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NUH32PHB-0401, Revision 2, Thermal Evaluation of Nuhoms 32PHB Transfer Cask for Normal, Off Normal, and Accident Conditions with Force Cooling (Steady State), Non-Proprietary
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Issue date:	03/10/2015
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ENCLOSURE15 Non-Proprietary NUH32PHB-0401, Revision 2, Thermal Evaluation of NUHOMS 32PHB Transfer Cask for Normal, Off Normal, and Accident Conditions with Force Cooling (Steady State)

Calvert Cliffs Nuclear Power Plant March 10, 2015

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CONTROLLED COPY E-281 Form 3.2-1 Calculation No.: NUH32PHB-0401 Calculation Cover Sheet Revision No.: 2 AR EVA Revision 8 Page: 1 of 35 DCR NO (if applicable): NUH32PHB-018 PROJECT NAME: NUHOMS 32PHB System PROJECT NO: 10955 CLIENT: CENG - Calvert Cliff Nuclear Power Plant (CCNPP)

CALCULATION TITLE:

Thermal Evaluation of NUHOMS 32PHB Transfer Cask for Normal, Off Normal, and Accident Conditions with Forced Cooling (Steady State)

SUMMARY

DESCRIPTION:

1) Calculation Summary This calculation determines the maximum component temperatures of the Calvert Cliff Nuclear Power Plant Onsite Transfer Cask (CCNPP-FC TC) loaded with 32PHB DSC at 29.6 kW with forced cooling and also determines the peak fuel cladding temperatures in the 32PHB DSC.

2) Storage Media Description Secure network server initially, then redundant tape backup If original Issue, Is licensing review per TIP 3.5 required?

Yes 0 No 0 (explain below) Licensing Review No.:

This calculation is prepared to support a Site Specific License Application by CCNPP that will be reviewed and approved by the NRC. Therefore, a 10CFR72.48 licensing review per TIP 3.5 is not applicable.

Software Utilized (subject to test requirements of TIP 3.3): Version:

ANSYS 10.0 Calculation is complete:

Originator Name and Signature: Venkata Venigalla Date:1 0 Calculation has been checked for consistency, co leteness and correctness:

Checker Name and Signature: Dav Qi ue Date: 0 1 /1 (Appendix B write up) I Calculation Is approved for use:

PA1ELGirish

_ Q, 0=) REVAGROUP, 2.5. .45=T11D2D8D413995674D417F CF, :n=PATELGirish 201 i.03.03 16:17:48 -05'00' Project Engineer Name and Signature: Girish Patel Date: I

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 2of35 REVISION

SUMMARY

AFFECTED AFFECTED REV. DESCRIPTION PAGES Computational 1/0 0 Initial Issue All All 1 To update and clarify the loss of forced cooling 1-3, 6, 8, 17 None condition based on the maximum fuel cladding and 21 temperature limit used for this condition.

2 To determine the time to reach steady-state conditions 1-6, 21,27- See Table 8-1 with air circulation and to determine the time limit for 30, and 33- and Table 8-2 transfer, if air circulation is turned off before reaching 35 steady-state conditions. These additional evaluations are performed in response to RAI 6-2b from NRC.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 3of35 TABLE OF CONTENTS Pame 1 .0 P u rp o s e ............................................................................................................................. 5 2.0 References ........................................................................................................................ 6 3.0 Assumptions and Conservatism .................................................................................... 7

.3.1 CCNPP-FC TC Mass Flow Rate Model ................................................................ 7 3.2 CCNPP-FC TC Model ........................................................................................... 7 3.3 32PHB DSC Model ............................................................................................... 7 4.0 Design Input ...................................................................................................................... 8 4.1 Design Load Cases ............................................................................................ 8 4.2 Thermal Properties of Materials .......................................................................... 8 4.3 Surface Properties of Materials ........................................................................... 9 4.4 Design Criteria ..................................................................................................... 9 5.0 Methodology .................................................................................................................... 10 5.1 Flow Rate Model ............................................................................................... 11 5.2 CCNPP-FC TC Model ........................................................................................ 14 5.3 Loss of Forced Airflow during Transfer Operations ............................................. 17 5.4 32PHB DSC/Basket Analysis ............................................................................. 17 6.0 Results and Discussion ............................................................................................... 20 7.0 Conclusion ...................................................................................................................... 27 8.0 Listing of Computer Files ........................................................................................... 29 APPENDIX A Forced Air Pressure Drop ............................................................................ 31 APPENDIX B Time Limit to Complete Transfer Operations After Forced Cooling is T u rn e d Off ....................................................................................................................... 33

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 4of35 LIST OF TABLES Page Table 4-1 Design Load Cases for 32PHB DSC in CCNPP-FC TC with FC .................... 8 Table 4-2 List of Materials in the CCNPP-FC TC Model (1).................................................. 9 Table 5-1 TC/DSC Annulus Hydraulic Diameter and Flow Area Calculation .................. 12 Table 5-2 List of the Friction Factors in the Mass Flow Model ...................................... 12 Table 5-3 Mass Flow Rates Along Each Annular Segment .......................................... 14 Table 5-4 Heat Transfer Coefficients in the DSC/TC Annulus for Forced Air Flow ..... 16 Table 6-1 Maximum Temperatures of CCNPP-FC TC @ 29.6 kW, Forced Air C o o ling ....................................................................................................... . . . 21 Table 6-2 Maximum Temperatures of CCNPP-FC TC @ 29.6 kW, Loss of Forced A ir T ra nsie nt ............................................................................................... . . 22 Table 7-1 Maximum Temperatures of CCNPP-FC TC @ 29.6 kW, Forced Air C irculatio n ................................................................................................ . . . 27 Table 8-1 Sum m ary of ANSYS Runs ............................................................................ 29 Table 8-2 Associated Files and Macros ........................................................................ 30 Table A-1 Forced Air Pressure Drop ............................................................................ 32 Table B-1 Maximum Fuel Cladding and Basket Component Temperatures after Air C irculation is Initiated .................................................................................. . . 34 Table B-2 Maximum Fuel Cladding and Basket Component Temperatures, Air Circulation Turned off after 8 Hours ............................................................. 35 LIST OF FIGURES Page Figure 5-1 Finite Element Mesh of Flow Rate Model with FLUID1 16 Elements .............. 18 Figure 5-2 Finite Element Model of CCNPP-FC TC ...................................................... 19 Figure 6-1 TC Temperature Distribution - Off-Normal Hot with Forced Convection, @

