wet bulb temperature can not exceed dry bulb temperature.

2.3 ACCW System design temperature is 125 0 F.

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 3 of 24 EGNEIGPg3o2 3.0 INPUT CRITERIA 3.1 Peak UHS Heat Duty Requirements Containment Heat Duty 1 = 158 x 106 BTU/hr (Ref. R8)Essential Chiller Heat Duty =5.1 x 106 BTU/hr (Ref. R3)Auxiliary Heat Duty 2 = 10.0 x 106 BTU/hr (Ref. R10)Total Heat Duty = 173.1 x 106 BTU/hr CCWS Heat Duty = 168.0 x 106 BTU/hr Notes: 1. Containment heat duty has been conservatively rounded up from 157.69 x 106 BTU/Hr given in Ref. R8.2. Includes Diesel Generator and HPSI, LPSI and Containment Spray pumps 3.2 Maximum One Hour Ambient Conditions Drybulb Temperature Ref. C1 contains a table which shows the maximum drybulb and concurrent wetbulb for the New Orleans area is 102 and 77 0 F respectively.

One degree is added to the wetbulb temperature for conservatism bringing the maximum 1 hour1.157407e-5 days 2.777778e-4 hours 1.653439e-6 weeks 3.805e-7 months drybulb/corresponding wetbulb temperatures to 102/780F.Wetbulb Temperature Ref. C1 discusses that 83 0 F is the maximum wetbulb temperature of record at Moisant Field for the period between 1946 and 1977. The reference discusses that 83 0 F is an acceptable design value and satisfies the requirements of Reg.Guide 1.27. A table attached to the reference provides maximum wetbulb and corresponding drybulb temperatures however, 83 0 F is not an entry in the table.An entry is provided for 83 0 F in the table for maximum drybulb and corresponding wetbulb temperatures.

Based on this evaluation, at 83 0 F wetbulb temperature, the corresponding drybulb temperature is 98 0 F.The site Met Tower data was evaluated in calculation Reference Ri 1 over a period from 1997 to 2001. This review indicates that the maximum one hour wetbulb temperature exceeded 83°F at 84.9 0 F with an associated drybulb temperature of 91.27 0 F. This calculation will determine if the 84.9 0 Fwb/91.3 0 Fdb met condition is more limiting for the highest Twb and coincident Tdb case.3.3 Maintain a CCW outlet temperature of 11 5 0 F to the plant auxiliaries.(Ref. R4)

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 4 of 24 3.4 Accident Flow Rates CCW Flow Rate -CFC (1400 gpm ea.) =Emergency Diesel Gen. =Shutdown Cooling Hx. =Safeguard Pumps =Total =(Ref. R5)2800 gpm 950 gpm 3100 gpm 50 gpm 6900 gpm ACCW Flow Rate -CCWHx -Chiller =Total =(Ref. R6)4500 gpm 850 gpm 5350 gpm 3.5 Hudson Products DCT Performance Curves -Heat Duty vs. Outlet Temperature as a function of Dry Bulb Temperature. (Ref. R1)3.6 Zurn Industries WCT Performance Curves -Outlet Temperature vs. Wet Bulb Temperature as a function of Cooling Range. (Ref. R12)3.7 Hot Air Recirculation Effect Dry Bulb Temperature

-1.9°F Wet Bulb Temperature

-1.0°F (Ref. 7.4)(Ref. 7.4)

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 5 of 24 4.0 ASSUMPTIONS 4.1 100% tube capacity on the DCT.4.2 95% tube capacity on the CCWHx.4.3 Linear interpolation between the flow rates of 6500 gpm and 7500 gpm will be used to determine the DCT performance at the accident CCW flow rate of 6900 gpm at 11 5 0 F CCW temperature.

4.4 Linear interpolation between the flow rates of 5000 gpm and 5750 gpm will be used to determine the WCT performance at the accident ACCW flow rate of 5350 gpm.4.5 The uncertainty associated with the CCW temperature control given in Reference R7 does have to be accounted for in this analysis.

Valves ACC-127A(B), located downstream of the CCW temperature control valves ACC-126A(B), will be throttled to ensure the design flow to the essential chiller is maintained.

Therefore, should ACC-126A(B) respond by increasing ACCW flow through the CCW heat exchanger to maintain CCW temperature at 112.6°F (115 0 F less 2.4 0 F maximum uncertainty), CCW temperature will rise to a maximum of 115'F since ACC-127A(B) will prevent ACCW flow from exceeding a value where design flow the essential chiller is not maintained.

By design, the UHS will then self-correct and CCW temperature will rise to a maximum of 115 0 F until ambient conditions become more favorable or when the accident heat load is reduced.4.6 This analysis assumes the Post Accident Sampling (PAS) system is secured.The impact is negligible since the operation of the PAS system is intermittent, and the PAS system heat load and cooling water flow are negligible.

In addition, PAS is required to be placed in service after 3 hours3.472222e-5 days 8.333333e-4 hours 4.960317e-6 weeks 1.1415e-6 months post-accident, after peak accident heat load has occurred. (Ref. R2)4.7 Containment heat loads were determined assuming a 112 0 F CCW temperature because this maximizes the heat input into the Ultimate Heat Sink. This calculation will use these maximum heat loads assuming 115'F CCW temperature to determine the heat removal contribution from the Dry Cooling tower, Wet Cooling Tower and the CCW Heat Exchangers.

This is acceptable because if CCW temperature were being controlled at 115'F, the heat load into the Ultimate heat Sink would be less. (Ref. R8)

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 6 of 24 EGNEIGPg6o2 5.0 METHODS OF ANALYSIS 5.1 Linear equations can be derived to describe the DCT and WCT performance since their performance curves assume a linear relationship (y = mx +b). Using the "Regression" Tool in Microsoft Excel, the slope and intercept of the DCT and WCT performance curves are calculated.

These results will provide an equation to describe the DCT performance as a function of dry bulb temperature and CCW flow and a WCT performance as a function of cooling range and wet bulb temperature.

5.2 The DCT heat duty and associated CCW outlet temperatures at dry bulb temperatures of 980 and 102 0 F are calculated using the equations derived from Section 5.1 and the conservation of energy.5.3 The WCT heat duty at dry bulb temperatures of 980 and 102'F is determined by subtracting the DCT heat duty from the, UHS total heat duty. The WCT outlet temperature is calculated using dry bulb/wet bulb temperatures of 102 0 F/78°F and 98°F/83°F using the equations derived from Section 5.1.5.4 The CCWHx heat duty is determined by subtracting the Essential Chiller heat duty from the WCT heat duty. With the CCW and ACCW inlet temperatures calculated and requiring a CCW outlet temperature of 11 5 0 F, STER Version 5.04 will calculate an allowable CCWHx fouling factor.The ACCW heat exchanger inlet temperature is set equal to 89.3 0 F if the calculated WCT outlet temperature in section 6.3 is less than 89.0°F. The Technical Specification maximum WCT basin water temperature is 89.0°F (Tech.Spec. Requirement 3/4.7.4).

The WCT performance is dictated by wet bulb temperature conditions as shown in the performance curves and will perform as calculated at the limiting atmospheric conditions.

However for the cases in which the WCT can cool the ACCW flow below 89°F, the Tech. Spec. WCT basin temperature limit of 89 0 F is the more limiting condition impacting the CCW heat exchanger fouling (Section 6.4).5.5 The design basis of the UHS will be based on the worst combination meteorological design parameter, maximum one hour Tddcoincident TWb or maximum one hour Twb/coincident Tdb, that produces the lowest CCWHx fouling factor.5.6 Using the most limiting historical meteorological design parameter as the baseline, a heat balance will be performed for various dry bulb temperatures to WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 7 of 24 determine the maximum wet bulb temperature allowed for the UHS to maintain its overall design heat duty capacity.5.7 Water density is determined using the average respective system temperature i.e. [(CCWmax+CCWmin)/2].

This density is used throughout the calculations such that the conservation of mass is maintained.

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 8 of 24 6.0 CALCULATION 6.1 Equation Fitting on Performance Curves 6.1.1 Dry Cooling Tower Two data points, CCW outlet temperature (CCWout) and Heat Duty, (Q), for dry bulb temperatures (Tdb) of 80°F, 90'F and 102'F were obtained from the Hudson DCT performance curves. The slope and intercept of these curves were calculated using Microsoft Excel Linear Regression Analysis.

The results are provided below. The printouts are provided in Attachment 7.1.CCW Flow Rate of 6500 gpm Temp.Dry Bulb (-F)80 90 102 Slope (CCWot- OF)4.4 4.4 4.4 Intercept (BTU x 106)-354-398-442 Alntercept Ref.- 80'F Tdb (BTU X 106)N/A-44-88 Alntercept/°F Tdb = -4.4 (Worst Case)From the above table, the linear equation at a CCW flow rate of 6500 gpm that fits the DCT performance as a function of Dry Bulb Temperature is described below: Q6500 gpM = 4.4CCWot -(354 + 4.4 (Tdb -80))where: Q6500 gpm CCWout Tdb= DCT Heat Duty Performance (BTU/Hr x 106)= CCW Outlet Temperature

(°F)= Dry Bulb Temperature (OF)CCW Flow Rate of 7500 gpm Temp.Dry Bulb (OF)80 90 102 Slope (CCWout- OF)4.0 4.0 4.0 Intercept (BTU X 106)-320-360-408 Alntercept Ref.- 80'F Tdb (BTU X 106)N/A-40-88 Alntercept

/ °F Tdb = -4.0 WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 9 of 24 From the above table, the linear equation at a CCW flow rate of 7500 gpm that fits the DCT performance as a function of Dry Bulb Temperature is described below: Q7500 gpm = 4.0CCWout

-(320 + 4.0(Tdb -80))where: Q 7 5 00 gpm CCWout Tdb= DCT Heat Duty Performance

-BTU/Hr x 106= CCW Outlet Temperature (OF)= Dry Bulb Temperature (OF)6.1.2 Wet Cooling Tower Two data points, Wet Bulb Temperature (TWb) and ACCW outlet temperature (ACCWout), for cooling ranges of 10.8°F, 21.6 0 F and 27 0 F were obtained from the Zurn WCT performance curves. The slope and intercept of these curves were calculated using Microsoft Excel Regression Analysis.

The results are provided below. The printouts are provided in Attachment 7.1.Cooling Rang (OF)10.8 21.6 27 ACCW Flow Rate of 5000 gpm e Slope Intercept (TWb-°F) (ACCW 0 ,,-°F)0.725 27.125 0.675 34.125 0.600 41.75 The linear equation for an ACCW flow of 5000 gpm that fits the WCT performance as a function of Cooling Range between 10.8 0 F and 21.6°F is described below: ASlope / °F Cooling Range = -0.00463 Alntercept

/ OF Cooling Range = 0.648 ACCWout =(0.725 -0.00463(AT

-10.8))Twb

+(27.125 + 0.648(AT-10.8))The linear equation for an ACCW flow of 5000 gpm that fits the WCT performance as a function of Cooling Range between 21.6 0 F and 27 0 F is described below: ASlope / OF Cooling Range = -0.0139 Alntercept/

°F Cooling Range = 1.412 WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 10 of 24 EWMRMI ACCWout =(0.675 -0.0139(AT

-21.6))Twb

+(34.125 + 1.412(AT -21.6))Cooling Rang (OF)ACCW Flow Rate of 5750 gpm e Slope Intercept (Twb-°F) (ACCWoud-°F) 0.775 24.125 0.600 42.000 0.575 45.125 10.8 21.6 27 The linear equation for an ACCW flow of performance as a function of Cooling Range described below: 5750 gpm that fits the WCT between 10.8°F and 21.6 0 F is ASIope / °F Cooling Range = -0.01620 Aintercept

/ OF Cooling Range = 1.655 ACCWOUt = (0.775 -0.01620(AT

-10.8))Twb

+(24.125 + 1.655(AT-10.8))The linear equation for an ACCW flow of 5750 gpm that fits the WCT performance as a function of Cooling Range between 21.6 0 F and 27.0 0 F is described below: ASIope / °F Cooling Range = -0.00463 Alntercept

/ °F Cooling Range = 0.5787 ACCWOUt =(0.6 -0.00463(AT

-21.6))Twb

+(42.00 + 0.5787(AT

-21.6))where: ACCWOUt Twb AT= ACCW Outlet Temperature (OF)= Wet Bulb Temperature (OF)= WCT Cooling Range Required (OF)

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 11 of 24 6.2 Dry Cooling Tower Performance 6.2.1 DCT Performance at Tdb = 102 0 F Determine DCT inlet temperature Q = mcp(Tin -Tout) or Tin = (Q/mcp) + Tout where Tin = DCT Inlet Temperature (OF)Q = 168.0 x 106 BTU/Hr (less Chiller Heat Duty) (Input 3.1)m = 6900 gpm x 60 min/hr / 0.016293 ft 3/Ibm / 7.4805 gal/ft 3= 3.39678 x 106 Ibm/hr Tout = 115°F @ CCW Heat Exchanger Cp = 0.998 BTU/Ibm -OF Tin = (168.0 x 106/ (3.39678 x 106

0.998)) + 115 Tin = 164.56°F Tavg = 139.79 0 F = 140'F The CCWout temperature at the DCT can be calculated using the conservation of energy where: QDCT = mcp(Tin -Tout)This heat balance will be performed to calculate the DCT Tout temperature at DCT performance curve inlet CCW flows of 6500 gpm and 7500 gpm and then interpolated at the CCW accident design flow of 6900 gpm.Q6500 gpm = 4.4*Tout -(354 + 4.4 (Tdb -80)) = mcp(Tin -Tout) (Sec. 6.1.1)where: Q6500 = Heat Transferred

@ CCW Flow of 6500 gpm Tout = CCWout temperature Tdb = 103.9 0 F (adding 1.9°F for Recirculation) (Input. 3.2, 3.7)m = 6500 gpm x 60 min/hr / 0.016293 ft 3/Ibm / 7.4805 gal/ft 3= 3.200 x 106 Ibm/hr cp = 0.998 BTU/Ibm -OF Tin = 164.56°F Solving for Tout yields 4.4*Tout + mcpTout = (354 + 4.4 (Tdb -80)) + mcpTin 4.4*Tout + (3.200)(0.998)Tout

= 354 + 4.4(103.9-80)

+(3.200)(0.998)*164.56 Tout = 129.67°F WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 12 of 24 Calculating Heat Transferred:

Q6500 = mcp(Tin -Tout)Q6500 = (3.200)(0.998)(164.56

-129.67)Q6500 = 111.42 x 106 BTU/Hr Performing Heat Balance at a CCW Flow Rate of 7500 gpm: Q 7 5oogpm = 4.0*Tout-(320 + 4.0(Tdb -80)) = mcp(Tin -Tout) (Sec. 6.1.1)where: Q7500 = Heat Transferred

@ CCW Flow of 7500 gpm Tout = CCWout Temperature Tdb = 103.9°F (adding 1.9°F for Recirculation) (Input 3.2, 3.7)m = 7500 gpm x 60 min/hr / 0.016293 ft 3 / Ibm / 7.4805 gal/ft 3= 3.692 x 106 Ibm/hr Cp = 0.998 BTU/Ibm -'F Tin = 164.56°F Solving for Tout yields: 4.0*Tout + mcpTout = (320 + 4.0(Tdb -80)) + mcpTi 4.0*Tout + (3.692)(0.998)Tout

= 320 + 4.0(103.9-80)

+(3.692)(0.998)*164.56 Tout = 132.99°F Calculating Heat Transferred:

Q7500 = mcp(Tin -Tout)Q7500 = (3.692)(0.998)(164.56

-132.99)Q7500 = 116.32 x 106 BTU/Hr By linear interpolation, the DCT heat duty @ 6900 gpm is: Q6900 gpm = Q6500 gpm + 6900-6500

(Q7500 gpm-Q6500 gpm)7500-6500 Q6900 gpm = 111.42x10 6 + (0.4)(116.32x10 6 -111.42x10 6)Q6900 gpm = 113.38x10 6 BTU/Hr Calculating CCWout Temperature:

m = 3.39678 x 106 Ibm/hr cp = 0.998 BTU/Ibm -'F Tout = Tin -(Q/mcp)Tout = 164.56 -(113.38/3.39678/0.998)

Tout = 131.11°F WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 13 of 24 6.2.2 DCT Performance at Tdb = 98°F The method of analysis for the DCT performance at a dry bulb temperature of 98 0 F is identical to the analysis given 6.2.1.Q6soo gprm = 4.4*Tout -(354 + 4.4 (Tdb -80)) = mcp(Tin -Tout)where: Q6500 Tout Tdb m Cp Tin (Sec. 6.1.1)(Input 3.2, 3.7)= Heat Transferred

@ CCW Flow of 6500 gpm= CCWout Temperature

= 99.9°F (adding 1.9°F for Recirculation)

= 3.200 Ibm/hr (x 106) (6500 gpm)= 0.998 BTU/Ibm -"F= 164.56°F Solving for Tout yields 4.4*Tout + mcpTout = (354 + 4.4 (Tdb -80)) + mcpTin 4.4*Tout + (3.200)(0.998)Tout

= 354 + 4.4(99.9-80)

+ (3.200)(0.998)*164.56 Tout = 127.36°F Calculating Heat Transferred:

Q 6 5oo = mcp(Tin -Tout)Q6500 = (3.200)(0.998)(164.56-127.36)Q 6 5oo = 118.8 x 106 BTU/Hr Performing Heat Balance at a CCW Flow Rate of 7500 gpm: Q7500 gpm = 4.0*Tout -(320 + 4.0(Tdb -80)) = mcp(Tin -Tout)where: Q7500 Tout Tdb m Co Tin (Sec. 6.1.1)(Input 3.2, 3.7)= Heat Transferred

@ CCW Flow of 7500 gpm= CCWout Temperature

= 99.9°F (adding 1.9 0 F for Recirculation)

= 3.692 Ibm/hr (x 106) (7500 gpm)= 0.998 BTU/Ibm -'F= 164.56°F Solving for Tout yields: 4.0*Tout + mcpTout = (320 + 4.0(Tdb -80)) + mcpTin 4.0*Tout + (3.692)(0.998)Tout

= 320 + 4.0(99.9-80)

+(3.692)(0.998)*164.36 Tout = 130.90°F WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 14 of 24 Calculating Heat Transferred:

Q75 0 0 = mcp(Tin -Tout)Q7500= (3.692)(0.998)(164.56

-130.90)Q7oo = 124.02 x 106 BTU/Hr By linear interpolation, the DCT heat duty @ 6900 gpm is: Q 6 9 0 0 gpm = Q 6 5 0 0 gpm + 6900-6500