29.6 kW, 127 Btu/hr-ft 2 Insolation, 104 0 F Ambient (load case # 3) ................ 23 Figure 6-2 32PHB DSC Temperature Distribution - Off-Normal Hot with Forced Convection, @ 29.6 kW, 127 Btu/hr-ft2 Insolation, 104 0 F Ambient (load c a s e # 3 ) ............................................................................................................. 24 Figure 6-3 TC Temperature Distribution - Loss of Forced Air Transient, t = 8 hr @

29.6 kW, 127 Btu/hr-ft2 Insolation, 104 0 F Ambient (load case # 5) ............... 25 Figure 6-4 32PHB DSC Temperature Distribution - Loss of Forced Air Transient, t =

8 hr @ 29.6 kW, 127 Btu/hr-ft2 Insolation, 1040 F Ambient (load case # 5) ....... 26

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 5 of 35 1.0 PURPOSE The Calvert Cliff Nuclear Power Plant Onsite Transfer Cask (CCNPP-FC TC) loaded with 32PHB DSC at 29.6 kW utilizes forced cooling as a possible recovery mode to improve the thermal performance of the system if the transfer operations exceed the operational time limits (such as 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months for 29.6 kW heat load) determined for off-normal hot horizontal transfer conditions in Reference [6].

This calculation determines the maximum component temperatures of the CCNPP-FC TC loaded with 32PHB DSC at 29.6 kW with forced air cooling under steady-state conditions and also determines the peak fuel cladding temperature within the 32PHB DSC with the forced air cooling. There are no time limits associated for horizontal transfer operations once the forced air circulation is initiated.

It also establishes a time limit to restore the forced air circulation or to complete the transfer of the 32PHB DSC at 29.6 kW in CCNPP-FC TC to the HSM-HB in case of system failure to ensure that the peak fuel cladding temperature remains below the temperature limit of 7520 F [8]. This time limit to restore the forced air circulation or to complete the transfer of the DSC into the storage module assumes that the system is under steady-state conditions. APPENDIX B presents the thermal evaluation to determine the minimum time to operate the blowers such that the system reaches steady-state conditions. In addition, an additional time limit to restore the forced air circulation or to complete the transfer of the DSC into the storage module is also computed considering that forced cooling was available only for eight hours before it is turned off.

To determine the maximum component temperatures of the Calvert Cliff CCNPP-FC TC loaded with 32PHB DSC at 29.6 kW with forced air cooling under steady-state conditions, this calculation utilizes the methodology described in [7] and the ANSYS thermal model of CCNPP-FC TC described in [6]. The peak fuel cladding and the basket component temperatures for 32PHB DSC are determined using the ANSYS thermal model and methodology described in [5].

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 Page: 6 of 35 AR EVA

2.0 REFERENCES

1 Rohsenow, Hartnett, Cho, "Handbook of Heat Transfer", 3 rd Edition, 1998.

2 Rohsenow, Hartnett, Ganic, "Handbook of Heat Transfer Fundamentals", 2 rd Edition, 1985.

3 ANSYS computer code and On-Line User's Manuals, Version 10.0.

4 Design Criteria Document, "Design Criteria Document (DCD) for the NUHOMS 32PHB System for Storage", Transnuclear, Inc., NUH32PHB.0101 Rev. 4.

5 Calculation, "Thermal Evaluation of NUHOMS 32PHB Canister for Storage and Transfer Conditions", Transnuclear, Inc., NUH32PHB-0403, Rev. 1.

6 Calculation, "Thermal Evaluation of NUHOMS 32PHB Transfer Cask for Normal, Off Normal, and Accident Conditions", Transnuclear, Inc., NUH32PHB-0402, Rev. 1.

7 Calculation, "Benchmarking of the ANSYS Model of the OS200FC Transfer Cask",

Transnuclear, Inc., NUH32PHB-0400, Rev. 2.

8 NRC Spent Fuel Project Office, Interim Staff Guidance, ISG-1 1, Rev 3, "Cladding Considerations for the Transportation and Storage of Spent Fuel".

9 GESC, NAC International, Atlanta Corporate Headquarters, 655 Engineering Drive, Norcross, Georgia (Engineering Report # NS3-020, Effects of 1300'F on Unfilled NS-3, while Bisco Products, Inc., 11/84).

10 Calvert Cliffs Independent Spent Fuel Storage Installation Updated Safety Analysis Report, Rev. 17.

11 I.E. Idelchik, Handbook of Hydraulic Resistance, 3 rd Edition, 1994.

12 ASHRAE Handbook Fundamentals, 1997.

13 Perry & Chilton, Chemical Engineering Handbook, 5 th Edition,1973.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 7of35 3.0 ASSUMPTIONS AND CONSERVATISM The following assumptions and conservatism are considered in the calculation.