(Q70oo gpm-Q6500 gpm)7500-6500 Q6900 gpm = 118.8x10 6 + (0.4)(124.02x10 6-118.8x10 6)Q 6 9 oo gpm = 120.89 X 106 BTU/Hr Calculating CCWout Temperature:

m = 3.39678 x 106 Ibm/hr cp = 0.998 BTU/Ibm -OF Tout = Tin -(Q/mCp)Tout = 164.56 -(120.89/3.39678/0.998)

Tout = 128.90°F 6.3 Wet Cooling Tower Performance 6.3.1 WCT Performance at Twb = 78 0 F and Tdb = 102'F Determine WCT Heat Duty Qwct = Total Heat Duty-DCT Heat Dissipated

@ Tdb of 102'F.Qwct = 173.10 x 106 -113.38 x 106 (Input 3.1, Sec. 6.2.1)Qwct = 59.72 x 106 BTU/Hr Determine WCT Cooling Range Qwct = mcp(AT) or AT = Qwct/mcp where AT = Cooling Range (OF)m = 5350 gpm / 0.01613 ft 3/lbm / 7.4805 gal/ft 3 x 60 min/hr=2.660 x 106 Ibm/hr cp = 0.998 BTU/Ibm -OF AT = 59.72 x 106/ 2.660 x 106 / 0.998 = 22.49°F Using a 22.49°F WCT Cooling range and increasing Twb by 1.0°F to account for recirculation, the ACCW outlet temperature can be calculated. (Input 3.7)

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 15 of 24 At 5000 gpm ACCWOUt = (0.675 -0.0139(22.49

-21.6))*79

+(34.125 + 1.412(22.49

-21.6))ACCWout = 87.73°F (Sec. 6.1.2)At 5750 gpm ACCWOut = (0.6 -0.00463(22.49

-21.6))*79

+ (42.00 + 0.5787(22.49

-21.6))ACCWOUt = 89.59°F (Sec. 6.1.2)By linear interpolation, the WCT heat duty @ 5350 gpm is: ACCWOUt = 87.73 + 5350-5000

(89.59 -87.73)5750-5000 ACCWout = 88.60°F ACCWOUt is less than 89.0°F, therefore:

ACCWOUt = 89.3 0 F (for CCWHx analysis) (Sec. 5.4)WCT inlet Temperature WCTin = 89.3°F + 22.49°F = 111.79°F 6.3.2 WCT Performance at T~h = 83 0 F and Tdb = 98 0 F Determine WCT Heat Duty Qwct = Total Heat Duty-DCT Heat Dissipated

@ Tdb of 98 0 F.Qwct = 173.1x 106 -120.89 x 106 (Input. 3.1, Sec. 6.2.2)Qwct = 52.21 x 106 BTU/Hr Determine WCT Cooling Range Qwct = mcp(AT) or AT = Qwct/mcp Where: AT = Cooling Range (OF)m = 5350 gpm / 0.01613 ft 3/Ibm / 7.4805 gal/ft 3 x 60 min/hr= 2.660 x 106 Ibm/hr cp = 0.998 BTU/Ibm -°F AT = 52.21 x 106 /2.660 x 106 / 0.998 = 19.66°F WATERFORD 3 DESIGN ECM95-008 Rev. 3 a ENGINEERING Page 16 of 24 Usn 966FWTCoin ag ndicesn Tbb .0 Ft con Using a 19.66°F WCT Cooling range and increasing Twb by 1.0°F to account for recirculation, the ACCW outlet temperature can be calculated. (Input 3.7)At 5000 gpm ACCWout = (0.725 -0.00463(19.66

-10.8))*84

+(27.125 + 0.648(19.66

-10.8))ACCWout = 90.32 0 F (Sec. 6.1.2)At 5750 gpm ACCWout = (0.775 -0.01620(19.66

-10.8))*84

+(24.125 + 1.655(19.66

-10.8))ACCWout = 91.83°F (Sec. 6.1.2)By linear interpolation, the WCT heat duty @ 5350 gpm is: ACCWout = 90.32 + 5350-5000

(91.83 -90.32)5750-5000 ACCWout:=

91.03°F 6.4 CCW Heat Exchanger Performance 6.4.1 CCWHx Performance at Twb = 78°F and Tdb = 102'F Determine CCWHx Heat Duty QCCWHx = WCT -Chiller Heat Duty @ Tdb of 102'F.QCCWHx = 59.72 X 106 -5.1 X 106 QCCWHx = 54.62 x 106 BTU/Hr (Sec. 6.3.1)(Input 3.1)As determined in Section 6.3.1, the WCT will return the ACCW flow back to the WCT basins at a temperature of 88.60°F in order to meet the Tech. Spec.Maximum WCT Basin Temperature Limit, the maximum allowable CCW heat exchanger fouling will be calculated using and ACCW inlet temperature of 89.3°F. The maximum allowable fouling is determined for an ACCW inlet temperature of 89.3 0 F, because the maximum allowable fouling is minimized at the higher ACCW inlet temperature.

Determine ACCWout Temperature QCCWHx = mcp(Tout -Tin) or Tout = QCCWHx/mCp+

Tin WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 17 of 24 Ewhere: where: m Cp Tin= 4500 gpm / 7.4805 gal/ft3 / 0.01613 ft3/Ibm

60 min/hr=2.238 x 106 Ibm/hr @ 89 0 F= 0.998 BTU/Ibm -'F= 89.3°F (Sec. 6.3.1)Tout = 54.62 x 10 6/2.238 x 10 6/0.998+89.3 Tout = 113.76°F Using STER Version 5.04, the following heat exchanger calculated for a CCWout temperature of 115 0 F. The printouts Attachment 7.2 performance is are provided in CCWin 131.11 CCW 0 1 t ACCWin 115.0 89.3 ACCWouU 113.77 Fouling Factor 0.00159* Calculated by STER Version 5.04 Additionally, the ACCWout temperature will be calculated using the actual WCT outlet temperature (i.e. CCW heat exchanger inlet temperature).

ACCWin temperature calculated in Section 6.3.1.Tin = 88.60'F Tout = 54.62 x 10 6/2.238 x 106 / 0.998 + 88.60 Tout = 113.06 0 F Using STER Version 5.04, the following heat calculated for a CCWout temperature of 11 5 0 F.(Sec. 6.3.1)exchanger performance is Fouling Factor 0.00172 CCWin 131.11 CCWout ACCWi ACCWou, 115.0 88.60 113.07* Calculated by STER Version 5.04 6.4.2 CCWHx Performance at TWb =83°F and Tdb = 98°F Determine CCWHx Heat Duty QCCWHx = WCT -Chiller Heat Duty @QCCWHx = 52.21 x 10 6 -5.1 x 10 6 QCCWHx = 47.11 X 106 BTU/Hr Tdb of 98°F.(Sec. 6.3.2)(Input 3.1)

WATERFORD 3 DESIGN ECM95-008 Rev. 3 0 ENGINEERING Page 18 of 24 ENTE I Determine ACCWout Temperature QCCWHx = mcp(Tout -Tin) or Tout = QCCWHx/mCp

+ Tin where: m = 4500 gpm / 7.4805 gal/ft 3 / 0.01613 ft 3/Ibm

60 min/hr= 2.238 x 106 Ibm/hr cp = 0.998 BTU/Ibm -'F Tin = 91.03'F (Sec. 6.3.2)Tout = 47.11 x 10 6/2.238 x 10 6 / 0.998 + 91.03 Tout= 112.12°F Using STER Version 5.04, the following heat exchanger performance is calculated for a CCW,,t temperature of 115 0 F. The printouts are provided in Attachment 7.2 CCWin CCWout 128.90 115.0 ACCWin 91.03 ACCWou*112.14 Fouling Factor 0.00197* Calculated by STER Version 5.04 WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 19 of 24 6.5 Ultimate Heat Sink Design Points The worst case ambient condition for the UHS is a Tdb of 102'F and a TWb of 78°F. This conclusion is based on the allowable fouling for the CCW heat exchanger to maintain a CCW outlet temperature of 115'F is less under these ambient conditions.

The design points for the UHS are given below.Dry Bulb Temperature (Tdb)Wet Bulb Temperature (Twb)DCT CCW Inlet Temperature DCT CCW Outlet/CCWHx Inlet Temperature DCT Heat Duty WCT ACCW Outlet/CCWHx Inlet Temperature CCWHx CCW Outlet Temperature CCWHx ACCW Outlet Temperature CCWHx Allowable Fouling Factor CCWHx Heat Duty WCT ACCW Inlet Temperature WCT Heat Duty WCT Cooling Range-102 0 F (Input 3.2)-78 0 F (Input 3.2)-164.56°F (Sec. 6.2.1)-131.11°F (Sec. 6.2.1)-113.38x 106 BTU/Hr (Sec. 6.2.1)-89.3 0 F* (Sec. 6.3.1)-115.0°F (Input 3.3)-113.77 0 F* (Sec. 6.4.1)-0.00159 (Sec. 6.4.1)-54.62 x 106 BTU/Hr (Sec. 6.4.1)-111.79 0 F* (Sec. 6.3.1)-59.72 x 106 BTU/Hr (Sec. 6.3.1)-22.49°F (Sec. 6.31)*As discussed in section 5.4, these values are calculated using an ACCW inlet temperature to the CCWHx of 89.3 0 F in order to maintain the Tech. Spec.maximum ACCW temperature of 89.0°F.6.6 Maximum TWb at Various Tdb to Maintain Overall UHS Design Heat Duty Capacity.The most limiting historical ambient condition for the UHS was determined to be a Tdb of 102 0 F and a TWb of 78 0 F. This analysis will determine equivalent meteorological conditions for the UHS to maintain its overall design heat duty capacity using the limiting fouling factor determined in the previous sections for the CCW heat exchanger.

6.6.1 DCT Performance at TO = 105 0 F The CCWout temperature at the DCT can be calculated using the conservation of energy where: QDCT = mcp(Tin -Tout)Heat capacity of the DCT at a CCW flow rate of 6500 gpm is calculated using the equation:

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 20 of 24 E-MaR QDCT = 4.4*Tout -(354 + 4.4 (Tdb -80))(Sec. 6.1.1)Solving the two equations, the heat balance becomes at a CCW flow of 6500 gpm: 4.4*Tout-(354

+ 4.4 (Tdb -80)) = mcp(Tin-Tout) where: Tout Tdb m Cp Tin= CCWout temperature

= 106.9°F (adding 1.9°F for Recirculation) (Input 3.2, 3.7)= 3.200 Ibm/hr (x 106) (6500 gpm)= 0.998 BTU/Ibm -'F= 164.56°F (Sec. 6.2.1)Solving for Tout yields 4.4*Tout + mcpTout = (354 + 4.4 (Tdb -80)) + mcpTin 4.4*Tout + (3.200)(0.998)Tout

= 354 + 4.4(106.9-80)

+(3.200)(0.998)*164.56 Tout = 131.41°F Calculating Heat Transferred:

QDCT = mcp(Tin -Tout)QDCT = (3.200)(0.998)(164.56

-131.41)QDCT = 105.86 x 106 BTU/Hr Heat capacity of the DCT at a CCW flow rate of 7500 gpm is calculated using the equation: QOCT = 4*Tout -(320 + 4 (Tdb -80))(Sec. 6.1.1)Using the Conservation of Energy, the heat balance becomes at a CCW flow of 7500 gpm: 4*Tout-(320

+ 4 (Tdb -80)) = mCp(Tin-Tout) where: Tout Tdb m Cp Tin= CCWout temperature

= 106.9°F (adding 1.9°F for Recirculation)

= 3.692 Ibm/hr (x 106) (7500 gpm)= 0.998 BTU/Ibm -'F= 164.56°F (Input 3.2, 3.7)(Sec. 6.2.1)Solving for Tout yields 4*Tout + mcpTout = (320 + 4 (Tdb -80)) + mcpTin WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 21 of 24 4*Tout + (3.692)(0.998)Tout

= 320 + 4(106.9-80)

+(3.692)(0.998)*164.56 Tout = 134.55°F Calculating Heat Transferred:

QOCT = mcp(Tin -Tout)QDCT = (3.692)(0.998)(164.56

-134.55)QDCT = 110.58 x 10 6 BTU/Hr By linear interpolation, the DCT heat duty @ 6900 gpm is: Q 6 9 0 0 gpm = Q 6 5 0 0 gpm + 6900-6500

(Q 7 5 0 0 gp-mQ6500 gpm)7500-6500 Q69oo gprn = 105.86xl 0 6 + (0.4)(110.59xl 06 -105.86xl 06)Q6900gprm

= 107.75x10 6 BTU/Hr Calculating CCWout Temperature:

m = 3.39678 x 106 Ibm/hr cp = 0.998 BTU/Ibm -°F Tout = Ti, -(Q/mcp)Tout = 164.56 -(107.75/3.39678/0.998)

Tout = 132.78°F 6.6.2 Required CCWHx Performance at Tdb = 105'F Determine CCWHx Heat Duty QCCWHx = Total -DCT -Chiller Heat Duty QCCWHx = 173.1 x 106 107.75 x 106- 5.1 X 106 (Input 3.1, Sec. 6.6.1)QCCWHx = 60.25 X 106 BTU/Hr Determine ACCWout Temperature Using STER Version 5.04, an ACCW inlet temperature of 86.7 0 F is required to dissipate the above heat load.-The printout is provided in Attachment 7.3 WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 22 of 24 EMMRn 6.6.3 Maximum Twb for a Tdb of 105'F Determine WCT Heat Duty Qw=t = Total Heat Duty-DCT Heat Dissipated Qwct = 173.1 x 10 6 -107.75 x 106 Qwct = 65.35 x 106 BTU/Hr (Input 3.1, Sec. 6.6.2)Determine WCT Cooling Range Qw:t = mcp(AT) or AT = Qwct/mcp where AT m Cp= Cooling Range (OF)= 2.660 x 106 Ibm/hr (5350 gpm)= 0.998 BTU/lbm -OF AT = 65.35 x 10 6/2.660 x 10 6/0.998 = 24.61°F Using a 24.61°F WCT Cooling range and an ACCW outlet temperature of 86.70F, the maximum Twb can be calculated.

At 5000 gpm: 86.7-F = (0.675 -0.0139(24.61

-21.6))*Twb

+(34.125 + 1.412(24.61

-21.6))(Sec. 6.1.2)Solving for Twb yields: Twb = 76.32 0 F At 5750 gpm: 86.7°F = (0.6 -0.00463(24.61

-21.6))*Twb

+(42 + 0.5787(24.61

-21.6))(Sec. 6.1.2)Solving for Twb yields: Twb = 73.30°F By linear interpolation and subtracting 1 OF to account for recirculation (and @5350 gpm) yields: (Input 3.7)Twb = 76.32+ 5350-5000

(73.30-76.32)

-1.0 5750-5000 Twb = 73.91°F WATERFORD 3 DESIGN ECM95-008 Rev. 3 SENGINEERING Page 23 of 24 The methodology given -in Section 6.6 was inputted into Microsoft Excel to determine equivalent meteorological conditions to maintain overall UHS design heat duty capacity.

The correlation between dry bulb and the corresponding wet bulb is provided in Attachment 7.3.6.6.4 Equivalent Meteorological conditions The Equivalent Meteorological Conditions for UHS plot given in Attachment 7.3 contains the three meteorological condition points: 1. 102 0 Fdb/7 8°Fwb 2. 9 8°Fdb 1 8 3°Fwb 3. 91.3 0 FdJ84.9°Fwb The 91.3°Fdb/8 4.9 0 FWb point falls in the acceptable range of the plot and therefore, is bounded by the curve. It is also noted that the 102 0 Fdb/7 8°Fwb point does not fall on the curve as may be expected.

This is due to the methodology discussed in section 5.4. The WCT basin temperature would be maintained cooler than the temperature specified in Technical Specification 3/4.7.4, assuming the design basis meteorological condition of 102 0 Fd/78 0 FWb.6.7 ACCW System Design Temperature In accordance with ASME Code ND-361 1, the piping is designed for the most severe condition of coincident pressure and temperature.

The maximum ACCW temperature, which occurs for the meteorological condition of 102 0 F drybulb and 78 0 F wetbulb, is 111.79°F.

Thus, the design temperature of 125°F as noted in PASSPORT is acceptable for ACCW System piping.(Ref. C2)

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Page 24 of 24 7.0 ATTACHMENT 7.1 Microsoft Excel Regression Analysis (2 pages)7.2 STER Version 5.04 Printouts (6 pages)7.3 Equivalent Meteorological Conditions for UHS to Dissipate Design Basis Heat Load (7 pages).7.4 Recirculation Effect on Dry Cooling Towers (9 Pages)7.5 Dry Cooling Tower Performance Curves (3 Pages)

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Attachment 7.1 Page 1 of 2 EITERGY Dry Cooling Tower Performance Curves -Regression Analysis Ref. Hudson Performance Curves Flow, gpm 6500 Entering Air Temp., °F 80 Heat Duty CCWout °F x 106 BTU/hr Point 1 85 20 Point 2 130 218

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept

-354 X Variable 1 4.4 Flow, gpm 6500 Entering Air Temp., °F 90 Heat Duty CCWout °F x 106 BTU/hr Point 1 95 20 Point 2 130 174

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept

-398 X Variable 1 4.4 Flow, gpm 6500 Entering Air Temp., 'F 102 Heat Duty CCWout °F x 106 BTU/hr Point 1 105 20 Point 2 130 130

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept

-442 X Variable 1 4.4 Flow, gpm 7500 Entering Air Temp., °F 80 Heat Duty CCWout °F x 106 BTU/hr Point 1 85 20 Point 2 130 200

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept

-320 X Variable 1 4.0 Flow, gpm 7500 Entering Air Temp., 'F 90 Heat Duty CCWout 'F x 106 BTU/hr Point 1 100 32 Point 2 120 110

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept

-360 X Variable 1 4.0 Flow, gpm 7500 Entering Air Temp., 'F 102 Heat Duty CCWout 'F x 106 BTU/hr Point 1 105 12 Point 2 130 112

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept

-408 X Variable 1 4.0 WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Attachment 7.1 Page 2 of 2 Wet Cooling Tower Performance Curves -Regression Analysis Ref. Zurn ASME Performance Curves Flow, gpm Range, 'F 5000 10.8 Point 1 Point 2

SUMMARY

OUTPUT Twb, 'F ACCWout, 'F 75 81.5 85 88.75 Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Flow, gpm 5000 Range, *F 21.6 Twb, 'F ACCWout, 'F Point 1 75 84.75 Point 2 85 91.5

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept 34.125 X Variable 1 40.675 Flow, gpm 5000 Range, 'F 27 Twb, 'F ACCWout, 'F Point 1 75 86.75 Point 2 85 92.75

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept 41.75 X Variable 1 0.6 Intercept X Variable 1 27.125 0.725 Flow, gpm 5750 Range, 'F 10.8 Twb, °F ACCWout, 'F Point 1 75 82.25 Point 2 85 90

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept 24.125 X Variable 1 0.775 Flow, gpm 5750 Range, °F 21.6 Twb, 'F ACCWout, 'F Point 1 75 87 Point 2 85 93

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept 42 X Variable 1 0.6 Flow, gpm 5750 Range, °F 27 Twb, 'F ACCWout, 'F Point 1 75 88.25 Point 2 85 94

SUMMARY

OUTPUT Regression Statistics Multiple R 1 R Square 1 Adjusted R Square 65535 Standard Error 0 Observations 2 Coefficients Intercept 45.125 X Variable 1 0.575 WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Attachment 7.2 Page 1 of 6 STER -5.04 Shell and Tube Heat Exchanger Rating Program Copyright 1995 by Holtec International.