3.1 CCNPP-FC TC Mass Flow Rate Model All the assumption and conservatism considered in this calculation for the CCNPP-FC TC Mass Flow Rate Model-are the same as those described in [7] and are summarized below.

The annulus between the DSC shell and the TC inner liner are divided into parallel, individual segments along the DSC axis. No circumferential air flow is considered between the parallel segments. Since the presence of circumferential flow will tend to exchange hotter air in the narrower segments of the annulus with cooler air in the wider segments of the annulus, ignoring the potential for circumferential flow will yield conservative temperature estimates for the peak temperatures on the DSC shell and TC inner liner An air flow rate of 450 cfm is considered for forced air cooling. To evaluate the air flow rate in each of the parallel segments, a constant pressure boundary condition is applied at the inlet such that the total mass flow rate at the outlet is equal to the total airflow rate of 450 cfm.

Since the pressure drop through the annulus between the DSC shell and TC inner shell is the major factor controlling the amount of air flow rate in each segment, the mass flow rate model considers only the annulus over the length of the DSC to determine the mass flow rate through each segment.

3.2 CCNPP-FC TC Model All the assumptions and conservatisms described in Section 3.1of [6] are applicable for this calculation.

The methodology to analyze the CCNPP-FC TC with forced cooling is presented in [7] and is used in this calculation.

3.3 32PHB DSC Model The assumptions and conservatism considered for 32PHB DSC model are the same as those described in [5], Section 3.0.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 8of35 4.0 DESIGN INPUT 4.1 Design Load Cases The following design cases in Table 4-1 are analyzed in this calculation to determine the thermal performance of CCNPP-FC TC with 32PHB DSC at 29.6 kW and with forced cooling (FC). The load cases are based on requirements in [4].

Table 4-1 Design Load Cases for 32PHB DSC in CCNPP-FC TC with FC Case Operation Condition Description Notes Ambient 3 )

Temperature( Insolation Airflow

[°F] [Btu/hr-ft2] [cfm]

1 Normal Normal Hot, FC (1) 104 82 450 2 Normal Normal Cold, FC (1) -8 0 450 3 Off-Normal Off-Normal Hot, FC -- 104 127 450 4 Off-Normal Off-Normal Cold, FC (1) -8 0 450 5 Off-Normal(4) Loss of Forced Airflow, (2) 104 127 0 Transient (2) 104_127_0 Notes:

1) Load cases # 1, 2 and 4 are bounded by the Load Case # 3 (See Section 6.0 for justification).

2) Initial temperatures taken from steady-state results of Load Case # 3. At time t=0, the forced air circulation is assumed to be lost.

3) Ambient air temperatures ranging from -8 to 104 0 F are conservative compared to the ambient air temperature range from -3 to 1030 F in [10], Section 12.3.6.

4) The temperature limits of off-normal transfer conditions are considered to evaluate this load case.

4.2 Thermal Properties of Materials Materials used in CCNPP-FC TC ANSYS thermal model are listed in Table 4-3, Section 4.3 of

[6]. The material numbers associated with elements simulating the forced air cooling are listed in Table 4-2.

The heat transfer coefficients for the forced air flow over the DSC/TC annulus are calculated using the same correlations described in [7],Section 5.2 and are presented in MassFIowConvCoeff_32PHB_29.6kW.xls for the 29.6 kW heat load as noted in Table 8-2.

Thermal properties used in CCNPP-FC TC model are listed in Section 4.3 of [6].

Materials and Thermal properties used in the 32PHB DSC models are listed in Section 4.1 of

[5].

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 9of35 Table 4-2 List of Materials in the CCNPP-FC TC Model (1)

Component Mat # in ANSYS Model TC FLUID1 16 Flow Elements 90 TC LINK34 Convection Elements 451-466 TC LINK34 Convection Elements (At Entrance through spacer disc)

TC LINK34 Convection Elements (At Exit thought Top Cask Lid) 471 (1) See Table 4-3, Section 4.3 of [6] for complete material listing of the CCNPP-FC TC components in addition to those listed above.

4.3 Surface Properties of Materials The emissivity value of 0.587 is considered for both the DSC shell (stainless steel) and the transfer cask inner shell (stainless steel) in calculation of thermal radiation exchange between these shells [1].

It is assumed that the absorptivity and the emissivity of stainless steel are equal. Solar absorptivity and emissivity of 0.587 are used for the TC outer surfaces [1].

4.4 Design Criteria The design criteria and evaluation of 32PHB DSC basket are presented in Reference [5] and design criteria for the TC are presented in Reference [6] and are listed below.

Maximum fuel cladding temperature limits of 752 0 F (4000C) for normal/off-normal load cases listed in Table 4-1 and 1,058 0 F (570 0C) for accident conditions listed in Table 4-1 are considered for the FAs with an inert cover gas as concluded in ISG-1 1 [8].

The ASTM B29 lead used in the gamma shield has a melting point of approximately 620°F [13].

" For design purposes of this application, the long-term, bulk average temperature of the NS-3 material is set to 280 OF [10] or less, and short-term limits for accident conditions should be 1,300 OF or less [9].

A Calculation Calculation No.:

Revision No.:

NUH32PHB-0401 2

AR EVA Page: 10 of 35 5.0 METHODOLOGY The CCNPP-FC TC contains design provisions for the use of forced air cooling to improve its thermal performance. The system will consist of redundant, industrial grade pressure blowers and power systems, ducting, etc. When operating, the fan system is expected to generate a flow rate of 450 cfm or greater, which will be ducted to the location of the ram access cover at the bottom of the cask.

The following are the steps to determine the maximum steady state temperatures of the DSC/TC components with the forced convection using ANSYS:

1. Assume a ATair for initial runs, Calculate Texit and Tavg based on the initial guess and the air properties based on Tavg.

Where, Texit = Tamb + A T.,

T :(Trb + Tx,) /2

=vg Tnb = 104 0 F

2. Run Flow Rate Model described in Section 5.1 iteratively based on average properties of air calculated in previous step to compute the air mass flow rate in each DSC/TC annulus segment. (Run ID: "FlowRate_32PHB_29kW" for 29.6 kW load case listed in Table 8-1)

3. Determine the heat transfer coefficients within the annulus based on the mass flow rates computed in Step 2 (see worksheet "Hcdata" for mass flow rate in Ibm/hr and Hccalc for convection coefficients in "MassFIowConvCoeff 32PHB_29.6kW.xls" for the 29.6 kW heat load as noted in Table 8-2)

4. Run Thermal Model (Run ID: "TR_32PHB_29kW' for 29.6 kW heat load as listed in Table 8-1) described in Section 5.2 based on mass flow rates and heat transfer coefficients calculated in Step 2 and Step 3.

5. Calculate Texit, Tavg, and ATair based on results from Thermal Model in Step 4.

6. Ifdifference between assumed ATair in Step 1 and calculated ATair in Step 5 is less than I°F, stop iterations, otherwise proceed to Step 7.

7. Rerun the Flow Rate Model described in Section 5.1 and Step 2 with air properties based on Tavg from Step 5.

8. Ifdifferences between air mass flow rates in each DSC/TC annulus segment from Step 7 and Step 2 are less than 0.1 lbm/hr, stop iterations, otherwise proceed to Step 9.

9. Repeat Steps 4 to 9 until the solution converges.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 11 of 35 The above methodology is validated versus a NRC accepted methodology using SINDA/FLUINT as documented in [7].

5.1 Flow Rate Model The forced air enters the TC from the ram access opening and the airflow turns and enters the ten (10) flow paths formed by the 0.25" thick cutouts in the spacer disc attached to the TC's bottom. After the forced air exits from the flow paths formed by the cutouts in the spacer disc, the airflow turns and flows in the annulus between the DSC and the TC's inner liner.

Given the gap between the DSC and TC varies with circumferential position, plus variances in the heating of the air, the airflow will distribute itself around the circumference of the DSC/TC inner liner, until an equal pressure drop is achieved everywhere.

For the purposes of this calculation, each half of the annulus is divided into 19 angular segments as shown in Table 5-1 with 00 at the top of the normally horizontal TC and 1800 at the bottom. The mass flow rate along each of the 19 angular segments is calculated using the Flow Rate Model. The mass flow rates obtained from this model are used as input to the thermal model of the DSC/TC described in Section 5.2.

The 19 annular segments for forced air flow are modeled using FLUID1 16 elements with their length equal to the length of the DSC. The potential for circumferential airflow is conservatively ignored as discussed in Section 3.1. The flow area and hydraulic diameter for each annular segment are calculated based on the position of the DSC within the TC cavity.

The determination of the gap between the DSC and the TC inner liner as a function of circumferential position was made considering a DSC shell outer diameter of 67.25 inches, a TC inner liner inner diameter of 68 inches, and a 0.120-inches thick slide rail that is located 18.50 from the centerline of the TO. Table 5-1 presents the calculation basis for the gap between the TC and DSC and the associated hydraulic diameter and air flow area.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 12 of 35 Table 5-1 TCIDSC Annulus Hydraulic Diameter and Flow Area Calculation Cask "X" Cask "Y" DSC "X" DSC "Y" Hydraulic Angle Location Location Location Location Diameter Flow Area Section Angle Segment (degrees) (in) (in) (in) (in) (m) (m) 1 -5 5 0 0.000 34.000 0.000 33.355 0.0328 2.423E-03 2 5 15 10 5.904 33.483 5.793 32.852 0.0326 2.407E-03 3 15 25 20 11.629 31.950 11.414 31.359 0.0319 2.363E-03 4 25 35 30 17.000. 29.445 16.696 28.918 0.0309 2.289E-03 5 35 45 40 21.855 26.046 21.481 25.600 0.0296 2.189E-03 6 45 55 50 26.046 21.855 25.625 21.502 0.0279 2.066E-03 7 55 65 60 29.445 17.000 29.003 16.745 0.0259 1.923E-03 8 65 75 70 31.950 11.629 31.510 11.469 0.0237 1.765E-03 9 75 85 80 33.483 5.904 33.068 5.831 0.0214 1.595E-03 10 85 95 90 34.000 0.000 33.625 0.000 0.0191 1.420E-03 11 95 105 100 33.483 -5.904 33.160 -5.847 0.0167 1.244E-03 12 105 115 110 31.950 -11.629 31.684 -11.532 0.0144 1.073E-03 13 115 125 120 29.445 -17.000 29.237 -16.880 0.0122 9.123E-04 14 125 135 130 26.046 -21.855 25.891 -21.725 0.0102 7.667E-04 15 135 145 140 21.855 -26.046 21.747 -25.917 0.0085 6.406E-04 16 145 155 150 17.000 -29.445 16.929 -29.323 0.0072 5.382E-04 17 155 165 160 11.629 -31.950 11.587 -31.836 0.0062 4.627E-04 18 165 175 170 5.904 -33.483 5.885 -33.376 0.0055 4.164E-04 19 175 185 180 0.000 -34.000 0.000 -33.895 0.0053 4.007E-04 The friction factor along the length of the DSC/cask annulus is calculated as:

f =(1.58

In Re- 3.28)- 2 [Eq. 7 of Reference 2 / Section 5.1 of 7]

Table 5-2 lists the friction factors as a function of Reynolds numbers.