Description:

CCW Heat Exchangers This report was created Monday, November 07, 2005 at 1:03:03 PM EQUIPMENT CONFIGURATION PARAMETER Number of Shells in Series/Parallel:

Shell Type: Bundle Type: Shell Inside Diameter [inches]: Number of Tube Passes: Baffle Type: Baffle Cut [% of shell ID]: Central Baffle Spacing [inches]: Number of Tubes [holes in tubesheet]:

Number of Tubes Plugged: Inlet Baffle Spacing [inches]: Outlet Baffle Spacing [inches]: Number of Pairs of Sealing Strips VALUE QA REF 1/1 TEMA E FIXED 45.000 1 NTIW 21.11 92.000 1276 63 114.000 114.000 0 3/3 1 1 1 1 5 2 1 Tube Outside Diameter [inches]:

0.7500 Tube Wall Thickness

[inches]:

0.0280 Tube Material:

304 Stainless Thermal Conductivity

[Btu/hr/ft/F]:

8.70 Tube Layout Angle [degrees]:

30 Tube Layout Pitch [inches]:

0.9375 Effective Tube Length [feet]: 42.000 Flow Orientation:

Counter-Current Tube Nozzle Inlet Diameter [inches]:

20.000 Tube Nozzle Outlet Diameter [inches]:

20.000 Shell Nozzle Inlet Diameter [inches]:

16.000 Shell Nozzle Outlet Diameter [inches]:

16.000 Integral Low Fin Tubes: NO 1 1 1 1 1 2 1 1 1 1

Description:

CCW Heat Exchangers This report was created Monday, November 07, 2005 at 1:03:03 PM PARAMETER VALUE QA REF Shell to Bundle Clearance

[inches]:

1.0000 4 Shell to Baffle Clearance

[inches]:

0.3750 5 Tube to Baffle Clearance

[inches]:

0.0156 2 Shell Inlet Annular Distributor:

NO Shell Outlet Annular Distributor:

NO Number of Baffles per Unit: 4 2 Impingement Plate Dist. [% nozzle dia]: 64.84 2 Omit Tubes at Inlet [% shell dia]: 23.05 Omit Tubes at Outlet [% shell dia]: 0.00

WATERFORD 3 DESIGN ECM95-008 Rev. 3 dhENGINEERING Attachment 7.2 Page 3 of 6 STER -5.04 Shell and Tube Heat Exchanger Rating Program Copyright 1995 by Holtec International.

Description:

CCW Heat Exchangers This report was created Monday, November 07, 2005 at 1:03:03 PM***** QA REFERENCES QA REF REFERENCE SOURCE DESCRIPTION 1 Struthers Wells Data Sheet Located in 457000087 2 5817-10750 Rev. 0 3 5817-10751 Rev. 0 4 5817-10747 Rev. 0 5 Fax from Merl Rice of Struthers dated 3/2/94* An Asterisk denotes values determined by the program.

Description:

CCW Heat Exchangers This report was created Monday, November 07, 2005 at 1:03:03 PM PERFORMANCE TEST MODE RESULTS TEST ID: 102/78 DATE: 11-07-05 PROCEDURE:

EC-M95-008 CONVERGENCE TOLERANCE:

0.05 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: Volume Flow Rate [gpm]: Inlet Temperature

[degrees F]: Outlet Temperature

[degrees F]: Fouling Factor [1/Btu/hr/sqft/F]:

Operating Pressure [psig]: Heat Transfer Coeff [Btu/hr/sqft/F]:

Pressure Drop [psi]: Velocity [ft/sec]: Reynolds Number: 3396.78 6882.58 131.11 115.00 0.00000 0.00 1302.72 3.07 4.80 47325 2237.68 4490.71 89.30 113.77 0.00159 0.00 838.20 3.24 14021 Total Heat Duty: 54,635,891 Btu/hr Log Mean Temperature Difference:

21.25 F Overall Heat Transfer Coefficient:

257.09 Btu/hr/sqft/F Corrected LMTD: 21.25 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: Density [Ibm/cu.ft]:

Specific Heat Capacity [Btu/Ibm F]: Thermal Conductivity

[Btu/hr ft F]: Absolute Viscosity

[cP]: WARNING 1: Central Baffle Spacing 123.055 101.535 61.666 61.979 0.998 0.998 0.372 0.364 0.539 0.669 May Exceed TEMA Maximum.

Description:

CCW Heat Exchangers This report was created Monday, November 07, 2005 at 1:04:21 PM PERFORMANCE TEST MODE RESULTS TEST ID: 102/78 DATE: 11-07-05 PROCEDURE:

EC-M95-008 CONVERGENCE TOLERANCE:

0.05 %PARAMETER Mass Flow Rate [1000 Ibm/hr]: Volume Flow Rate [gpm]: Inlet Temperature

[degrees F]: Outlet Temperature

[degrees F]: Fouling Factor [1/Btu/hr/sqft/F]:

Operating Pressure [psig]: Heat Transfer Coeff [Btu/hr/sqft/F]:

Pressure Drop [psi]: Velocity [ft/sec]: Reynolds Number: TUBE SIDE SHELL SIDE 3396.78 6882.58 131.11 115.00 0.00000 0.00 1302.13 3.07 4.80 47325 2237.68 4490.15 88.60 113.07 0.00172 0.00 836.51 3.24 13916 Total Heat Duty: 54,635,441 Btu/hr Log Mean Temperature Difference:

21.96 F Overall Heat Transfer Coefficient:

248.79 Btu/hr/sqft/F Corrected LMTD: 21.96 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: 123.055 Density [Ibm/cu.ft]:

61.666 Specific Heat Capacity [Btu/Ibm F]: 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.372 Absolute Viscosity

[cP]: 0.539 WARNING 1: Central Baffle Spacing May Exceed 100.835 61.988 0.998 0.364 0.674 TEMA Maximum.

Description:

CCW Heat Exchangers This report was created Monday, November 07, 2005 at 1:05:17 PM PERFORMANCE TEST MODE RESULTS TEST ID: 98/83 DATE: 11-07-05 PROCEDURE:

EC-M95-008 CONVERGENCE TOLERANCE:

0.05 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: Volume Flow Rate [gpm]: Inlet Temperature

[degrees F]: Outlet Temperature

[degrees F]: Fouling Factor [1/Btu/hr/sqft/F]:

Operating Pressure [psig]: Heat Transfer Coeff [Btu/hr/sqft/F]:

Pressure Drop [psi]: Velocity [ft/sec]: Reynolds Number: 3396.78 6878.42 128.90 115.00 0.00000 0.00 1296.93 3.07 4.80 46834 2237.68 4492.12 91.03 112.14 0.00197 0.00 837.64 3.24 14029 Total Heat Duty: 47,139,080 Btu/hr Log Mean Temperature Difference:

20.15 F Overall Heat Transfer Coefficient:

233.90 Btu/hr/sqft/F Corrected LMTD: 20.15 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: Density [Ibm/cu.ft]:

Specific Heat Capacity [Btu/Ibm F]: Thermal Conductivity

[Btu/hr ft F]: Absolute Viscosity

[cP]: WARNING 1: Central Baffle Spacing 121.950 101.586 61.684 61.978 0.998 0.998 0.372 0.364 0.544 0.668 May Exceed TEMA Maximum.

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Attachment 7.3 Page 1 of 7 Equivalent Meteorological Conditions for the Ultimate Heat Sink to Dissipate the Design Basis Heat Load 105 Design Conditions:

1) Heat Duty 173.1 x 106 BTU/hr 2) CCWout = 115'F 3) All DCT and WCT Fans 78°Fw b / 102°Fdb Operating L100 E CD I-.0 ~ ~ ~ ~ 3F ---------

F b 98*F~db-95 O Since the wet bulb temperature can not exceed dry bulb temperature, __-the UHS can reject the design basis heat load for any dry bulb-temperature bellow this point, regardless of wet bulb temperature.

---zJ ill 84.9°Fw b / 91.3°Fdb 90 1 70 72 74 76 78 80 82 84 86 88 90 92 94 96 Wet Bulb Temp. (OF)Note: The 102°Fdb / 78 0 FWb point does not fall on the curve as may be expected.

This is due to the methodology discussed in section 5.4 and implemented in 6.4.1. The WCT basin temperature would be maintained cooler than the temperature specified in Technical Specification 3/4.7.4, assuming the design basis meteorological condition of 102 0 Fdb / 78 0 Fwb.DCT CCWHx WCT Dry Heat Heat CCWH heat Wet Bulb Rejected DCT Rejected x Rejected WCT Bulb Temp. (x 106 CCWout (x 106 ACCWin (x 106 Range Temp.(OF) BTU/Hr) (°F) BTU/Hr) (°F)* BTU/Hr) (LF) (OF)105 107.75 132.78 60.25 86.70 65.35 24.61 73.91 103 111.50 131.67 56.50 88.47 61.60 23.20 77.42 100 117.14 130.01 50.86 91.12 55.96 21.08 82.48 98 120.89 128.90 47.11 92.89 52.21 19.66 85.78 95 126.52 127.24 41.48 95.54 46.58 17.54 90.47 93 130.28 126.13 37.72 97.31 42.82 16.13 93.44*Calculated using STER Version 5.04. Printouts included in Attachment

Description:

CCW Heat Exchangers This report was created Tuesday, November 08, 2005 at 7:06:40 AM PERFORMANCE PREDICTION MODE RESULTS CASE ID: Met105 DATE: 11-08-05 PROCEDURE:

EC-M95-008 CONVERGENCE TOLERANCE:

0.01 %PARAMETER Mass Flow Rate [1000 Ibm/hr]: Volume Flow Rate [gpm]: Inlet Temperature

[degrees F]: Outlet Temperature

[degrees F]: Fouling Factor [1/Btu/hr/sqft/F]:

Operating Pressure [psig]: Heat Transfer Coeff [Btu/hr/sqft/F]:

Pressure Drop [psi]: Velocity [ft/sec]: Reynolds Number: TUBE SIDE SHELL SIDE 3396.78 6885.48 132.78 115.00 0.00000 110.00 1314.88 3.05 4.80 47688 2237.68 4488.56 86.70 113.71 0.00159 60.00 841.14 3.24 13821 Total Heat Duty: 60,286,041 Btu/hr Log Mean Temperature Difference:

23.38 F Overall Heat Transfer Coefficient:

257.77 Btu/hr/sqft/F Corrected LMTD: 23.38 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: Density [Ibm/cu.ft]:

Specific Heat Capacity [Btu/Ibm F]: Thermal Conductivity

[Btu/hr ft F]: Absolute Viscosity

[cP]: WARNING 1: Central Baffle Spacing 123.888 100.204 61.673 62.007 0.998 0.998 0.373 0.364 0.535 0.678 May Exceed TEMA Maximum.

Description:

CCW Heat Exchangers This report was created Tuesday, November 08, 2005 at 7:07:40 AM***** PERFORMANCE PREDICTION MODE RESULTS CASE ID: Met103 DATE: 11-08-05 PROCEDURE:

EC-M95-008 CONVERGENCE TOLERANCE:

0.01 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: 3396.78 2237.68 Volume Flow Rate [gpm]: 6883.35 4489.94 Inlet Temperature

[degrees F]: 131.67 88.47 Outlet Temperature

[degrees F]: 115.00 113.79 Fouling Factor [1/Btu/hr/sqft/F]:

0.00000 0.00159 Operating Pressure [psig]: 110.00 60.00 Heat Transfer Coeff [Btu/hr/sqft/F]:

1312.22 842.71 Pressure Drop [psi]: 3.05 3.24 Velocity [ft/sec]:

4.80 Reynolds Number: 47441 13960 Total Heat Duty: 56,530,060 Btu/hr Log Mean Temperature Difference:

21.92 F Overall Heat Transfer Coefficient:

257.81 Btu/hr/sqft/F Corrected LMTD: 21.92 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: 123.333 101.128 Density [Ibm/cu.ft]:

61.682 61.995 Specific Heat Capacity [Btu/Ibm F]: 0.998 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.373 0.364 Absolute Viscosity

[cP]: 0.537 0.672 WARNING 1: Central Baffle Spacing May Exceed TEMA Maximum.

Description:

CCW Heat Exchangers This report was created Tuesday, November 08, 2005 at 7:20:40 AM PERFORMANCE PREDICTION MODE RESULTS CASE ID: Met100 DATE: 11-08-05 PROCEDURE:

EC-M95-008 CONVERGENCE TOLERANCE:

0.01 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: Volume Flow Rate [gpm]: Inlet Temperature

[degrees F]: Outlet Temperature

[degrees F]: Fouling Factor [1/Btu/hr/sqft/F]:

Operating Pressure [psig]: Heat Transfer Coeff [Btu/hr/sqft/F]:

Pressure Drop [psi]: Velocity [ft/sec]: Reynolds Number: 3396.78 6880.21 130.01 115.00 0.00000 110.00 1308.25 3.05 4.80 47073 2237.68 4492.08 91.12 113.92 0.00159 60.00 845.07 3.24 14170 Total Heat Duty: 50,888,081 Btu/hr Log Mean Temperature Difference:

19.73 F Overall Heat Transfer Coefficient:

257.87 Btu/hr/sqft/F Corrected LMTD: 19.73 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: Density [Ibm/cu.ft]:

Specific Heat Capacity [Btu/Ibm F]: Thermal Conductivity

[Btu/hr ft F]: Absolute Viscosity

[cP]: WARNING 1: Central Baffle Spacing 122.505 102.520 61.695 61.977 0.998 0.998 0.372 0.365 0.542 0.662 May Exceed TEMA Maximum.

Description:

CCW Heat Exchangers This report was created Tuesday, November 08, 2005 at 7:23:27 AM***** PERFORMANCE PREDICTION MODE RESULTS CASE ID: Met98 DATE: 11-08-05 PROCEDURE:

EC-M95-008 CONVERGENCE TOLERANCE:

0.01 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: 3396.78 2237.68 Volume Flow Rate [gpm]: 6878.13 4493.56 Inlet Temperature

[degrees F]: 128.90 92.89 Outlet Temperature

[degrees F]: 115.00 114.00 Fouling Factor [1/Btu/hr/sqft/F]:

0.00000 0.00159 Operating Pressure [psig]: 110.00 60.00 Heat Transfer Coeff [Btu/hr/sqft/F]:

1305.59 846.62 Pressure Drop [psi]: 3.05 3.24 Velocity [ft/sec]:

4.80 Reynolds Number: 46827 14310 Total Heat Duty: 47,124,352 Btu/hr Log Mean Temperature Difference:

18.27 F Overall Heat Transfer Coefficient:

257.90 Btu/hr/sqft/F Corrected LMTD: 18.27 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: 121.949 103.445 Density [Ibm/cu.ft]:

61.704 61.965 Specific Heat Capacity [Btu/Ibm F]: 0.998 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.372 0.365 Absolute Viscosity

[cP]: 0.545 0.655 WARNING 1: Central Baffle Spacing May Exceed TEMA Maximum.

Description:

CCW Heat Exchangers This report was created Tuesday, November 08, 2005 at 7:26:44 AM***** PERFORMANCE PREDICTION MODE RESULTS CASE ID: Met95 DATE: 11-08-05 PROCEDURE:

EC-M95-008 CONVERGENCE TOLERANCE:

0.01 %PARAMETER Mass Flow Rate [1000 Ibm/hr]: Volume Flow Rate [gpm]: Inlet Temperature

[degrees F]: Outlet Temperature

[degrees F]: Fouling Factor [1/Btu/hr/sqft/F]:

Operating Pressure [psig]: Heat Transfer Coeff [Btu/hr/sqft/F]:

Pressure Drop [psi]: Velocity [ft/sec]: Reynolds Number: TUBE SIDE SHELL SIDE 3396.78 6875.05 127.24 115.00 0.00000 110.00 1301.61 3.06 4.80 46461 2237.68 4495.84 95.54 114.12 0.00159 60.00 848.94 3.24 14520 Total Heat Duty: 41,493,912 Btu/hr Log Mean Temperature Difference:

16.08 F Overall Heat Transfer Coefficient:

257.95 Btu/hr/sqft/F Corrected LMTD: 16.08 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: Density [Ibm/cu.ft]:

Specific Heat Capacity [Btu/Ibm F]: Thermal Conductivity

[Btu/hr ft F]: Absolute Viscosity

[cP]: WARNING 1: Central Baffle Spacing 121.120 104.830 61.717 61.946 0.998 0.998 0.372 0.365 0.549 0.646 May Exceed TEMA Maximum.

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Attachment 7.3 Page 7 of 7 STER -5.04 **********

Description:

CCW Heat Exchangers This report was created Tuesday, November 08, 2005 at 7:28:06 AM***** PERFORMANCE PREDICTION MODE RESULTS CASE ID: Met93 DATE: 11-08-05 PROCEDURE:

EC-M95-008 CONVERGENCE TOLERANCE:

0.01 %PARAMETER Mass Flow Rate [1000 Ibm/hr]: Volume Flow Rate [gpm]: Inlet Temperature

[degrees F]: Outlet Temperature

[degrees F]: Fouling Factor [1/Btu/hr/sqft/F]:

Operating Pressure [psig]: Heat Transfer Coeff [Btu/hr/sqft/F]:

Pressure Drop [psi]: Velocity [ft/sec]: Reynolds Number: TUBE SIDE SHELL SIDE 3396.78 2237.68 6873.01 4497.41 126.13 97.31 115.00 114.21 0.00000 0.00159 110.00 60.00 1298.94 850.49 3.06 3.24 4.80 46216 14662 Total Heat Duty: 37,726,460 Btu/hr Log Mean Temperature Difference:

14.62 F Overall Heat Transfer Coefficient:

257.98 Btu/hr/sqft/F Corrected LMTD: 14.62 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: Density [Ibm/cu.ft]:

Specific Heat Capacity [Btu/lbm F]: Thermal Conductivity

[Btu/hr ft F]: Absolute Viscosity

[cP]: WARNING 1: Central Baffle Spacing 120.565 105.755 61.726 61.934 0.998 0.998 0.372 0.366 0.552 0.640 May Exceed TEMA Maximum.

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Attachment 7.4.,--_--I Pagel of 9 Recirculation Effect on Dry & wet Cooling Towers During development of the ultimate heat sink design basis, 1.9 0 F was added to the drybulb temperature and 1.0°F was added to the wetbulb temperature to account for interaction (recirculation) between the dry cooling tower / wet cooling tower and their surroundings.

This attachment serves to show that these values are reasonable and conservative.

Recirculation Effect on Dry Cooling Tower PEIR OM-111 (pages 3 through 7 of this attachment) provides drybulb and wetbulb temperatures recorded at the dry and wet cooling towers against the outdoor ambient temperatures recorded at the Met Tower. The PEIR records drybulb and wetbulb temperatures at 6 different locations near the dry and wet cooling towers for 5 consecutive days in June 1996. Readings were taken once per day for various fans operating and not operating.

Since this discussion involves recirculation with fans operating, only the data with fans operating is relevant.

Thirty drybulb and wetbulb temperatures were recorded.The drybulb temperature results show that 26 drybulb temperature readings or 86.7% of the total (=26/30x100) were either equal to or less than the temperatures recorded at the Met Tower. Since the temperatures recorded at the dry and wet cooling towers are less than or equal to the ambient temperature, no effects of recirculation (warm air discharging from the cooling towers that makes its way into the suction of the cooling towers) are present.Three readings or 10% of the 30 total readings were 1IF over the temperature recorded at the Met Tower. Note that these are still less than the drybulb temperature value of 1.9 0 F. The highest reading over the ambient temperature, 2 0 F, was only recorded once or 3.3% of the 30 total readings.

This is within 1/10 of 1IF of the drybulb temperature value. Since this temperature is within 1/10 of IVF and was only recorded once, the drybulb temperature value of 1.9 0 F is considered an acceptable value.Recirculation Effect on Wet Cooling Tower The wetbulb temperature results show that 22 wetbulb temperature readings or 73.3% (=22/30x1

00) were either equal to or less than the temperatures recorded at the Met Tower. Thus showing no effects of recirculation.

Six readings or 20%were 1IF over the temperature recorded at the Met tower. Since the wetbulb temperature recirculation value is 1IF, 93.3% (=73.3%+20%)

of the readings are equal to or less than the wetbulb temperature parameter of 1 0 F. The highest reading, 2 0 F over the ambient temperature recorded at the Met Tower, was WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Attachment 7.4--,- __--_Page 2 of 9 recorded twice or 6.7% of the total readings.

The highest recorded value is within 1IF of the wet bulb value. Since the highest recorded reading is within 1 OF of the wetbulb value and was recorded only twice, the wetbulb value of 1.0°F is considered reasonable.

A paper of the Cooling Tower Institute entitled "Recommended Recirculation Allowances" (pages 8 and 9 of this attachment) describes how to determine design wetbulb temperatures.

The method is carried out below for the following data from this calculation, EC-M95-008 Rev. 1: ACCW accident flow rate 5350 gpm ACCW temperature leaving wet cooling tower 89.3 OF Design wetbulb temperature 78 OF Calculated approach temperature (89.3-78) 11.3 OF Wet cooling tower inlet temperature 111.0 OF 9 Wet cooling tower range 22.49 OF First, determine the design uncorrected recirculation value using the curve for average maximum recirculation.

At 5350 gpm, uncorrected recirculation value is 0.5°F. Second, correct for the actual approach and range. Conservatively take the range.to be 30°F and the approach to be 121F, then the correction factor is 1.49. Third, multiply the uncorrected recirculation value by the correction factor to obtain the actual recirculation value which is 0.751F (=0.5'F x 1.49). This calculated value is within the wetbulb temperature of 1OF. As a result, the use of the 1OF wetbulb temperature is considered acceptable value.Conclusion The present values of 1.9 0 F for the drybulb temperature and 1.0°F for the wetbulb temperature are reasonable and acceptable.

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Attachment 7.4 aPage 3 of 9 EinUMm PAGE 1 of 1 , 4 (REQUEST (RESPONSE TOTAL NUMBER OF ATTACHMENT PROBLEM EVALUATION

/ INFORMATION REQUEST No. O \- If I PRIORITY CODE: _T_ RESPONSE REQUIRED BY: 8/15/96 TO: _5,t- ..... -; -L.l- ./8116 -FROM: _ Operations GROUP/DEPARTMENT GROUP/DEPARTMENT SUPPORT RESPONSE Rick Williams 3290 0O: GROUP/DEPARTMENT ORIGINATOR (PRINT NAME) PHONE FROM: OPS SYSTEM: ACC PRINT NAME GROUP/DEPT

REFERENCES:

DUE DATE: PROBLEM/ REQUEST : Operations requests to know if the dry and wet bulb temperatures as read from the met towers is sufficient to use in determining ultimate heat sink fan requirements.

If not, where should the temperatures be taken and what type of instrument should be used.AUTHORIZED BY: ive tw DATE: RESPONSE ASSIGNED e6 -F_.E-t DATE: 1f- 7-6'RESPONSE: F_-F- AT-AME-NT-PREPARED BY I DATE:W 8-]!7 REVIEWED BY / DATE ://,,,I 1 j-%Y(p APPROVED BY / DAT .RESPONSE ACCEPTABLE:

DATE: ._2-7-5_DISTRIBUTION:

R RESP. DISTRIBUTION:

REQ. RESP.X (ORIG)RECORDS CENTER TRAINING MANAGER DBD PROGRAM MGR. (ALL TECH PEIRS) NUC. SAFETY & REG. AFFAIRS MANAGER NOEC MGR. NUC. PURCH. & CONTRACTS MANAGER NUC. PLANT OPERATIONS MANAGER M JAGEMENT SYSTEMS MANAGER NOSA MGR.-- Ai -ys__NUC. SERVICES MANAGER r .-:Lif NUC. GA MANAGER ONTROLLER (0 NOEC. !P. STAFF) & PARAGRAPH 5.2.3.1 PEIR NO.: OM-III PAGE I OF 3 PEIR CONTINUATION SHEET m PROBLEM/REQUEST CONT' D. [] RESPONSE CONT' D 1. STATEMENT OF PROBLEM/INFORMATION REQUEST Are dry and wet bulb temperatures as read from the met tower sufficient to use in determining UHS fan requirements?

If not, where should the temperatures be taken and what type of instrument should be used?11. RESULTS AND CONCLUSIONS Measuring temperatures in the Dry Cooling Tower (DCT) and Wet Cooling Tower (WCT) areas will not provide reliable readings to use for Technical Specification compliance.

The Met tower will provide the average temperature of ambient air that would be seen entering the UHS during design accident conditions.

Also, temperatures recorded at the Met tower are not affected by the configuration the UHS fans may be operating in during normal operations.

Therefore, ambient temperatures recorded at the Met tower should be used for Technical Specification compliance.

Ill. REFERENCES CR# 96-0975 Calculation EC-M95-008; Ultimate Heat Sink Design Basis Calculation EC-M95-009; UHS Fan Requirements Under Various Ambient Conditions Calculation MN(Q)-9-52; UHS Performance FSAR Section 9.2.5; Ultimate Heat Sink FSAR Table 2.3-2(a);

UHS Meteorological Design Parameters Technical Specification 3/4.7.4 Ultimate Heat Sink W3-DBD-004:

Component Cooling Water Auxiliary Component Cooling Water IV. ASSUMPTIONS None W5 I2,Rv 0 Attchmen tIl (Pg 2of2 W5.602, Rev. 0 Attachment II (Page 2 of 2)

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Attachment 7.4 ENGNEEINGPage 5 of 9-orY PEIR NO.: OM-III 2 PAGE 2 OF 3 PEIR CONTINUATION SHEET[-- PROBLEM/REQUEST CONT' D. EE RESPONSE CONT' D V. DISCUSSIONS/DETAILS

Background

The design basis of the UHS uses the most limiting coincident ambient conditions of 102 °Fdb 1 78 °Fb and 98 °Fdb / 83 °Fb. These temperatures were obtained from readings taken over a 30 year time period at the New Orleans airport. During development of the UHS design basis, 1.0 OF was added to the wet bulb and 1.9 OF was added to the dry bulb, to account for interaction (recirculation) between the WCT / DCT and their surroundings.

These temperatures were used to establish UHS capacity, and are assumed to bound various combinations of ambient conditions that may exist over the plants operational life. Technical Specification table 3.7-3 was developed to maintain the design basis UHS capacity with various combinations of WCT and DCT fans out of service. On June 26, 1996 CR# 96-0975 was written when temperature readings taken in the DCT area indicated 95 OF dry bulb, and temperatures taken in the WCT area indicated 84 OF wet bulb.Evaluation The UHS is designed for DBA heat loads, and assumes all fans, required by Technical Specification table 3.7-3 to be operable, are running in fast speed. During normal operations plant heat load is much lower than DBA loads, and the number of UHS fans running depends on current ambient conditions.

This can create various configurations of UHS fans actually running. Each one of these configurations alters the environment surrounding the UHS in a different way, and causes local temperature readings to vary depending on the location they are taken and what fans are operating.

This effect is illustrated in attachment

1. Temperatures recorded on attachment 1 were taken on five different days, at various locations, and with DCT/WCT fans operating in different configurations.

Measuring temperatures in the DCT and WCT areas will not provide reliable readings to use for Technical Specification compliance.

The Met tower will provide the average temperature of ambient air that would be seen entering the UHS during design accident conditions.

Also, temperatures recorded at the Met tower are not affected by the configuration the UHS fans may be operating in during normal operations.

Any slight variation between temperatures recorded at the Met tower and at the inlet to the UHS, are either captured by the recirculation effect considered in the UHS design basis or within existing UHS margins.W560, ev I Itahet I(ae f2 W5.602, Rev. 0 Attachment II (Paqe 2 of 2) a WATERFORD 3 DESIGN ENGINEERING ECM95-008 Rev. 3 Attachment 7.4 Page 6 of 9 PEIR NO.: OM-111 PAGE 3 OF 3 PEIR CONTINUATION SHEET j PROBLEM/REQUEST CONT'D. RESPONSE CONT'D Vl. FAILURE MODE AND EFFECTS ANALYSIS Not Required VII. NUCLEAR SAFETY SIGNIFICANCE None VIII. RECOMMENDATIONS/FURTHER ACTIONS Design Engineering recommends that Operations use the Met tower to record ambient temperatures for Technical Specification Compliance.

The Met tower will currently provide a one hour average dry bulb temperature shown on PMC point C48558. By September 30, 1996 the Met tower will be able to provide a 1 hour1.157407e-5 days 2.777778e-4 hours 1.653439e-6 weeks 3.805e-7 months average wet bulb shown on PMC point C48560.IX. ATTACHMENTS 1.0 UHS Ambient Temperatures "5.... Re. 0*tahetI Pg 2.of.2.W5.602, Rev. 0 Attachment Il (Page 2 of 2)

U t-ký Ntl E. NA<V -ThrMi EK kU LSs OCr F?!j! FAST tm 1 lrimms, LDCT Fans Off_V~TFn AST tot 14.) trigi.DCTaif OCT Vanb FAST kx 10Mias act (in rALwof Fagsm OCT East Lp ows OCT East Up DCT EsstUp B63J M(A N79 UCT Ee4*1 0~1w WS7 0Cl East Down L)CT W~sI U.)Fan mwolr 7 pct YiýSt up DCT WounUp F.an M400( 7 T W F U~DCT @4Cm N~A DCl WWI'tOw Pa~n mioI 9 O)CTWBit Down Fan motix 9 ITW&Ll Down Fan9173 East WCT MAtfa VXT Ou*~d Doa 61 it Lsw4a~ l g wo O78 -¶likW Ow 6 1 Ist tandair off Qdock LEIbACT Wtu3l WCT Dossido IDnrn &I ISM Lamwing olfC~tka East VOT WQ;A W--O Mw' w IiiI 3 ~ dd M"M Taw.t M4I VeAG Idsk)924100 9 Mitt Twe MIo Towo.MCI 14uisu Mot To3 IMct 04ta tob)Po PC405 11 MIA Dalm (03i)mot Data (dIb)Fai n gru~ 9 fastm 'oto 7 OCT East Ommt WlfT VMsl Lk 8W3~o9 fnmti T ECM95-008 Rev.3 WATERFORD 3 DESIGN ACM ent 7 ENGINEERING Attachment 7.4_--_ _ _ _ I _ Page 8 of 9 BflFATr COOQIu; TOWER INSTUTE RECOMMENDED RECIRCULATION ALLOWANCES SupPlemIenting the text a' -he CrI Technical Sub-Cooismttaz

2 repnrt on the stury of "Rec..ireulaliun" fCTI Bulletin PFM-110).

in watearcoalitig tewers hai heaen defined as "an adulhcrat-on n!the atmophere, entering the tower by a portion of the atmospheret eaving the tower." This adulteration by the exhaust air t aCse h6d wet bulb tnmperacure of the entering air above chat of die ambientc tir7-reducing the rnwer over-all poflcemance, In 19M8 the. Cooling Tower Inslituce published its Bulletin PFM.110 entitled"Recireulat!eV" which presected the rc-ptiues of a seven year rhidy ýi the rectiu-lation charaeorix;tic-a of counterflow and Crnsflc.'w xiechaceieal draft watcr-enolinu

Qwer3.The of the work indicated that ciruolation was predominantly o flin.,9t oa. Lower length. Acttmpti to incluie other varltbles auvh ga htarrm height, atack height, tower width, exit velocity or inlet velocity did not reveal any ni end in inffcencn.g the reeirculation or im-prove the correlation.

The equation pub.liahed, In which maxienum cireulation Is given 0s a function of tower length only, represents th, experimental data adequute.ly for both coitterfinw andinduced draft toaeral.Maximum rec;.culation, like maximum wet bulb tempcratare, occur. only- a por.tion of the time And to design a tower for sch ma-xiniuco conditions is not gener.ally e0conoenically justilied.

F rt.her, prepcr aricrrarinn of the tower with pre.vaiiing winds con usually be caunted upon 0n reduce the incidence of mnximurn reeirculaticn iinct prevailing w;nin and.iigh we" hulb remperatures frequcetly occur cimaItaneoi),,lv.

A review of the late published indicos the average re.Cor thels imterred in. the subjeiz, a onm.Aptte d0,eun fan ao the data is pree-td in R.7l Bdle:i. ' A. 4ppendix oMnian.ite sumMry ahi.tit and pureJ7cell data is alta nasUcttc.circulation to he approximately CO per cnt of the maximn for the towcrs in'eluded in the stdy. 'lisle allowance Ls fr moat operating conditions and is recommended by the Cooling Towor Innhitute in soctring or desi.gnin eomntetflow ar iduced dralt ceolicg tewetr, With rhe publication of reliable reeir.culation data it is now possibc for the purclmcr to .pee'ly a design inlet wIvt bulb temperature rimply by adding to the epprepriste amihent wet bulb tem.p.rarure tie recommended recireulation in dcgrees F for the specified conditions of pi.rformanrnt The epcceilatlon of a desin' inlet nie: bulb temperaturn corrected for remrc:,-lade6, it. lieu of an anfBient wet bulb teeuperatnre, provide, an adequate r6cir-tulatinn allowance and further makes possiblo performarie testing without aerting. 'jarent ennling tnwera or cech h.a-use of their effect on the inlet we:. bulb tcnperatuare of the tower or cell being testcd.T he curves Fpotted On the reverse of thisl shese show wet bulb temperotura cor-rection for mnaximlum renireulation and recotucnded reeircaion elewettces, bse~sd nn 6o per cent of mox-imum, far waIef Rows up to 100f.000 gprn. A tahle of corrtct!on factors for various rangas and appronehes it alsec preenelcd.

H1OW TO sFT.sCT DESIGN INLET WE'7T' BULn TEMPERLA'I'EE The desgn inlet wee bulb teemper-ture is obtalncd by addine a recrculndon al.]oA.nr. exrtessed in cLeg. F, to the am-Iient wet bulb temperseture

.,rtcted for the mea in which &h coolhng tower wnill be located.Example 1. Seect a der.ign inlet ecet bulb temperature far a tower required to cool 4l0,000 gpm from 112 F to 89. F when the area an:bicnt wet bulb otemper.awre is 75 F. From the curve, the rectai.mended recireulation allowance at 40,000 olpr ii 1.2 F, Fromts the Correction Factor Tbhle, the orreectien ftaor for a range of 30 F and an aproach of 7 F is 1..The recommended recirculation, allow.ante will be 1.2 F X 1.25 = 1.5 F. The design inlet wet hulb ttmperature is 75 F + 1.5 F -76.5 F. The tower should be prec."ied and designed to cool 40,000 ,pm fhom [IV. F to 82 F at a dealgn in-let wet bulb temperstute of 76,5 F."xampls 2. Axume .bove tower has been Installed and a 102000 epm eact.,!on it dre-ired.

The reeireulation allaw-cute fer the extecsion should be haste an Ite combined water flow of 50,000 gpts at thclapecti-id rnge ,ad approach.In this ease the recircclation alluwance will he 1.37 F X 1.25 -1.1 F. The cx-tenaion should 'Lat be speLifed andl de-szigned to cool 10,000 gpm from 112 F tu 82 F at a dmi,-n inlet wet bulb tempera.turs of 76,7 F.If the Conlin,! ramgc and op.proech for the toiere extensinn differ from the original then the couluig range end approach which pro.duce the hiher rerire:flaton allowasce chalid be iwed.Se1cetian of an ininc wet bulb tc¢mpora-ture for a tower t ruower e.trngian in the vicinity of oth-.r celing :swer% rbould he Mada in the sattue manne. mi gi-cr. in Example-s I and 2 above. however, the ambient wet buib tcraperaturc upcn which the inlet ietl xalb tcrpereture i7 to her baed !hould be stleeterl to provide fer the effect of A4.iphborin-rooling towr.9 on the site choreu.