Table 5-2 List of the Friction Factors in the Mass Flow Model Re f 4*f Re f 4*f 1 0.093 0.372 1500 0.015 0.058 100 0.063 0.250 1750 0.014 0.055 200 0.039 0.154 2000 0.013 0.052 300 0.030 0.122 3000 0.011 0.046 400 0.026 0.105 4000 0.010 0.041 500 0.023 0.094 5000 0.010 0.039 600 0.021 0.086 6000 0.009 0.037 800 0.019 0.075 8000 0.008 0.034 1000 0.017 0.069 12500 0.007 0.030 1250 0.016 0.063 22500 0.006 0.025 The areas, hydraulic diameters, and friction factors calculated for the 19 annular segments are applied as real constants to the FLUID1 16 elements. The friction factors are applied using the TB,FCON command as function of temperature and Reynolds number.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 13 of 35 The total mass flow rate based on 450 cfm discharge from the fan for the 29.6 kW load case is calculated as follows:

m = 450 cfm

Pa,,ravergetemp

=450* (0.3048)'

0.973 kg 60 S

=0.2067 kg I s

Where, m = Total Mass Flow Rate, (kg/s) 3 Pair,averagelemp = Density of air based on Average Air Temperature = 0.973 kg/mi The air density in the above equation is calculated based on a pressure drop of 6 inches water gauge based on the calculations presented in Appendix A and an initial air exit temperature of 2920 F for the 29.6 kW heat load case. The final air exit temperature is determined iteratively through the steps shown in Section 5.0.

The forced air introduced in the annular gap between the DSC and the cask distributes itself based upon the flow area and hydraulic diameter. The Flow Rate Model computes the air flow rate in each annular segment based on achieving an equal pressure drop over any segments of the annulus. The Flow Rate Model for determining the mass flow rates is shown in Figure 5-1.

A constant volumetric airflow rate of 450 cfm is assumed to evaluate the air mass flow rate in each of the parallel segments. A constant pressure is applied at the inlet of the air flow into the DSC/TC annulus and the mass flow at the outlet is computed for the flow along the 19 annular segments. The pressure at the inlet is iteratively changed until the total mass flow rate at outlet of the 19 annular segments is equal to total mass flow rate of 0.2067kg/s for the 29.6 kW heat load.

The mass flow rates obtained for each of the 19 angular segments for use in the CCNPP-FC TC thermal model along with the hydraulic diameters and flow areas are presented in the Table 5-3 29.6 kW heat load cases.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 14 of 35 Table 5-3 Mass Flow Rates Along Each Annular Segment 29.6 kW Hydraulic Flow Massflow Diameter Area Section (Ibm/hr) (in) (in2) 1 100.53 1.29 3.75 2 99.46 1.28 3.73 3 96.26 1.26 3.66 4 91.33 1.22 3.55 5 84.26 1.16 3.39 6 75.78 1.10 3.20 7 66.59 1.02 2.98 8 57.09 0.93 2.74 9 47.89 0.84 2.47 10 39.32 0.75 2.20 11 30.98 0.66 1.93 12 23.67 0.57 1.66 13 17.61 0.48 1.41 14 12.81 0.40 1.19 15 9.17 0.34 0.99 16 6.66 0.28 0.83 17 5.01 0.24 0.72 18 4.07 0.22 0.65 19 3.77 0.21 0.62 5.2 CCNPP-FC TC Model ANSYS model and the thermal analysis methodology for the CCNPP-FC TC are described in Section 5.0 of reference [6]. This calculation utilizes the thermal model of CCNPP-FC TC from reference [6] by adding the FLUID116 and LINK34 elements to simulate the forced convection. Figure 5-2 shows the CCNPP-FC TC finite element model with the LINK34 and FLUID116 elements added.

Forced air circulation through the annulus of the DSC/TC is modeled using the FLUID1 16 and LINK34 elements. The FLUID1 16 element models the forced air flow along the axial length of the DSC/cask annulus by conducting heat and transmitting the fluid between its nodes, whereas the LINK34 elements model the convection from the DSC/TC surfaces due to the forced air flow. The FLUID1 16 elements are modeled such that they are connected to the LINK34 convection elements.

The mass flow rates obtained from the Flow Rate Model described in Section 5.1 for each of the annular segments from 0' to 1500 are applied to the FLUID1 16 elements using the "SFE,,,hflux" command.

Based on the mass flow rates obtained for each of the annular segments from 00 to 1500, the convection heat transfer coefficients for the DSC/TC annulus are computed using the correlations for flow within ducts and pipes. The convection heat transfer coefficients are

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 15 of 35 computed as a function of the local hydraulic diameter, the Reynolds number, and the thermophysical properties of air. These convection heat transfer coefficients are applied to the LINK34 elements using the mpdata,hf / mp,hf commands.

The correlations for the convection coefficients are identical to those in [7] and are taken from equations 7, 43, 44, 45, 57, and 57a from Chapter 7 of [2] as follows:

For 0.5 < Pr < 2000 and 104 < Re < 5x1 06:

Nu= hcDh - Re x Pr x f/2 k 1.07 + 12.7(Pr 21 3 - 1)(f/2)0.