WATERFORD 3 DESIGN ECM95-008 Rev. 3 ENGINEERING Attachment 7.4 Page 9 of 9-G R~COMMCNDID

ýCI(2CULATION ALLOWANCES r 'Oft COUNTERF1 OW AND CUSqFtO~W N01JCED 0P.AF-, COOLIN4G TQWGRS wc 4: 3 2 Ih J.: T.- V AVERAGE, MAXIMUM R CRUATION L Ii- + I _I I. .. .-F I 7 --7 4ýI __ I I-Li I L.1~ ~~H i--r i it+/-LLi+/- E i Li~ECOMMENOED RECIRCIULA-i0NLLOWANc Et-wt I I I rffl j 0 10 20 30 40 so WATER FLOW, IN 1030 (i,'m 60 70 PC 90 100 NCT9. R-ifrudation lauo AN-MTh(, UrVV nhAY4 OriA.d ,na20 F auuvlng ange~ anldI To r 'apparoh ir1 any -at W3ib loftpMauto.

1aci~rruLarion allow-andez, Jar vrhar purformonoce COM-ditinns Can be. u6tainad bY flewitS 0E thn Cdo A-iiOIt Pactafs 16-11.!rsiir foarA-1riiar 7nsitu-.tiara,.0. r-.Vrs. .f thl. Al.., to Ao-0."t CORRECTION FACTORS Rlrng2. 2 F 5-TO 15 20 25 30 5s 40 45 No 5 7 S 0.21 0.31 n.J3 0,35 0.37 0,47 0.49 0.61'0.53 0.55 0.64 OMD 0.71 0.74 0.7h 0.80 0,93 0.97 0.611 I .03 1.74 1.20 I .250 1.30 1.3s 1.30 1.37 1.44 1.56 1.47 1,16 1.70 1,11 1 1.73 1.83 1.91 1.97 1 .S0 1.90 2.01 2.10 2.19 10 12 13 0.'39 0.41 0.43 0.45 0,46 0,57 0.59 0.63 0.,5 0.78 0,01 O.R4 0.86 0168 1.00 1.04 1.07 1.13 19 17 21 22 23 24 25 0.47 0.67 0.90 1.15 0.49 0.1A ,9 A 0.s1 0.70 0..95 1.20 0,,2 0.72 0-.97 1.22 0.l3 0.74 0,99 1.24.S4 0,75 1,00 1.26 0.M5 0.77 1.02 1,23 0.56 0.79 1,04 1.30 0.57 0.90 1,05 1,31 0,58 0.1 1.06 1.37 0.N. 0.82 1.07 1.33 1,7,0 1.40 I.A? 1.83 2.64 2.25 1.74 1.45 1.66 1,B3 2.09 2.31 1.27 1.44 1.70 1.92 2.11 2.36 1.20 1.52 1.74 1.96 2.17 2.40 1.33 1.56 1,77 1.99 2.21 2.,44 1,36 1.57 1.50 2.02 2.25 2,47 1.37 t.61 1.23 2.06 2,29 2.52 1.!2 I.6 1.06 2.10 2.33 2,57 1.46 1.6t 1.92 2.16 2.40 2.64 1.48 1.70 1.95 2.. 2.57 1.50 1.71 1,98 2.22 2.46 2.70 1.12 1.7/ Z,0 2.25 2.49 2.73 1.5 .2.0' '.77 2.52 2.14v 1.56 1.80 2.04 2.29 2.4 2,79 1,57 l.e2 7.06 2,31 2.56 2.81 I 03.3 220-jjjj rT ,I ......1111 Il.. ý i trn lh44 1 IIII!I IJI'.l Il 4ff 21IT El A w.14 ai Ii'22 66.46.S40.01 20.(200 4 18o ui ii!pilfdi!"i, MMUH-1-101

'4f In R? fli! All -, "I I pi V-11.IH K iIM. -I.,II tt 7 too ~.pi; 2Il-' i 40 ~.~~; j! 2 in Till.' IF! 113 l9i I ANY UIPM111111 11 g IM"N"Y'Le it~ A~fi 122 44 LI 141m0 £ l~ ..24 H!i i*M !.:Ft;nil7 I I -i+i ;4"=

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~~i~tI 66ý.30 40 50 60 70 80 9g0 OO 110 120 130 140 1SO WATER TEMPIERAtuRE BASIS'I COOLING WATER FLOW RATE -6000 GPM.160 170 30.. 40.50o ..M0 s0o 90.. 0oo. 420 120, 130 140_ 15O IGO I?, I.EAVING 0ftY COOLING TOWER. IF NOTES COMPONENT COOLING WATER SYSTEM LOCA. OPERATING MODE IACCIDENT CONDITION)

RWOSON PRODUCIs, CORPOILAT,101`

INTERMAL ,PERFORMANCF.

DRY COOLING TOWER LOVISAIW pow(A a L16wT.: MOL'ANV IIIASCO SKAVICKI M'-"DN5 1 -0 NY-4034 r9 IIX)2(? ISK $A I SIT-TP-250 PERFORMNCE CURVES FOR DRY TOWER ECM95-008 Attachment 7.5 Page 1 of 3 Revision 0 1715II 24OP AII~ Ii.I ;aaa~i2a2,I222~:24mlaN2ua2222,, **242,

2..~h~¶I1W~64.22o .. ....200 U,~ j 2..d Iil 554 irlSO w.a434 ýWI40'69 2.41 00... .. ....):!.!7 I)$:7 I-Ut Wý..l .14 .1 I:ii: r i][i ii]!i Hiilit I I --WIM11M F;: IF~i IA Ii'1:l;;a;t.:;: g a RE 2!a2 2 12 1 tp~.:a:2JI

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Illi 3,0 .40 .50 60 70 00 0 .100 210 120 130.140 ,150 .16a0. 170 %0 40 50 60 TO 80 90. Ii 0X 0 ..li0 IO. 130 440 i50 (0 ITrO WATER TEMPERATURE LEAVING DRY COOLING TO*EI ,IU~bNPROUCS CORPORATION 1,100001%

RXAZ OASIS.,'*-.. / ,/ '/,\I COOLING WATER FLOW, RATE .6500 GPM.NOTES .COMPONENT COOLING WATER $YSIEEM LOCA OPERATING dMODE (ACCIDENT CONDITION I THERMAL PERFORMANCE DRY COOLING TOWER"UAIqFoftO StatION -oftI 2. 3 LOUISAqA rQWKR 6 L2,2HT COMPA-4-[IIASCG .IVImvcCS mC I*2t* -22*222 mai"."25 .'7 I... 403.17 ND002ISk IB I 5 SIT-TP-250 PERFORMANCE CURVES FOR DRY TOWER ECM95-008 Attachment 7.5 Revision 0 Page 2 of 3 640 53.3 400 53Z3 113 S32.0 Is.21.3 16.0 230..... ... .. ......h 1r%I:, I'Lwu*mIFA 1 I2 I Ji liii

!lqF!ll;: lQ!il!l I:i'I.AR; .21. A! " !,,..,.-.]..

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q *K121 116 .~HUDSOf4 PRODUCTS COEPONATION HO1102 04. RIA BASIS I COOLING WATER rLOW RATE -7300 GPM NOTES COMPONENT COOLING WATER SYSTEM LOCA, OPERATING MODE IACCIDENT CONDITION

)"~'THERMAL PERFORMANCE DRY COOLING TOWER PON WATERFORD 128,2014.

UNIT No0 I 1850C ftriit 101C14 a~ 1 19 , c 75.41 L NY- 403479 ND002 j SK IC SIT-TP-250 PERFORMANCE CURVES FOR DRY TOWER ECM95-008 Attachment 7.5 Page 3 of 3 Revision 0 ATTACHMENT 9.2 ENGINEERING CALCULATION COVER PAGE Sheet 1 of 2 Ml ANO-1 El ANO-2 El GGNS [] IP-2 El IP-3 El PLP El JAF EPNPS ERBS EVY [W3 E] NP-GGNS-3

[] NP-RBS-3 CALCULATION (1) EC # 8465 (2)Page 1 of 42 COVER PAGE (3) Design Basis Calc. M YES I-I NO (4) r- CALCULATION Z EC Markup"5) Calculation No: ECM95-008 Revision:

3 (7) Title: Ultimate Heat Sink Design Basis -Editorial:

[-] YES Z NO (9) System(s):

ACC, CC (10) Review Org (Department):

(11) Safety Class: (12) Component/Equipment/Structure Type/Number:

, Z Safety / Quality Related ACCMPMPOO01A I- Augmented Quality Program CC MPMPOOI-A M] Non-Safety Related CC MPMP001-AB ACCMPMP010B CC MPMP001-B ACCMTWR0001A (13) Document Type: CC MHX0001A ACCMTWR0001B (14) Keywords (Description/Topical CC MHX0001B Codes): RSG, 3716 MWt, EPU, Ultimate CC MTWR0001A Heat Sink, UHS, ACCW, CCW, WCT, DCT, Cooling Tower CC MTWR0001 B REVIEWS (15) Name/Signature/Date (16) Name/Sianature/Date (17) Name/lignature/D t N/A -,/i/i/ Joe Reese Responsible Engineer [] Design Verifier Sup isor/Approval

[ Reviewer[_ Comments Attached El C mments Attached EN-DC-126 REV 2 ATTACHMENT 9.2 ENGINEERING CALCULATION COVER PAGE Sheet I of 2 El ANO-1 [3 ANO-2 [I GGNS L] IP-2 El iP-3 r PLP[I JAF QPNPS 0 RBS 0 VY 0 W3 NP-GGNS-3

[] NP-RBS-3 CALCULATION (1) EC # 8465 (2 Page I of 41 COVER PAGE (3) Design Basis Cabc. 0 YES EL NO (4) El CALCULATION

[ EC Markup Calculation No: ECM95-008 Revision:

3 Title: Ultimate Heat Sink Design Basis Editorial:

[I YES Z NO System(s):

ACC, CC (10) Review Org (Department):

111) Safety Class: ( Component/Equipment/Structure TypelNumber:___________

[ Safety I Quality Related I Augmented Quality Program CC MPMPOO01-A ACCMPMPOOOIA E] Non-Safety Related CC MPMPOO01-AB ACCMPMPOOOIB CC MPMPI0001 -B ACCMTWROOO1A (13) Document Type: B13.18 CC MHX0001A ACCMTWROOOIB (14) Keywords (DescriptionlTopical CC MHX0001EB Codes): RSG, 3716 MWt, EPU, Ultimate CC MTWR0001A Heat Sink, UHS, ACCW, CCW, WCT, DCT, Cooling Tower CC MTWR0001B REVIEWS (15) Name/Signature/Date

16) Na/ISi at re/Date (17) Name/SignaturelDate Jacob Regiser a .o Ed Brouwer (Westinghouse) (Westinghouse) (Westinghouse)

Responsible Engineer [ Design Verifier SupervisorlApproval I Reviewer I Comments Attached EI Comments Attached EN-DC-126 REV 2 ATTACHMENT 9.3 CALCULATION REFERENCE SHEET Sheet 1 of 3 CALCULATION CALCULATION NO: ECM95-008 REFERENCE SHEET REVISION:

3 I. EC Markups Incorporated (N/A to NP calculations)

1. None 2.I1. Relationships:

Sht Rev Input Output Impact Tracking Doc Doc Y/N No.R1. MN(Q)9-52, Ultimate Heat 1 2 D N Sink Performance R2. MN(Q)9-3, Ultimate Heat 1 4 z -N Sink StudyI R3. 9C2-5Y, Chillers Heat 1 1 t] [ N Rejections R8. ECS-05-013, UHS 1 1 -N Containment Heat Loads R10. MN(Q)9-65, CCW 1 2 X z Y EC-8465 Temperature Evaluation.

R22. ECM95-009, Ultimate 1 2 zI Y EC-8465 Heat Sink Fan Requirements Ill. CROSS

REFERENCES:

1. None.2.3.IV. SOFTWARE USED: Title: STER Version/Release:

Version 5.04 by Holtec, W3 Software Manual 460000024 Vol.Title: Microsoft Excel Version/Release:

2002 Disk/CD No. N/A 1 V. DISKICDS INCLUDED: Title: N/A Version/Release:

Disk/CD No.VI. OTHER CHANGES: None EN-DC-126 REV 2 ATTACHMENT 9.4 RECORD OF REVISION Sheet i of 1 i Reviisio n. Reco~rd of Re'vision Initial issue.0 0 -1 Determine equivalent meteorological conditions that UHS can reject the design basis heat load.CR 970777 documented that the containment heat loads for the UHS did not contain certain conservative assumptions.

The purpose of this calculation 0 -2 change is to revise the UHS design bases requirements corresponding to maximum containment heat load rate determined by calculation MN(Q)93.This is a complete rewrite; therefore no revision bars are used.Provides justification for use of hot air recirculation values and adds computation of the ACCW System design temperature in response to the recommended dispositions of Design Basis Review Open Items: OICCW296Cand OICCW297C.

Adds Keywords to Section 3. Replaces Reference 3.3 and removes references to the FSAR. Corrects typographical

...... errors. This is a complete rewrite; therefore no revision bars are used.Modified UHS Design Basis as a result of Total Heat Duty input changes at 3716 MWt. A methodology change was made in section 5.4 to ensure Tech Spec 3/4.7.4 compliance.

Calculation and Attachment changes have been made accordingly.

Added page 2 of 2 to Attachment 7.3 to include the regression analysis for the DCT. This analysis was referenced in section 6.1.1 of the calculation.

Section 6.6.4 was added to address Met tower DRN conditions from Calculation ECM03007 (Ref. R22).03-509 The basis for the heat load from emergency diesel generators and the LPSI/HPSI/CS pumps in circular.

Calculation ECM95-008 references calculation MNQ9-3 for this heat load and MNQ9-3 references ECM95-008 for the same heat load. ECM95-008 now references Calculation MNQ9-65 which develops the basis for these heat loads.DRN 05- Added Assumption 4.7 to clarify that containment heat loads were determined 766 assuming 112 0 F CCW temperature (ECS01-005).

This revision incorporated all outstanding changes and DRNs. ECS05-013 was changed to the new input for containment heat loading and all calculations were revised accordingly.

CR-WF3-2005-0230 documented that 2 the CCW flows used in the calc did not bound the As-Built flows determined during flow testing. The CCW accident flow has been increased to a bounding6900 gpm.EN-DC-126 REV 2 Corrected transposition errors in paragraphs 5.3 and 5.4, math operator in paragraph 6.3.1, and copy and paste error in Attachment 7.1, identified on 3 CR-WF3-2007-1420.

The errors did not affect the results of the calculation.

Therefore, this is an administrative change only.This EC Markup addresses the impact of Replacement Steam Generators EC-8465 (RSGs) on this calculation.

Changes are incorporated on pages 1 -3, 11- 22, Attachment 7.2:4 -6, Attachment 7.3: 1 -7, Attachment 7.4: 2.EN-DC-126 REV 2 WATERFORD 3 DESIGN ECM95- 008 Rev. 3 ENGINEERING Page 1 of 24 1.0 PURPOSE 1.1 The purpose of this calculation is to determine the Ultimate Heat Sink design basis under LOCA conditions using the worst combination meteorological design parameters.

1.2 This calculation also determines the ACCW System design temperature.

Co g-( I. w LU Ch ~ ~ & 0ý b WATERFORD 3 DESIGN ECM95- 008 Rev. 3 B ENGINEERING Page 2 of 24

2.0 CONCLUSION

2.1 The UHS is capable of dissipating the LOCA heat duty requirements for both worst combination meteorological design parameters, 102'F db/78'F wb and 98'F db/8 3 1 wb. The 102'F db/78'F wb meteorological condition would allow less fouling in the CCW heat exchanger in order to maintain a CCW outlet temperature of 115'F, therefore is chosen as the UHS design point. The design conditions for the UHS are given below.Dry Bulb Temperature (Tdb) -1027 Wet Bulb Temperature (Twb) 78F DCT CCW Inlet Temperature

-X d, b 44 DCT CCW Outlet/CCWHx Inlet Temp.DCT Heat Duty r WCT ACCW Outlet/CCWHx Inlet Temp. -89.3F*CCWHx CCW Outlet Temperature

-115.0'F CCWHx ACCW Outlet Temperature -LO.0 CCWHx Allowable Fouling Factor CCWHx Heat Duty (f64-S2-x 1 BT r WCT ACCW Inlet Temperature

\ ' LU WCT Heat Duty B r WCT Cooling Range*As discussed in section 5.4, these values are calculated using an ACCW inlet temperature to the CCWHx of 89.3 0 F in order to maintain the Tech. Spec.maximum ACCW temperature of 89 0 F.As discussed in section 6.6.4, the meteorological condition of 91.3°Fdd84.9 0 Fwb from Reference R11 is not more limiting than 102*Fdb/7 8 0 Fwb case above.2.2 Using the limiting historical meteorological parameter, 102'F db/781F wb, a relationship (See Attachment 7.3) was developed to provide equivalent dry bulb temperature/corresponding wet bulb temperature required to maintain overall UHS design heat duty capacity.

The linear relationship demonstrates that for a dry bulb temperature increase/decrease of 1.0 0 F, the corresponding wet bulb temperature can decrease/increase approximately 1.7 0 F and maintain the UHS design heat duty capacity.

The relationship also demonstrates the UHS can dissipate its design heat load for any dry bulb temperature below 93 0 F, regardless of wet bulb temperature, since wet bulb temperature can not exceed dry bulb temperature.

2.3 ACCW System design temperature is 125 0 F.

WATERFORD 3 DESIGN ECM95- 008 Rev. 3 B ENGINEERING Page 3 of 24 3.0 IN PUT CRITERIA 3.1 Peak UHS Heat Duty Iqeuirement Containment Heat Du) = x 106 BTU/hr (Ref. RB)Essential Chiller Heat Duty =5.1 x106 BTU/hr (Ref. R3)Auxiliary Heat Duty = 10.0 x 106 BTU/hr (Ref. R10)Total Heat Duty 1;3=1,,-4-84x 106 BTU/hr CCWS Heat Duty 3T 108 BTU/hr Notes: 1.

l d' 't" ha bo round'" UP ,;fr IV'! 1 "2 j @ ) .g t6 "r'l I F A W ,, R OR r- r -A ncludes Diesel 6enerator and HPSI, LPSI and Containment Spray pumps ...0?U]3.2 Maximum One Hour Ambient Conditions Drybulb Temperature Ref. Cl contains a table which shows the maximum drybulb and concurrent wetbulb for the New Orleans area is 102 and 77F= respectively.