Re = VxpxDh p

f = (1.58 x In Re - 3.28)-2 For 0.5 < Pr < 2000 and 3000 < Re < 104:

Nu= hcDh (Re-1000)1x3 Pr x f/2 0 5 k 1.0 + 12.7(Pr 2 - 1)(f/2)

For 0.5 < Pr < 2000 and 0 < Re < 3000:

Nu = hcDh = 2.035x (x*)-(1/3) -0.7, for x* < 0.01 k

Nu = 2.035 x (x*)-( 1 3) -0.2, for 0.01 < x*< 0.06 Nu = 3.657 + 0.0998/x*, for x* > 0.06 Where:

Nu = Nusselt number hc = convection coefficient Dh = hydraulic diameter k = thermal conductivity of fluid at film temperature V = flow velocity p = density of fluid at the film temperature

,u = dynamic viscosity Pr = Prandtl number f = friction factor Re = Reynolds number x* = entry length factor = x/Re/Dh /Pr x = length of duct/pipe

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 16 of 35 Forced convection is omitted conservatively and conduction is assumed in the region between the canister support rails (i.e., approximately 1500 to 1800) due to the narrowness of the gap between the DSC and the TC inner liner. Based on the above correlations and the mass flow rates from Section 5.1 the heat transfer coefficients for the annular segments from 00 to 1500 are calculated and are presented in Table 5-4 for the DSC/TC annulus with a 29.6 kW heat load.

The material.properties used in the CCNPP-FC TC model are listed in Section 4.3 of [6] as noted in Section 4.0.

The geometry of the CCNPP-FC TC Model is shown in Figure 5-1 to Figure 5-5 of Reference

[6] and in Figure 5-2 with the LINK34 and FLUID1 16 elements.

Typical boundary conditions for the Thermal Model of CCNPP-FC TC are shown in Figure 5-6 through Figure 5-7 of Reference [6].

Steady state calculations were performed to determine the maximum component temperatures for the CCNPP-FC TC with 32PHB DSC at 29.6 kW and forced convection.

Table 5-4 Heat Transfer Coefficients in the DSC/TC Annulus for Forced Air Flow HARt Trnn~fAr flnpfficIpnt~ (RtII/hr~in2~oF~

... .. ......... . . ........... \ ....... ... .F )

Temp Entry at Section Section Section Section Section Section Section Section (OF) Spacer(') 1 2 3 4 5 6 7 8 110 0.028 0.028 0.028 0.027 0.027 0.026 0.025 0.024 210 0.029 0.029 0.028 0.028 0.027 0.026 0.025 0.024 310 0.015 0.029 0.029 0.029 0.029 0.028 0.027 0.026 0.024 410 0.030 0.030 0.030 0.029 0.029 0.028 0.026 0.025 510 0.031 0.031 0.030 0.030 0.029 0.028 0.027 0.025 Heat Transfer Coefficients (Btu/hr-in 2 -°F)

Exit at Temp Section Section Section Section Section Section Section Section Top (OF) 9 10 11 12 13 14 15 16 Lid(')

110 0.022 0.020 0.009 0.010 0.011 0.012 0.015 0.017 210 0.022 0.020 0.010 0.011 0.012 0.014 0.017 0.020 310 0.023 0.010 0.011 0.012 0.014 0.016 0.019 0.022 0.016 410 0.023 0.011 0.012 0.013 0.015 0.017 0.021 0.024 510 0.011 0.012 0.013 0.014 0.016 0.019 0.022 0.026 Notes:

(1) The lowest heat transfer coefficient is used for the Entry at spacer disc and Exit at Top lid for conservatism

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 17 of 35 5.3 Loss of Forced Airflow during Transfer Operations The postulated loss of forced airflow condition considers an evaluation of the system performance for the case wherein steady-state conditions are established with the fan in operation and, subsequently the fan airflow is lost. To minimize the occurrence of this postulated condition, the CCNPP-FC TC skid is equipped with redundant industrial grade blowers, each one of these blowers capable of supplying the required minimum air flow rate.

These blowers are also powered with a redundant power.supply. The analysis assumes that the transient begins with DSC/TC at steady-state conditions from load case# 3. At time = 0, the fan airflow is lost and the system starts to heat up.

This analysis presents a time limit to restore the forced airflow or to complete the transfer of the 32PHB DSC with 29.6 kW heat load to the HSM-HB concrete module. The time limit is selected such that the peak fuel cladding temperature will remain below the normal/off-normal cladding temperature limit of 752°F for transfer operations as recommended in [8]. The selected time limit is bounding for NUHOMS 32PHB system with heat loads at or less than 29.6 kW. The results of the calculated thermal response of the DSC and TC for this transient analysis are presented in Section 6.0.

It should be noted that this condition also covers the normal/off-normal conditions in the transfer operations when the fans are removed and the ram is prepared to insert the DSC into the HSM-HB.

5.4 32PHB DSC/Basket Analysis The DSC shell temperature profiles from steady state analysis in Section 5.2 for load case #

3 and from the transient analysis described in Section 5.3 for load case # 5 are used to determine the maximum basket component temperatures including the maximum fuel cladding temperature based on the 32PHB DSC/basket model described in Reference [5]. No changes are considered to the thermal model of the 32PHB DSC and the methodology presented in Reference [5].

Calculation No.: NUH32PHB-0401 Revision No.: 2 Page: 18 of 35 The mass flow rate along each of the 19 annular A constant segments is pressure is obtained at the applied at the outlet for use in inlet, such that the CCNPP-FC total mass flow TC thermal rate is 0.2067 model.

kg/s for 29.6 kW load cases.