One degree is added to the wetbulb temperature for conservatism bringing the maximum 1 hour1.157407e-5 days 2.777778e-4 hours 1.653439e-6 weeks 3.805e-7 months drybulb/corresponding wetbulb temperatures to 102/78cF.Wetbulb Temperature Ref. Cl discusses that 837F is the maximum wetbulb temperature of record at Moisant Field for the period between 1946 and 1977. The reference discusses that 83F is an acceptable design value and satisfies the requirements of Reg.Guide 1.27. A table attached to the reference provides maximum wetbulb and corresponding drybulb temperatures however, 831F is not an entry in the table.An entry is provided for 831F in the table for maximum drybulb and corresponding wetbulb temperatures.

Based on this evaluation, at 831=wetbulb temperature, the corresponding drybulb temperature is 98F.The site Met Tower data was evaluated in calculation Reference R1 1 over a period from 1997 to 2001. This review indicates that the maximum one hour wetbulb temperature exceeded 83'F at 84.9cF with an associated drybulb temperature of 91.27TF. This calculation will determine if the 84.9F wb/9 1.3cF db met condition is more limiting for the highest Twb and coincident Tdb case.3.3 Maintain a CCW outlet temperature of 11 5F to the plant auxiliaries. (Ref. R4)

T WATERFORD 3 DESIGN ECM95- 008 Rev. 3 ENGINEERING Page 11 of 24 6.2 Dry Cooling Tower Performance 6.2.1 DCT Performance at Tdb = 1027 Determine DCT inlet temperature Q = mcp(Tin -or Tin = (Q/mcp) + Tout where 1lM Tin = DCJ/Inlet Temperature (TF)Q = 1-e x 108 BTU/Hr (less Chiller Heat Duty) (Input 3.1 O m = 6900 gpm x 60 min/hr / 0.016293 ft'/Ibm / 7.4805 gal/ft3.0= 3.39678 x 106 Ibm/hr Tout = 1157 @ CCW Heat Exchanger U Cp = 0.998 BTU/Ibm -'F U.-1-,T.* --x 6/ 3.39678 x 108

0.998)) + 115 The CCWoLt temperature at the DCT can be calculated using the conservation of energy where: QocT = mcp(TI, -T!t)This heat balance will be performed to calculate the DCT Tout temperature at DCT performance curve inlet CCW flows of 6500 gpm and 7500 gpm and then interpolated at the CCW accident design flow of 6900 gpm.Q6500gpm = 4.4*Tot -(354 + 4.4 (lb -80)) = mi;(Tin -Tut) (Sec. 6.1.1)where: Q6500 = Heat Transferred

@ CCW Flow of 6500 gpm Tout = CCWo= temperature Tdb = 103.9"F (adding 1.9'F for Recirculation) (Input. 3.2, 3.7)m = 6500 gpm x 60 min/hr / 0.016293 ft 3/lbm / 7.4805 gal/ft= 3.200 x 106 Ibm/hr cp = 0.998 BTU/Ibm -'F Tin ,='Solving for Tout yields 4.4*Tout + mcpT 0 ut = (354 + 4.4 (Tdb -80)) + mqTi'4.4*T,,t + (3.200)(0.998)To

= 354 + 4.4(103.9-

80) +-11200)(0.998)*

T~t =0ý-67 W WATERFORD 3 DESIGN ECM95- 008 Rev. 3 SENGINEERING Page 12 of 24 Calculating Heat Transferred:

Q 6 5 oo = mcp(Tin -Tt) 164g6 It Q6500 = (3.200 (0.998)Q6500 = X10 'BT-7 -r .,W Performing Heat Balance at a CCW Flow Rate of 7500 gpm: Q7500gpm = 4.0*Tot -(320 + 4.0('b -80)) = m;(TIn -Tt) (Sec. 6.1.1)where: Q7500 = Heat Transferred

@ CCW Flow of 7500 gpm T 0 ut = CCWout Temperature Td = 103.9'F (adding 1.9'F for Recirculation) (Input 3.2, 3.7)m = 7500 gpm x 60 min/hr / 0.016293 ft 3 / Ibm / 7.4805 gal/ft 3= 3.692 X 106 Ibm/hrC0 Cp = 0.998 BTU/Ibm, -'F 0?Tin Solving for yields: 4.0*To= + mcpTout = (320 + 4.0(Tdb -80)) + mnTi, 4.0*Tout + (3.692)(0.998)Tout

= 320 + 4.0(103.9-

80) +,3 692) (0.998)*Calculating

--eat Transferred:

Q7500 = mcp(Tin -Tt rl(b2 Q7500 = 62 (0.998)(64

-eJ-Q75wo-ta ((106 BTU7R`F By linear interpolation, the DCT heat duty @ 6900 gpm is: Q6900 gpm = 0Q,,16500 pm + 6900- 6500* (Q7500 gm- Q 5 0 0 gpm) ..7500- 650 Q 6 9 0 0 gpM 106 + (0.4)ftt&<2101

-;1t-T72f*10

6) 'Q6900gpm : 106 BTU/Hr 20-11 I, Calculating CCWout Temperature:

m = 3.39678 x 106 Ibm/hr= 0.998 BTU/Ib, -'F Tim~~- (0/rn. ..T out -* 6 -.(1, .3 8 967818 '^,',.,J,, .)ot 0~ =P-4 "ý '9 0 WATERFORD 3 DESIGN ECM95- 008 Rev. 3 ENGINEERING Page 13 of 24 6.2.2 DCT Performance at Tdb = 98F The method of analysis for the DCT performance at a dry bulb temperature of 981 is identical to the analysis given 6.2.1.Q6s5ogpm = 4.4*Tot -(354 + 4.4('Gb -80)) = mg(Tin -T~t)where: Qe 5 0 o = Heat Transferred

@ CCW Flow of 6500 gpm Tout = CCWot Temperature Tdb = 99.9F (adding 11.97F for Recirculation) m = 3.200 Ibm/hr (x 106) (6500 gpm)Cp .= n098 BTU/Ibm -'F Tin f Solving for Tgo.t yieUlds (Sec. 6.1.1)(Input 3.2, 3.7)4.4*Tout + mcpT1t = (354 + 4.4 (Tdb -80)) + mTi," 4.4*Tot t 00)(0.998)To., = 354 + 4.4(99.9-

80) + (3.200)(0.998)

Calculating Heat Transferred:

Qm= mcp(Tin -Tt Q6500 =

Pe650n Heat B tU/Hr Performing Heat Balance at a CCW Flow Rate of 7500 gpm: U')LL0 W0 Q7500opm = 4.0*Tout -(320 + 4.0(lb -80)) = mg(Tin -"ut)where: Q 7 5 0 0 = Heat Transferred

@ CCW Flow of 7500 gpm Tout = CCWOl Temperature Tdb = 99.9cF (adding 11.97 for Recirculation) m = 3.692 Ibm/hr (x 106) (7500 gpm)Cp = TU/llbm -F Tin Solving for Tout yields:+ mcpTo.t = (320 + 4.0(Tdb -80)) + mqTi, 4.0*Tot + (3.692)(0.998)To

=a2Q + 4.0(99.9-

80) +3.692)(0.998)646&--

Tout tro t. ro?(Sec. 6.1.1)(Input 3.2, 3.7)to LO (0 0?w WATERFORD 3 DESIGN ECM95- 008 Rev. 3 ENGINEERING Page 14 of 24 LO (0 Calculating Heat Transf.e 141 Q75= mcp(Tin -Q75oo = (3.6692)(0.998)'-6uJJ W Q7soo 24-&Mx10 6 B By linear interpolation, the DCT heat duty @ 6900 gpm is: Q 6 9 0 0 pm= Q 6 5 oo gpm + 6900- 6500 *(Q 7 5 0 0 gpm- Q500 PM)7500- 65 , _0 LO CC Q 6 0og oPM 106 + (o.4) 1o -1) 0 Q6900 gpm = 106 BTU/Hr 12V-7I3 u Calculating CC out Temperature:

m = 3.39678 x 106 Ibm/hr cp = 0.998 BTU/Ibm -'F C.u Tin-Tout 5a- -3.39678/0.998)oC To.ut r+ LU 6.3 Wet Cooling Tower Performance 6.3.1 WCT Performance at Tlb = 78F and Tdb = 102'F Determine WCT Heat Duty O I Qwc = Total Heat Duty- DCT Heat Dissipated

@ Tb of 102F. co QWC -x 10 6 -14+e3x 10" (Input 3.1, Sec. 6.2.1) I0 Q.d-f -106 BTU/Hr 0 Determine CT Cooling Range Qwct = mcp(AT) or AT = Qwctmcp where AT = Cooling Range (CF)m = 5350 gpm / 0.01613 ft 3/Ibm / 7.4805 gal/ft 3 x 60 min/hr=2.660 x 106 Ibm/hr cp =- 0.998 BTU/lbm -'F AT z 10 6/2.660 x 10 6/ 0.998 =,C'.0j Using a'2-49'aF WCT Cooling range an increasing Twb by 1.01 to account W for recirculation, the ACCW outlet temperature can be calculated, (Input 3.7)

WATERFORD 3 DESIGN ECM95- 008 Rev. 3 ENGINEERING Page 15 of 24 At 5000 gpm ACCW~t = '0.675- 0.0139 ,21.6))*79

+(34.125 + 1.412a 21.6))ACCWout = (Sec. 6.1.2)At 5750 gpm- 1 ACCWou = (- 0.00463 21.6))'79

+(42.00 + 0.5787 0.--21.6))

ACCWo U .(Sec. 6.1.2)By linear interpolation, the WCT heat duty @ 5350 gpm is: ACCWOUI 5350- 5000*L .- .O 5750- 5000 (ACCWoUt -( LU.ACCWoUt is le :an 89.0'F, therefore:

ACCWUt = 89.31F (for CCWHx analysis) (Sec. 5.4)WCT inlet Temperature WCTin = 89.3F i --6.3.2 WCT Performance at Twb = 83F and Tdb = 98¶F Determine WCT Heat Duty Q..t = Tot geatDuty-DC eat Dissipated

@ Ub of 98'F.Qct = x 10 -4 ..89- x 1l (Input. 3.1, Sec. 6.2.2) 0, Q=106 BTU/Hr Determine WCT Cooling Range Qwct = mcp(AT) or AT = Qwct/mcp Where: AT = Cooling Range (F)m = 5350 gpm / 0.01613 ft 3/Ibm I 7.4805 gai/ft 3 x 60 min/hr= 2.660 x 106 Ibm/hr Cp = 0.998 BTU/Ibm -'F LO AT1Ora/ 2.660x10 .998L 0?

WATERFORD 3 DESIGN ECM95- 008 Rev. 3_1_ ENGINEERING Page 16 of 24 Using a 19.66TF WCT Cooling range and increasing Twb by 1.0'F to account for recirculation, the ACCW outlet temperature can be calculated. (Input 3.7)(Sec. 6.1.2)(Sec. 6.1.2)U*)0?0 W gpm is: 6.4 CCW Heat Exchanger Performance 6.4.1 CCWHx Performance at Twb = 78'F and Tdh = 102cF Determine CCW H 9 uty QCCWHX = WCT Chiller eat Duty @ "b of 1027F. (Sec. 6.3.1)QccwHx =QX 106 -5.1 X 16 (input 3.1)QCCWHx .=46 106 BTU/Hr 57,g4 K As deteýn Section 6.3.1, the WCT ill return the ACCW flow back to the WCT basins at a temperature of .F in order to meet the Tech. Spec.Maximum WCT Basin Temperature Limit, the maximum allowable CCW heat exchanger fouling will be calculated using and ACCW inlet temperature of 89.3'F. The maximum allowable fouling is determined for an ACCW inlet temperature of 89.3cF, because the maximum allowable fouling is minimized at the higher ACCW inlet temperature.

10 (0?(0 6 Determine ACCWoUt Temperature QccwHx = mcp(Tout -Tn) or Tou = QCCWHx/mCp

+ Tin WATERFORD 3 DESIGN ECM95- 008 Rev. 3_--- ENGINEERING Page 17 of 24 where: m = 4500 gpm 1 7.4805 gal/ft3 /0.01613 ft3/Ibm

60 min/hr=2.238 x 106 Ibm/hr @ 897F p = 0.998 BTU/Ibm -'F Tin,19 3 (Sec. 6.3.1)Tout -10 6/2.238 x 10 6/0.998+89.3 Using ST Version 5.04, the following heat exchanger performance is calculated for a CCW,,t temperature of 1150F. The printouts are provided in Attachment 7.2 ICO (0 w CCW CCW 0 ut ACCWi, 115.0 89.3* Ated by STER Version 5.04 ACCW.Fouling Factor U-)(0 Nt 0?w Additionally, the ACCWout temperature will be calculated using the actual WCT outlet temperature (i.e. CCW heat exchanger inlet temperature).

ACCWIn ter p, rture calculated in Section 6.3.1.T =_106 (Sec. 6.3.1)Tout~ 106/2.238 x 10 6/0.998 Using STER Version 5.04, the following heat exchanger performance is calculated for a CCWout temperature of 1157F.L1 (0 00 1wL Fouling 6.4.2 CCWHx Performance at TWb = 83'F and Tjh = 98F Determine CCWH uty 55.43J QCCWHx = WC; Chier-eat Duty @ U of 981F.QCCWHx = &2-24-x 10 6 -5.1 x 1 QCCWHX =.ýx 106 BTU/Hr (610.,3 (Sec. 6.3.2)(Input 3.1)

WATERFORD 3 DESIGN ECM95- 008 Rev. 3 ENGINEERING Page 18 of 24 Determine ACCWout Temperature QCCWH, = mcp(To,, -T1) or Tout = QCCWHx/mCp

+ Tin where: m = 4500 gpm / 7.4805 gal/ft 3 / 0.01613 ft 3/Ibm

60 min/hr= 2.238 x 106 Ibm/hr cp = 0.998 BTU/Ibm -T: Tin ..1 ý,._(Sec. 6.3.2)Using STEFRVersion 5.04, the following heat exchanger performance is calculated for a CCWo~t temperature of 1157. The printouts are provided in Attachment 7.2 LO (0 0?uj* Calculated CCW 11 ACCW n-1 1 5 .0 .by STER Version 5.04 ACCW Fouling Factor VV# I, 9 WATERFORD 3 DESIGN ECM95- 008 Rev. 3____ ENGINEERING Page 19 of 24 6.5 Ultimate Heat Sink Design Points The worst case ambient condition for the UHS is a Tdb of 1027 and a Twb of 781F. This conclusion is based on the allowable fouling for the CCW heat exchanger to maintain a CCW outlet temperature of 11 5V is less under these ambient conditions.

The design points for the UHS are given below.Dry Bulb Temperature (Tdb)Wet Bulb Temperature (Tb)DCT CCW Inlet Temperature DCT CCW Outlet/CCWHx Inlet Temr DCT Heat Duty WCT ACCW Outlet/CCWHx Inlet Temperature CCWHx CCW Outlet Temperature CCWHx ACCW Outlet Temperature CCWHx Allowable Fouling Factor CCWHx Heat Duty WCT ACCW Inlet Temperature WCT Heat Duty WCT Cooling Range-102'F (Input 3.2)-3.2)-w Sec. 6.2.1)-~1I 0 Sec. 6.2.1)-1BTU/Hr (Sec. 6.2.1)-89.37F* (Sec. 6.3.1)LO (.0 0?.0*As discussed in section 5.4, these values are calculated using an ACCW inlet temperature to the CCWHx of 89.3 0 F in order to maintain the Tech. Spec.maximum ACCW temperature of 89.0°F.6.6 Maximum Twb at Various Tdb to Maintain Overall UHS Design Heat Duty Capacity.The most limiting historical ambient condition for the UHS was determined to be a Tdb of 102'F and a Twb of 781F. This analysis will determine equivalent meteorological conditions for the UHS to maintain its overall design heat duty capacity using the limiting fouling factor determined in the previous sections for the CCW heat exchanger.

6.6.1 DCT Performance at Tdb = 1057F The CCWot temperature at the DCT can be calculated using the conservation of energy where: QDCT = mcp(Ti, -Tt)Heat capacity of the DCT at a CCW flow rate of 6500 gpm is calculated using the equation:

WATERFORD 3 DESIGN ECM95- 008 Rev. 3 ENGINEERING Page 20 of 24 QOCT = 4.4*Tout -(354 + 4.4 (Cb -80)) (Sec. 6.1.1)Solving the two equations, the heat balance becomes at a CCW flow of 6500 gpm: 4.4*Tout-(354 + 4.4(lb -80)) = mg(Tin- "rut)where: T o u t = CCWout temperature Tdb = 106.9F (adding 1.97F for Recirculation) (Input 3.2, 3.7) LO m 3.200 Ibm/hr (x 106) (6500 gpm)Cp, = 0.998 BTU/Ib. -'F Tin (Sec. 6.2.1)Solving for Tout yields 4.4*Tout + mcpTout = (354 + 4.4 (Tdb -80)) + rnýTin 4.4*Tout + (3.200)(0.998)Tut

= 354 + 4.4(106.9-

80) +,-,_(3.200)(0.998)i6 Tou ,=tC7W?Calculating Heat Transferred:

(0 QDcT = mcp(Ti -Tot) .-V QDCT = 3.Q0(0.998)

L QDCT=e 106 BTU/Hr Heat capacity of the DCT at a CCW flow rate of 7500 gpm is calculated using the equation: QOCT = 4*Tot -(320 + 4 (*Eb -80)) (Sec. 6.1.1)Using the Conservation of Energy, the heat balance becomes at a CCW flow of 7500 gpm: 4*T,,t- (320 + 4('b -80)) = m$(Tin- Tut)where: Tout = CCWot temperature Tdb = 106.9F (adding 1.9F for Recirculation) (Input 3.2, 3.7)m = 3.692 Ibm/hr (x 106) (7500 gpm)p = .998 BTU/Ibm -F Q0A(Sec. 6.2.1)Solving for Tout yields L 4*To~t + mcpTo.t = (320 + 4(Td -80)) + m1Ti, WATERFORD 3 DESIGN ECM95- 008 Rev. 3__ ENGINEERING Page 21 of 24 4*To= + (3.692)(0.998)Tout

=_2D.+ 4(106.9- 80) +

}Calcula ng Fleat Transferred:

to QDCT = mcp(Tin -Tut) I QDCT = 536jJ(0.998)

LU QDCT 1 O 1031BT-U/r-By linear interpolation, the DCT heat duty @ 6900 gpm is: Q6900gpm = , + 6900- 6500* (Q75oo0 g- Q500 gpm)log9. 7500- 65, U" Q6900 gpm = 06 +(0.4)( 1~~0 6 .Q?61)Q60oogpm .1 BTU/Hr Ujj.h7 .T 19.06'?Calculating CCWout Temperature:

m = 3.39678 x 106 Ibm/hr c = 0.998 BTU/Ibm -'F t -=(Tom- Q ou. ("7-7q339678/0.998) 6.6.2 Required CCWHx Performance at Tdb = 1057 Determine CCW QCCWHx = Tot -D -Chiller Heat Duty to QCCWHx = X 106- x 1id- 5.1 x1A (Input 3.1, Sec. 6.6.1) J QCCWH. 10B TUIHr 0?Determine A CW(,t Temperature v Using STER Version 5.04, an ACCW inlet temperature oig Ps required to dissipate the above heat load. The printout is provided in Attachment 7.3 WATERFORD 3 DESIGN ECM95- 008 Rev. 3""__ ENGINEERING Page 22 of 24 6.6.3 Maximum Tw for a Tj Of 1057 Determine D t 11,t Duty Qw1t e t uty- DCT- eat Dissipated Qwct=.,;¶ 106 -1675 x 1 Qwct #106 BTU/H r DeterSee WCT Cooling Range (0 co LU a, (Input 3.1, Sec. 6.6.2)Qw-t = mc)(AT) or AT = Qwt/mcp where AT m cp= Cooling Range ('F)= 2.660 X 106 Ibm,/hr (5350 gpm)= 0.998 BTU/Ibm -'F in ACCW outlet temperature of 6--(Sec. 6.1.2)(Sec. 6.1.2)account for recirculation (and @(?a,D 0 w 5350 m ields: (Input 3.7)Twb 3505000 o 40 1.0 Twb 501 75S3 WATERFORD 3 DESIGN ENGINEERING ECM95- 008 Rev. 3 Attachment 7.2 Page 4 of 6 STER -eli and Tube Heat Exchanger Ratin rogram Copyrigh 95 by Holtec International.

All righ served.This computer code is lidated under Holtec International's

'2pgram.File"N me: WTFRDCCW.EQP Unit Na .CCMHX001A&B Unit DescriptiCCCW Heat Exchangers This report created Monday, November 07, 5 at 1:03:03 PM***** PERFO NC TEST MODE RESULTS *'*N'~'S TB TID: 102/78 Y DATE: :- 05 PROCEDU ýEC- M95- 008 CONVERGENC T-LERANCE:

0.05 %i'- PARAMETER TUBE SIDE SHELL SID Mass Flow Rate [1000 lbm/hr]: 3396.78 2237.68 Volume Flow Rate [gpm]: 6 .58 4490.71 t Temperature

[degrees F]: 131 89.30 Outle mperature

[degrees F]: 115.00 13.77 Fouling F r [1/Btu/hrlsqftlF]:

0.00000 .0. 9 Operating Pres e [psigl: 0.00 0.00 Heat Transfer Coe /hr/sqftlF]:

1302.72 838.20 Pressure Drop [psi]: 3.07 3.24 Velocity [ft/sec]: Reynolds Number: 47325 14021 Total tDuty: 54,635,8 tu/hr Log Mean erature Difference:

21.25 F S Overall Heat Tr er Coefficient:

257.09 Btu/hr/sqft/F Corrected LMTD: 21.25 F ( Effective Surface Area per 1I: 10002.93 sq ft P ence Temperature

[F]: 123.055 101.535 ( Densit m/cu.ft]:

6 61.979 Specific He apacity [Btu/Ibm F]: 0.998 0.998 Thermal Conduc [Btu/hr ft F]: 0.372 .364 WAbsolute Viscositral 0.539 0.S WARNING 1: Central Ba acing May Exceed TEMA Maximum.LOt LU C?K'/I'N I K V\~ ~...--'\N--

Description:

CCW Heat Exchangers This report was created Friday, October 23, 2009 at 12:28:43 PM S* * * *

PERFORMANCE TEST MODE RESULTS *** * *TEST ID: 102/78 DATE: 06-29-09 PROCEDURE:

ECM9S-008 CONVERGENCE TOLERANCE:

0.05 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 lbm/hrj: 3396.78 2237.68 Volume Flow Rate [gpm]: 6884.39 4490.71 inlet Temperature

[degrees F]: 132.06 89.30 Outlet Temperature

[degrees F]: 115.00 115.21 Fouling Factor [ I /Btu/hr/sqft/F]:

0.00000 0.00133 Operating Pressure [pslg]: 0.00 0.00 Heat Transfer Coeff [Btu/hr/sqft/F]:

1305.85 840.24 Pressure Drop [psi]: 3.06 3.24 Velocity [ft/sec];

4.8 I Reynolds Number: 47536 14130 Total Heat Duty: 57,859,131 Btu/hr Log Mean Temperature Difference:

20.96 F Overall Heat Transfer Coefficient:

275.95 Btu/hr/sqft/F Corrected LMTD: 20.96 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: 123.530 102.257 Density [Ibm/cu.ft]:

61.658 61.969 Specific Heat Capacity [Btu/Ibm F]: 0.999 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.372 0.364 Absolute Viscosity

[cP]: 0.536 0.664 WARN ING I: Central Baffle Spacing May Exceed TEMA Maximum.N->dhme4~ ~~?~ ~~1 I.O (0 cT LU

~ECM95- 008 Rev. 3 WATERFORD 3 DESIGN Acm ent 7 dhENGINEERING Attachment 7.2 Page 5 of 6 STER -.04 Shell a d Tube Heat Exchanger ating Program Copyright 199 Holtec International.

rights reserved.This computer code is va ated under Holtec Intern onal's QA progra I File Name: WTFRDCCW.EQP Unit Name. CMHX0001A&B Unit Descripti CCW Heat Exchangers This repo s created Monday, Novemb 07, 2005 at 1:04:21 PM PER RMANCE TEST MODE RE TS T ID: 102/78 DATE: 1-07-05 PROCED E: EC- M95- 008 LO CONVERGE E TOLERANCE:

0.05 %PARAMETER TUBE SIDE S LL SIDE W Mass Flow Rate [1000 Ibm/h 3396.78 2237.6-,, , Volume Flow Rate [gpm]: 6882.58 4490.15 In emperature

[degrees F]: 131.11 88.60 Outlet mperature

[degrees F]: 15.00 113.07 Fouling Fa r [1/Btu/hr/sqft/F]:

0. 00 0.00172 Operating Pre re [psig]: 0.0 0.00 Heat Transfer Co Btu/hr/sqft/F]:

1302.13 836.51 Pressure Drop [psi]: 3.07 .24 Velocity [ft/sec]:

4.80/ eynolds Number: 47325 13916 Total at Duty: 5 5,441 Btu/hr Log Mean mperature Difference:

6 F Overall Heat sfer Coefficient:

248.79 Btu sqft/F Corrected LMTD: 21.96 F Effective Surface Area r Shell: 10002.93 sq ft k ference Temperature

[F]: 123.055 100.83\. Den i,[Ibm/cu.ft]:

61.666 61.988 SSpecific at Capacity [Btu/lbm F]: 0.998 0.998 Thermal Con tivity [Btu/hr ft F]: 2 0.364 Absolute Viscosi P]: 0.53 0.674 WARNING 1: Centra ifie Spacing May Exceed MA Maximum.

B Unit

Description:

CCW Heat Exchangers This report was created Friday, October 23, 2009 at 12:30:06 PM* * ** PERFORMANCE TEST MODE RESULTS * * *TEST ID: 102/78 DATE: 06-29-09 PROCEDURE:

ECM95-008 CONVERGENCE TOLERANCE:

0.05 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: 3396.78 2237.68 Volume Flow Rate [gpm]: 6884.39 4490.41 Inlet Temperature

[degrees F]: 132.06 88.92 Outlet Temperature

[degrees F]: 11 5.00 114.83 Fouling Factor [ I /Btu/hr/sqft/F]:

0.00000 0.00139 Operating Pressure [psig]: 0.00 0.00 Heat Transfer Coeff [Btu/hr/sqft/F]:

1305.52 839.32 Pressure Drop fpsl]: 3.07 3.24 Velocity [ft/sec]:

4.81 Reynolds Number: 47536 14073 Total Heat Duty: 57,858,860 Btu/hr Log Mean Temperature Difference:

21.35 F Overall Heat Transfer Coefficient:

270.96 Btu/hrlsqft/F Corrected LMTD: 21.35 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: 123.530 101.877 Density [Ibm/cu.ft]:

61.658 61.974 Specific Heat Capacity [Btu/Ibm F]: 0.999 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.372 0.364 Absolute Viscosity

[cP]: 0.536 0.666 WARNING 1: Central Baffle Spacing May Exceed TEMA Maximum.iP&p /;.-ar t LO C.0?Q WATERFORD 3 DESIGN ENGINEERING ECM95- 008 Rev. 3 Attachment 7.2 Page 6 of 6..........-.

I This computer code is vali ted under Holtec Int File Na e: WTFRDCCW.EQP Unit Nam .CCMHX0001A&B Unit Descrip n: CCW Heat Exchangers SThis rep wascreated Monday, Nove*'*** RFORMANCE TEST MODE i/ TEST ID: 98/83 DATE: 11 05 SPR )CEDURE.'

EC- M95- 008 CONERGENCE TOLERANCE:

0.05 taARAMENC TUB T MODESH Mass Flow Rate ,000 Ibm/hr]: 3396.78 X.2 SVolume Flow Rate [ m]: 6878.42 Inlet Temperature

[deDes F]: 128.90 AOutlet Temperature

[deg1sF]:

115.00 1 ( Fouling Factor [llBtu/hr/sqft:

0.00000 0.,erating Pressure [psig]: 0.00 He Transfer Coeff [Btu/hr/sqft/F.

1296.93 8 Press e Drop [psi]: w "4 3.07 Velocity w aec]: 4 [ ].80 ReYnolds N bera : 4 34 1 Total Heat Duty: 47,139,080 Buhr Log Mean Temperatur Difference:

20.15 F Ovllg Transfer Cicient: 233.90 Btu/hr/sqft/F0 k."orrected LMTD: 20.15 F/ E ftive Surface Area per She , 10002.93 sq ft R eeraen emperature

[F]: 0121.950 1 Density [lb cu.ftJ: 1.684 6\ Specific Heat apacity [Btu/Ibm F]:. 8 Thermal Conducity

[Btu/hr ft F]: 0.37. C Absolute Viscosity se]: 0.544 ARNING 1: Centra D Spacing May Exceed T ting 11l ri(:ern(17, 2005 at 1 RESULTS **LL SI[237.68$92.12 12.0019 0.00 37.64 3.24 4029)1.586 1.978).998).364.668Max:05:17 PM/I- -K I to co LU'imum./)

Description:

CCW Heat Exchangers This report was created Friday, October 23, 2009 at 122:31:20 PM* *

PERFORMANCE TEST MODE RESULTS * ** *TEST ID: 98/83 DATE: 06-29-09 PROCEDURE:

ECM9S-008 CONVERGENCE TOLERANCE:

0.05 %PARAMETER TUBE SIDE SHELL SIDE-.------.-.

-.. ...........

....... ... ........ .° ... .Mass Flow Rate C 1000 Ibm/hr]: 3396.78 2237.68 Volume Flow Rate [gpmj. 6880.20 4492.39 Inlet Temperature

[degrees F]: 129.85 91.36 Outlet Temperature

[degrees F]: 115.00 1! 3.92 Fouling Factor [1 !/Btu/hr/sqft/F]:

0.00000 0.00158 Operating Pressure [psfg]: 0.00 0.00 Heat Transfer Coeff [Btu/hr/sqft/F]:

1300.34 840.47 Pressure Drop [psi]: 3.07 3.24 Velocity [ft/sec]:

4.80 Reynolds Number: 47045 14188 Total Heat Duty: 50,362,221 Btulhr Log Mean Temperature Difference-19.53 F Overall Heat Transfer Coefflclent:

257.75 Btu/hr/sqft/F Corrected LMTD: 19.53 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: 122.425 102.638 Density [Ibm/cu.ft]:

61.676 61.964 Specific Heat Capacity [Btu/Ibm F]: 0.998 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.372 0.364 Absolute Viscosity

[cPj: 0.542 0.661 WARNING 1: Central Ba file Spacing May Exceed TEMA Maximum.1140, ',~tL~mewk I?~e 4' C)~4*LO (0 0 uJ WATERFORD 3 DESIGN ECM95- 008 Rev. 3 WAT NERR3IGN Attachment 7.3 r ENGINEERING Page 1 of 7 Equivalent Meteorological Conditions for the Ultimate Heat Sink to Dissipate the Design Basis Heat Load Note: The 1021F db / 78, wb point does not fall on the curve as may be expected.

This is due to the methodology discussed in section 5.4 and implemented in 6.4.1. The WCT basin temperature would be maintained cooler than the temperature specified in Technical Specification 3/4.7.4, as ming the design basis meteorolo ical condition of 102'F db / 781F wb.LO 0?C-)w LO (0 I I*Calculated using STER Version 5.04. Printouts included in Attachment

.05 Since ~ ~ ~ ~ ~ ~ ~ ~ ~~3 the wet bulb tepeatr cans noOeceddyrulaemeatreing- 7/8Fdt49b w/931 70 72 74 76 78 80 82 84 86 88 90 92 94 96 Wet Bulb Temip. Deg. F LDry DGT OCT CCWHx CCWHx WCT WCT Wet Bulb Bulb Heat CCWout Heat ACCWin Heat Range Temp.Temp. Rejected (OF) Rejected (OF)* Rejected (OF) (OF)O(F) (x10A6 (X1 OA 6 (xlOI6 BTU/hr) BTU/hr) BTU/hr)'105 111.75 133.72 63.45 86.82 68.55 25.82 73.51 103 115.48 132.62 59.72 88.52 64.82 24.42 76.98 100 121.12 130.95 54.08 91.01 59.18 22.29 81.82 98 124.85 129.85 50.35 92.68 55.45 20.89 84.98 95 130.49 1128.18 144.71 95.18 149.81 118.76 89.56 93 1 134.22 127.08 140.98 196.86 146.08 17.36 19 2.4:6 WATERFORD 3 DESIGN ECM95- 008 Rev. 3 WAT NER 3INGN Attachment 7.3-ENGINEERING Page 2 of 7 STER -5.04 Shell and Tube Heat Exchanger Rating Program Copyright 1995 by Holtec International.

All rights reserved.This computer code is validated under Holtec International's QA pro am.File Na e: WTFRDCCW.EQP Unit Nam CCMHX0001A&B Unit Descri tion: COW Heat Exchangers Thi report was created Tuesday, November 08, 2005 t 7:06:40 AM PERFORMANCE PREDICTION MODE SULTS CASE ID: Met105 DATE: 11 05 PROCEDURE:

EC- M9 008 CONVERGENCE TOLE NCE: 0.01 %PARAMETER TUBE SI E SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: 33 .78 2237.68 Volume Flow Rate [gpm]: 6 5.48 4488.56 Inlet Temperature

[degrees F]: 32.78 86.70 , C, Outlet Temperature

[degrees F]: 115.00 113.71 't Fouling Factor [1/Btu/hr/sqft/F]:

0.00000 0.00159 , Operating Pressure [psig]: 110.00 60.00 W Heat Transfer Coeff [Btu/hr/sqft/]:

14.88 841.14 Pressure Drop [psi]: 05 3.24 Velocity [ft/sec]:

4.Reynolds Number: 476 13821 Total Heat Duty: 60,286,041 Bt /hr Log Mean Temperatu Difference:

23.38 F Overall Heat Trans r Coefficient:

257.77 Btu/hr/sq Corrected LMTD: 23.38 F Effective Surfac Area per Shell: 10002.93 sq ft \7'Reference T mperature IF]: 123.888 100. 4 Density [Ib cu.ft]: 61.673 62.00 Specific eat Capacity [Btu/Ibm F]: 0.998 0.998 Therm Conductivity

[Btu/hr ft F]: 0.373 0.364 Abs te Viscosity

[cP]: 0.535 0.678 W RNING 1: Central Baffle Spacing May Exceed TEMA Maximum.

- - r***k***STER-5.04*********

M m e F-, This computer code is validated under Holtec International's QA program. ._'I File Name: WTFRDCCW.EQP Unit Name: CCMHX0OOIA&TB Unit

Description:

CCW Heat Exchangers

)This report was created Tuesday, October 27, 2009 at 10: 13:41 AM* * * *

PERFORMANCE PREDICTION MODE RESULTS *****CASE ID: Metl05 DATE: 06-29-09 PROCEDURE:

ECM95-008

)CONVERGENCE TOLERANCE:

0.01 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 ibm/hr]: 3396.78 2237.68 Volume Flow Rate [gpm]: 6887.29 4488.65 Inlet Temperature

[degrees F]: 133.72 86.82 .O Outlet Temperature

[degrees F]: 114.98 115.28 " .0 Fouling Factor [ I IBtu/hr/sqft/F]:

0.00000 0.00133 cl Operating Pressure [psig]: 110.00 60.00 Heat Transfer Coeff [Btu/hr/sqftlF]:

1 317.06 842.84 Pressure Drop [psi]: 3.05 3.24 LLd Velocity [ft/sec]:

4.80 Reynolds Number: 47895 13948 Total Heat Duty: 63,522,381 Btu/hr Log Mean Temperature Difference:

22.96 F Overall Heat Transfer Coefficient:

276.58 Btu/hr/sqft/F Corrected LMTD: 22.96 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature IF]: 124.352 101.048 Density [Ibm/cu.ftj:

61.666 61.996 Specific Heat Capacity [Btu/Ibm F]: 0.998 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.373 0.364 Absolute Viscosity

[cP]: 0.532 0.672 WARNING I: Central Baffle Spacing May Exceed TEMA Maximum.

O 3ECM95- 008 Rev. 3 WATERFORD 3 DESIGN Attachment 7.3 a ENGINEERING Page 3 of 7 STER -5.04 **********

All rights reserved.This computer code is validated under Holtec International's QA pr ram.File Naa: WTFRDCCW.EQP Unit Nam CCMHX0001A&B Unit Descri ion: CCW Heat Exchangers This port was created Tuesday, November 08, 200 at 7:07:40 AM\P****PRFORMANCE PREDICTION MODE SULTS *CASE ID: Met103 DATE: 11 05 PROCEDURE:

EC- M95- 08 CONVERGENCE TOLERA CE: 0.01 %PARAMETER TUBES S- E SHELL SIDE Mass Flow Rate [1000 lbm/hr]: 33 .78 2237.68 Volume Flow Rate [gpm]: 6 83.35 4489.94 Inlet Temperature

[degrees F]: 131.67 88.47 Outlet Temperature

[degrees F]: 115.00 113.79 Fouling Factor [1IBtulhrlsqftlF]:

.00000 0.00159 Operating Pressure [psig]: 0.00 60.00 Heat Transfer Coeff [Btu/hr/sqft/

.13 .22 842.71 Pressure Drop [psi]: 3. 3.24 Velocity [ft/sec]:

4.80 Reynolds Number: 47441 13960 Total Heat Duty: 56,530,060 Btu/Log Mean Temperatu Difference:

21.92 F Overall Heat Tran r Coefficient:

257.81 Btu/hr/sqft/F Corrected LMTD: 21.92 F Effective Surfac Area per Shell: 10002.93 sq ft Reference Tmperature

[Fl: 123.333 101.128 Density [Ib cu.ft]: 61.682 61.995 Specific eat Capacity [Btu/lbm F]: 0.998 0.998 /Therm Conductivity

[Btu/hr ft F]: 0.373 0.364 Abso te Viscosity

[cP]: 0.537 0.672 WV NING 1: Central Baffle Spacing May Exceed TEMA Maximum.)/N'S I 9.N'LO (0 I.0?0 LU

* * * ~ ~ ~~ST E R " 5 .0 4 * * * *

Shelf and Tube Heat Exchanger Rating Program 73 h r j 7 'Copyright 1995 by Holtec International.

olc, This computer code Is validated under Holtec International's QA program. , (File Name: WTFRDCCW.EQP X Unit Name: CCMHXO00 1 A&B Unit

Description:

CCW Heat Exchangers This report was created Tuesday, October 2 7, 2009 at 10: 10:01 AM***

PERFORMANCE PREDICT[ON MODE RESULTS * * * * *CASE ID: Metl05 DATE: 06-29-09 PROCEDURE:

ECM95-008 CONVERGENCE TOLERANCE:

0.01 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [I 1000 Ibm/hrj: 3396.78 2237.68 Volume Flow Rate Igpm]: 6885.17 4489.98 Inlet Temperature (degrees F]: 132.62 88.52 Outlet Temperature

[degrees Fl: 115.00 115.28 Fouling Factor [1 /Btu/hr/sqftlF]:

0.00000 0.00133 Operating Pressure [pslgJ: 110.00 60.00 Heat Transfer Coeff [Btu/hr/sqftlF]:

1314.49 844.29 Pressure Drop [psi]: 3.05 3.24 Velocity [ft/sec]:

4.80 Reynolds Number: 47653 14076 Total Heat Duty: 59,730,240 Btu/hr Log Mean Temperature Difference:

2 1.59 F Overall Heat Transfer Coefficient-276.61 Btu/hr/sqft/F Corrected LMTD: 21.59 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[Fl: 123.810 101.900 Density [Ibm/cu.ft]:

61.674 61.985 Specific Heat Capacity [Btu/Ibm F]: 0.998 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.373 0.364 Absolute Viscosity

[cP]: 0.535 0.666 WARNING 1: Central Baffle Spacing May Exceed TEMA Maximum.)LO 0J 0 WATERFORD 3 DESIGN ECM95- 008 Rev. 3 ENWTERRDINGN Attachment 7.3 SENGINEERING4 of 7 STER -5.04 *Shell and Tube Heat Exchanger Rating Program Copyright 1995 by Holtec International.

All rights reserved.This computer code is validated under Holtec International's QA pro m.File Na :WTFRDCCW.EQP Unit Nam CCMHX0001A&B Unit Descri ion: CCW Heat Exchangers This eport was created Tuesday, November 08, 2005 7:20:40 AM /***.PERFORMANCE PREDICTION MODE R LILTS CASE ID: Metl00 DATE: 11 05 PROCEDURE:

EC- M9 008 CONVERGENCE TOLE CE: 0.01 %PARAMETER TUBE SI SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: 339 _ 8 2237.68 Volume Flow Rate [gpm]: 68 0.21 4492.08 Inlet Temperature

[degrees F]: 0.01 91.12 Outlet Temperature

[degrees F]: 115.00 113.92 Fouling Factor [1/Btu/hr/sqft/F]:

0.00000 0.00159 Operating Pressure [psig]: 10.00 60.00 Heat Transfer Coeff [Btu/hr/sqft/F 1 8.25 845.07 Pressure Drop [psi]: 3. 5 3.24 Velocity [ft/sec]:

4.8 Reynolds Number: 47073 14170 Total Heat Duty: 50,888,081 Btu r Log Mean Temperatur ifference:

19.73 F Overall Heat Transfe oefficient:

257.87 Btu/hr/sqft/

Corrected LMTD: 19.73 F Effective Surface rea per Shell: 10002.93 sq ft Reference Te perature [F]: 122.505 102.52 Density [lb cu.ft]: 61.695 61.977 Specific at Capacity [Btu/Ibm F]: 0.998 0.998 Thermap onductivity

[Btu/hr ft F]: 0.372 0.365 Absol t(e Viscosity

,7,3 4* 7'This computer code is validated under Holtec International's QA program. f /File Name: WTFRDCCW.EQP Unit Name: CCMHXOOO I A&B Unit

Description:

CCW Heat Exchangers This report was created Tuesday, October 27, 2009 at 10:26:18 AM* * * *

PERFORMANCE PREDICTION MODE RESULTS *CASE ID: MetlO5 DATE: 06-29-09 PROCEDURE:

ECM95-008 CONVERGENCE TOLERANCE:

0.01 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 lbm/lhr]:

3396.78 2237.68 Volume Flow Rate [gpm]: 6881.98 4491.99 Inlet Temperature

[degrees F]. 130.95 91.01 Outlet Temperature

[degrees F]: 114.99 115.25 Fouling Factor [ I /Btu/hr/sqft/F]:

0.00000 0.00133 Operating Pressure [psig]: 110.00 60.00 Heat Transfer Coeff [Btu/hr/sqft/FJ:

1310.46 846.32 Pressure Drop [psi]: 3.05 3.24 LU Velocity [ftisec]:

4.80 Reynolds Number: 47280 14262 Total Heat Duty: 54,099,751 Btu/hr Log Mean Temperature Difference:

19.55 F Overall Heat Transfer Coefficient:

276.64 Btu/hr/sqft/F Corrected LMTD: 19.55 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: 122.970 103.128 Density [Ibm/cu.ft]:

61.688 61.969 Specific Heat Capacity [Btu/Ibm F]: 0.998 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.372 0.365 Absolute Viscosity

[cPl: 0.539 0.658 WARNING I: Central Baffle Spacing May Exceed TEMA Maximum.

!Unit Desc tion: CCW Heat Exchangers Thi report was created Tuesday, November 08, 2005 t 7:23:27 AM CAE D:e8**PERFORMANCE PREDICTION MODE SULTS *CASE ID: Met98 /DATE: 11 05 PROCEDURE:

EC- M9 008 CONVERGENCE TOLE NCE: 0.01 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: 2237.68 0 Volume Flow Rate [gpm]: 6 178.13 4493.56 C?Inlet Temperature

[degrees F]: 28.90 92.89 0 Outlet Temperature

[degrees F]: 115.00 114.00 .Fouling Factor [lIBtu/hr/sqftlF]:

0.00000 0.00159 Operating Pressure [psig]: 10.00 60.00 Heat Transfer Coeff [Btu/hr/sqft/F.

1 05.59 846.62 Pressure Drop [psi]: 3. 5 3.24 Velocity [ft/sec]:

4.Reynolds Number: 4682 14310 Total Heat Duty: 47,124,352 Bt hr Log Mean Temperatur Difference:

18.27 F Overall Heat Transfe Coefficient:

257.90 Btu/hr/sqftl Corrected LMTD: 18.27 F Effective Surface rea per Shell: 10002.93 sq ft Reference Te perature [F]: 121.949 103.44!Density [lb cu.ft]: 61.704 61 .965 £Specific at Capacity [Btu/Ibm F]: 0.998 0.998 Therma onductivity

[Btu/hr ft F]: 0.372 0.365 Absol e Viscosity

[cP]: 0.545 0.655 W NING 1: Central Baffle Spacing May Exceed TEMA Maximum.

- - - - STER 5.04"* ***Shell and Tube Heat Exchanger Rating Program Copyright 1995 by Holtec International.

7"afrl This computer code is validated under Holtec International's QA program. 5 W "7 -File Name: WTFRDCCW.EQP Unit Name: CCMHXOOO 1 A&B Unit

Description:

CCW Heat Exchangers This report was created Tuesday, October 27, 2009 at 10:35:48 AM* * *\*

PERFORMANCE PREDICTION MODE RESULTS CASE ID: Metl05 DATE: 06-29-09 PROCEDURE:

ECM95-008 CONVERGENCE TOLERANCE:

0.0 1 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [ 1000 lbmn/hrj:

3396.78 2237.68 Volume Flow Rate [gpm]: 6879.91 4493.38 Uo Inlet Temperature (degrees F]: 1 29.85 92.68 (0 Outlet Temperature

[degrees F]: 115.00 115.24 I Fouling Factor [lI/Btu/hr/sqft/F]:

0.00000 0.00133 ?Operating Pressure [psig]: 110.00 60.00 w/ Heat Transfer Coeff [Btu/hr/sqft/F]:

1307.84 847.70 I Pressure Drop [psiJ: 3.05 3.24 Velocity Ift/sec]:

4.80 Reynolds Number: 47038 14388 Total Heat Duty: 50,351,139 Btu/hr Log Mean Temperature Difference:

18.19 F Overall Heat Transfer Coefficient:

276.66 Btu/hr/sqft/F Corrected LMTD: 18.19 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[Fl: 122.423 103.958 Density [Ibm/cu.ft]:

61.697 61.958 Specific Heat Capacity [Btu/lbm F]: 0.998 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.372 0.365 Absolute Viscosity

[cP]: 0.542 0.652 WARNING 1 Central Baffle Spacing May Exceed TEMA Maximum.

WATERFORD 3 DESIGN ECM95- 008 Rev. 3 ENGINEERINGAttachment 7.3 Page 6 of 7 STER -5.04 **********

COW Heat Exchangers Th report was created Tuesday, November 08, 2005 t 7:26:44 AM* ** PERFORMANCE PREDICTION MODE R SULTS *CASE ID: Met95 DATE: 11 05 PROCEDURE:

EC- M- 008 CONVERGENCE TOLE NCE: 0.01 %PARAMETER TUBE SI SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: 339 .78 2237.68 Volume Flow Rate [gpm]: 6 5.05 4495.84 Inlet Temperature

[degrees F]:27.24 954 Outlet Temperature

[degrees F]: 115.00 114.12 Fouling Factor [1/Btu/hr/sqftF]:

0.00000 0.00159 Operating Pressure [psig]: 110.00 60.00 Heat Transfer Coeff [Btu/hr/sqftl 301.61 848.94 Pressure Drop [psi]: 3.24 Velocity [ft/secl: Reynolds Number: 464 14520 Total Heat Duty: 41,493,912

/hr Log Mean Temperatur Difference:

16.08 F Overall Heat Transf Coefficient:

257.95 Btu/hr/sq Corrected LMTD: 16.08 F Effective Surfac Area per Shell: 10002.93 sq ft Reference T perature [F]: 121.120 104. 0 Density [lb cu.ft]: 61.717 61.94 Specific eat Capacity [Btu/Ibm F]: 0.998 0.998 Therm Conductivity

[Btu/hr ft F]: 0.372 0.365 Abso te Viscosity

[cP]: 0.549 0.646 W NING 1: Central Baffle Spacing May Exceed TEMA Maximum..-,.. .\ , ,," (0 C?)0J File Name: WTFRDCCW.EQP Unit Name: CCMH XOOO IA&xB Unit

Description:

CCW Heat Exchangers This report was created Tuesday, October 27, 2009 at 10:38:37 AM* * **

PERFORMANCE PREDICTION MODE RESULTS ***CASE ID: Met] 05 DATE: 0*6-29-09 PROCEDURE:

ECM95-008 CONVERGENCE TOLERANCE:

0.0 1 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [ 1000 ibm/hr]: 3396.78 2237.68 Volume Flow Rate [gpm]: 6876.79 4495.53 Inlet Temperature

[degrees F]: 128. 18 95.18 Outlet Temperature

[degrees Fj: 114.99 11I5.20 L Fouling Factor El /Btulhrlsqft/Fl:

0.00000 0.00133 (Operating Pressure [psig]:- 1 10.00 60.00 Heat Transfer Coeff [Btu/hr/sqftlFj:

1303.82 849.73 0 Pressure Drop [psi): 3.06 3.240 Velocity [ft/sec 3: 4.80 Reynolds Number: 46667 14576 Total Heat Duty: 44,705,029 Btu/hr Log Mean Temperature Difference:

16.15 F Overall Heat Transfer Coefficient:

276.68 Btu/hr/sqft/F Corrected LMTD: 16.15 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: 12 1.586 105.192 Density [lbm/cu.ftJ:

6 1.710 6 1.941 Specific Heat Capacity [Btu/lbmn F]: 0.998 0.998 Thermal Conductivity

[Btu/tr ft F]. 0.372 0.366 Absolute Viscosity

[cP]: 0.546 0.643 WARNING I -Central Baffle Spacing May Exceed TEMA Maximum.

All rights reserved.This computer code is validated under Holtec International's QA prog m.File Na e: WTFRDCCW.EQP Unit Nam : CCMHX0001A&B Unit Descri tion: CCW Heat Exchangers Thi eport was created Tuesday, November 08, 2005 7:28:06 AM >PERFORMANCE PREDICTION MODE R ULTS CASE ID: Met93 DATE: 11 05 PROCEDURE:

EC- M9 008 CONVERGENCE TOLE CE: 0.01 %PARAMETER TUBE S.D SHELL SIDE Mass Flow Rate [1000 Ibm/hr]: 339 .8 2237.68 Volume Flow Rate [gpm]: 68 3.01 4497.41 Inlet Temperature

[degrees F]: 6.13 97.31 Outlet Temperature

[degrees F]: 115.00 114.21 Fouling Factor [1/Btu/hr/sqft/F]:

0.00000 0.00159 Operating Pressure [psig]: 10.00 60.00 Heat Transfer Coeff [Btu/hr/sqftlF.

1 8.94 850.49 Pressure Drop [psi]: 3.24 Velocity [ft/sec]:

4.8 Reynolds Number: 46216 14662 Total Heat Duty: 37,726,460 Btu r Log Mean Temperatur Difference:

14.62 F Overall Heat Transf Coefficient:

257.98 Btu/hr/sqftlF Corrected LMTD: 14.62 F Effective Surfac Area per Shell: 10002.93 sq ft Reference T perature [F]: 120.565 105.75 Density [Ib cu.ft]: 61.726 61.934 Specific eat Capacity [Btu/Ibm F]: 0.998 0.998 Therm Conductivity

[Btu/hr ft F]: 0.372 0.366 Abso te Viscosity

[cPj: 0.552 0.640 W NING 1: Central Baffle Spacing May Exceed TEMA Maximum.))LO (0 (0 Lu

- - - - +****

/)t .e/ -t This computer code is validated under Holtec International's QA program.File Name: WTFRDCCW.EQP 7 Unit Name: CCMHXOOOA&B Unit

Description:

CCW Heat Exchangers This report was created Tuesday, October 27, 2009 at 10:44:31 AM** * ** PERFORMANCE PREDICTION MODE RESULTS *****CASE ID: MetIO5 DATE: 06-29-09 PROCEDURE:

ECM95-008 CONVERGENCE TOLERANCE:

0.01 %PARAMETER TUBE SIDE SHELL SIDE Mass Flow Rate [1000 lbm/hr]: 3396.78 2237.68 Volume Flow Rate [gpm]: 6874.75 4497.01 Inlet Temperature

[degrees Fl: 127.08 96.86 Outlet Temperature

[degrees F]: I 15.00 115.20 Fouling Factor [I /Btu/hr/sqft/F]:

0.00000 0.00133 Operating Pressure [psig]: 110.00 60.00 1O Heat Transfer Coeff [Btu/hr/sqft/F]:

1301.22 851.12 (0 Pressure Drop [psi]: 3.06 3.24 0o Velocity [ftlsec]:

4.80 o Reynolds Number: 46426 14704 wLl Total Heat Duty: 40,941,521 Btu/hr Log Mean Temperature Difference:

14.79 F Overall Heat Transfer Coefficient:

276.71 Btu/hr/sqft/F Corrected LMTD: 14.79 F Effective Surface Area per Shell: 10002.93 sq ft Reference Temperature

[F]: 121.041 106.029 Density [Ibm/cu.ftl:

61.718 61.930 Specific Heat Capacity [Btu/Ibm Fl: 0.998 0.998 Thermal Conductivity

[Btu/hr ft F]: 0.372 0.366 Absolute Viscosity

[cP]: 0.549 0.638 WARNING I: Central Baffle Spacing May Exceed TEMA Maximum.

SWATERFORD 3 DESIGN ECM95- 008 Rev. 3 WAT NERR EINGN Attachment 7.4 B , ENGINEERING Page 2 of 9 recorded twice or 6.7% of the total readings.

The highest recorded value is within 1F of the wet bulb value. Since the highest recorded reading is within 1 IF of the wetbulb value and was recorded only twice, the wetbulb value of 1.0 0 F is considered reasonable.

A paper of the Cooling Tower Institute entitled "Recommended Recirculation Allowances" (pages 8 and 9 of this attachment) describes how to determine design wetbulb temperatures.

The method is ared out below for the following data from this calculation, EC- M95- 008 Rev.ACCW accident flow rate 5350 gpm ACCW temperature leaving wet cooling tower 89.3 OF Design wetbulb temperature 78 OF Calculated approach temperature (89.3- 78) 11.3 0 Wet cooling tower inlet temperature 1 Wet cooling tower range -2"i°OF First, determine the design uncorrected recircu'io-value using the curve for average maximum recirculation.

At 5350 gpm, uncorrected recirculation value is 0.51F. Second, correct for the actual approach and range. Conservatively take the range to be 30°F and the approach to be 12°F, then the correction factor is 1.49. Third, multiply the uncorrected recirculation value by the correction factor to obtain the actual recirculation value which is 0.75°F (=0.5 0 F x 1.49). This calculated value is within the wetbulb temperature of 1°F. As a result, the use of the 1OF wetbulb temperature is considered acceptable value.Conclusion The present values of 1.9 0 F for the drybulb temperature and 1.0 0 F for the wetbulb temperature are reasonable and acceptable.

C?LC)L0 w

ML12023A081

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2.0 CONCLUSION

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