Figure 5-1 Finite Element Mesh of Flow Rate Model with FLUID116 Elements

Calculation No.: NUH32PHB-0401 Revision No.: 2 Page: 19 of 35 Exit Nodes Coupled to FLUID116 Elements \

Air Flow Inlet Nodes, Fixed at 104'F I

Fluid 116 and Link34 TC Rail

/

Elements Figure 5-2 Finite Element Model of CCNPP-FC TC

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 20 of 35 6.0 RESULTS AND DISCUSSION Based on the ambient conditions for normal/off-normal operations presented in Table 4-1, off-normal hot ambient conditions (load case # 3) presents the bounding case for the thermal analysis due to the higher ambient temperature/insolation. Therefore, the maximum temperatures of the CCNPP-FC TC with 32PHB DSC at 29.6 kW and forced convection for off-normal hot ambient conditions (load case # 3) bounds the maximum temperatures for normal hot/cold and off-normal cold conditions (load cases # 1, 2 and 4).

Steady state thermal analysis is performed for the CCNPP-FC TC with 32PHB DSC at 29.6 kW and forced convection for off-normal hot ambient conditions listed in Table 4-1 to determine the DSC shell temperature profile and the maximum TC component temperatures.

The DSC shell temperature profiles is used to determine the peak fuel cladding and basket component temperatures based on the 32PHB DSC/Basket thermal model steady state analysis.

Table 6-1 summarizes the maximum temperatures for the CCNPP-FC TC components /

32PHB DSC components and shows that the maximum component temperatures are below the allowable limits. Figure 6-1 and Figure 6-2 present the temperature profiles for the off-normal hot condition with forced convection for the CCNPP-FC TC and 32PHB DSC.

In addition, the maximum difference between the exit air temperature of 2920 F assumed in Section 5.1 and exit air temperature of 291.6 obtained from the thermal model as presented in Table 6-1 for the 29.6 kW heat load is -0.4 0 F. Therefore, no further iterations are required.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 21 of 35 Table 6-1 Maximum Temperatures of CCNPP-FC TC @ 29.6 kW, Forced Air Cooling Temperature [OF]

Component Off-Normal Hot (Load Case # 3) Max.

Allowable Fuel Cladding 689 752 [4, 8]

Basket (Guide Sleeve). 667 Al/Poison Plate 666 Basket Rails 451 Top Shield Plug 366 Bottom Shield Plug 247 Max. DSC Shell (1) 410 ---

Inner Shell 362 ---

Gamma Shield 356 620 Structural Shell 310 ---

Bulk Avg. Temp of Radial Neutron Shield Bulk Avg. Temp of Top Neutron Shield Bulk Avg. Temp of Bottom Neutron Shield Cask Lid 256 ---

Cask Outer Shell 279 ---

Forced Air, Inlet / Exit 104/291.6 (1) The maximum DSC shell temperature is the temperature along the "DSC Shell" as shown in Figure 5-3 of [6] and does not include the top and bottom end plates.

Transient thermal analysis is performed for the CCNPP-FC TC with 32PHB DSC at 29.6 kW and without forced convection to analyze the loss of forced air circulation condition listed in Table 4-1 to determine the DSC shell temperature profile and the maximum TC component temperatures. This analysis assumes that the transient begins with DSC/TC at steady-state conditions from load case# 3. At time = 0, the fan airflow is lost and the system starts to heat up.

Based on the transient thermal analysis a maximum duration of 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months is available to complete the transfer to the HSM-HB or re-establish the fan airflow. The DSC shell temperature profile at 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months from the time the fan airflow is lost is used to determine the peak fuel cladding and basket component temperatures based on the 32PHB DSC/Basket thermal model steady state analysis. Table 6-2 summarizes the maximum temperatures for the CCNPP-FC TC components / 32PHB DSC components and shows that the maximum component temperatures are below the allowable limits.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 22 of 35 Table 6-2 Maximum Temperatures of CCNPP-FC TC @ 29.6 kW, Loss of Forced Air Transient Temperature [OF]

Component Loss of Forced Air Flow Max.

(Load Case # 5) Allowable Time = 8 hrs Fuel Cladding 734 752 [4, 8]

Basket (Guide Sleeve) 716 Al/Poison Plate 715 Basket Rails 478 Top Shield Plug 377 Bottom Shield Plug 316 Max. DSC Shell 422 ---

Inner Shell 364 ---

Gamma Shield 358 620 Structural Shell 310 ---

Bulk Avg. Temp of 216 280 [10]

Radial Neutron Shield Bulk Avg. Temp of 202 280 [10]

Top Neutron Shield Bulk Avg. Temp of Bottom Neutron Shield Cask Lid 253 ---

Cask Outer Shell 276 ---

(1) The maximum DSC shell temperature is the temperature along the "DSC Shell" as shown in Figure 5-3 of [6] and does not include the top and bottom end plates.

Figure 6-3 and Figure 6-4 present the temperature profiles for the loss of forced air flow transient analysis at 8 hrs for the CCNPP-FC TC and 32PHB DSC.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 23 of 35 AN NiV 25 2009 11:21:48 POrT No. 5 NDL SOUMICTN STEP=-1 SUB =4 TI*iE=l SM =104 S =361.724

-104 132.636 161.272 189.908 218.544 ED 247.18 F'-1 275.816 304.452 333.088 361.724 AN NOV 25 2009 11:21:49 PICT NO. 6 MEAL SOI17rIN STEP=-1 SUB =4 TIME=1 TEMP SM =104 SM =361.724 104 132.636 161.272 189.908 218.544 247.18 275.816 304.452 333.088 361.724 Figure 6-1 TC Temperature Distribution - Off-Normal Hot with Forced Convection,

@ 29.6 kW, 127 Btu/hr-ft2 Insolation, 104°F Ambient (load case # 3)

A Calculation Calculation Revision No.:

No.: NUH32PHB-0401 2

AR EVA Page: 24 of 35 ANEYS 10.0A1 ANYS 10.OA1 NO 25 2009 NOV 25 2009 13:39:19 13:39:26 PLwr NO. 2 PLtr NO. 3 NODAL SOEUT'IO NDAL SCUIMON S7EP-1 SUB=I1 am =1 TIME=1 TEMP 20=258.12 S =247.426 S( -689.126 S1 -667.038 258.12 247.426 306.01 294.049

- 353.899 M 340.673 387 .297 401.789

- 449.679 433.92 497.568 480.544 545.458 _-- 527.167 593.347 573.791 641.237 620.415 689.126 667.038 Fuel Cladding Guide Sleeve AN0YSl.OA AiSYS 10. AI NV 25 2009 NOV25 2009 13:39:43 13:39:47 KoLOT. 6 Pwn NO. 5 NODALSCLI NowL SCUTIcO4 STEE'=I STEP=1 SUB-1 TD6=1 a. =1 TEW TEWP WN =250. 226 S =104

-450.662

=C S =407.957 l 250.226 104 272.497 137.773 294.768 171.546 317.038 205.319 339.309 239.092 Fri 361.579 272.865 383.85 _'- 306.638 406.121 1 340.411 1 428.391 374.184 450.662 407.957 Basket Rail DSC Shell Figure 6-2 32PHB DSC Temperature Distribution - Off-Normal Hot with Forced Convection, @ 29.6 kW, 127 Btu/hr-ft 2 Insolation, 104 0F Ambient (load case # 3)

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 25 of 35 AN NOV 25 2009 11:43:17 PLOr NO. 3 NCKAL SOurIcTIM TlbE=8 S,* =IE69 096

=151.

M =363.79 151.096 174.728 198.361

- 221.994 245.626 269.259

_-- 292.892 316.524 340.157 363.79 CUNPP-FC-TC with 322HB, 29.6 kW - Off-Nonmal Loss of FC Transient AN NOV 25 2009 11:43:18 PIOr NO. 4 NOEAL SOIUMIcIN TEWP SM]N =151. 096 SM(=363.79 151.096 174. 728 198. 361 221.994 245. 626 269.259

_-- 292.892 316.524 340.157 363.79 CENPP-FC-TC with 32PHB, 29.6 kW - Off-NoWmal Loss of FC Transient Figure 6-3 TC Temperature Distribution - Loss of Forced Air Transient, t = 8 hr

@ 29.6 kW, 127 Btu/hr-ft2 Insolation, 104 0 F Ambient (load case # 5)

A Calculation Calculation Revision No.:

No.: NUH32PHB-0401 2

AR EVA Page: 26 of 35 ANSYS 10.0A1 ANSYS10.0A1 NOV25 2009 NO 25 2009 13:41:01 13:41:09 PLOTr N. 12 PLwr NO. 13 NODL SOLwrIcz NODAL SC1JTIM1 STEP=2 S7EP-2 SU =1 TMW=2 TEMW TIME-2 SMN=373. 651 SMH :364. 024 SMX -734.416 SM 364.024 715. 816

- 373.651 i403.112 413.736 453.821 442.2 481.288 493.906 533.991 520,376 574. 076 559.464 614.161 598.552 654.246 637.64 694.331 676. 728 734.416 715.816 Fuel Cladding Guide Sleeve MEYS 10.OAI ANSYS10.OAI NOV25 2009 NOV25 2009 13:41:26 13:41:30 PLOr NO. 15 PIr NO. 16 NDL STEEI2 SELTIcIN NODAL SOION US E=1 TIME=2 T!lM=2 TwM SM -366.165 SVN -258. 341 SM4 =478.169 I( =422.84 366.165 258. 341 378.61 276. 618

- 391.054 403.499 294. 896 313.174 415.944 331. 451 428.389 349.729 440.834 _-- 368.007 M 453.279 386.285 465.724 404.562 478.169 422.84 Basket Rail DSC Shell Figure 6-4 32PHB DSC Temperature Distribution - Loss of Forced Air Transient, t = 8 hi

@ 29.6 kW, 127 Btulhr-ft 2 Insolation, 104 0 F Ambient (load case # 5)

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 27 of 35

7.0 CONCLUSION

Table 7-1 summarizes the maximum temperatures of the TC components and the 32PHB DSC for the off-normal hot horizontal transfer condition with forced cooling and at 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months transient after the loss of forced cooling.

Table 7-1 Maximum Temperatures of CCNPP-FC TC @ 29.6 kW, Forced Air Circulation Temperature [°F]

Component Off-Normal Hot Loss of Forced Cooling Max.

AIMowabx (Load Case # 3) time = 8 hrs (Load Case # 5) e Fuel Cladding 689 734 752 [4, 8]

Basket (Guide Sleeve) 667 716 Al/Poison Plate 666 715 Basket Rails 451 478 Top Shield Plug 366 377 Bottom Shield Plug 247 316 Max. DSC Shell (1) 410 422 ---

Inner Shell 362 364 ---

Gamma Shield 356 358 620 Structural Shell 310 310 ---

Bulk Avg. Temp of Radial Neutron Shield Bulk Avg. Temp of 223 202 280 [10]

Top Neutron Shield Bulk Avg. Temp of Bottom Neutron Shield Cask Lid 256 253 Cask Outer Shell 279 276 ---

Forced Air, Inlet / Exit 104/291.6 ....

Notes:

(1) The maximum DSC shell temperature is the temperature along the "DSC Shell" as shown in Figure 5-3 of [6] and does not include the top and bottom end plates.

Based on the discussion in APPENDIX B, the following time limits are proposed to ensure that the fuel cladding temperature does not exceed its normal temperature limit of 752°F.

If air circulation is initiated, it must be maintained for a minimum duration of 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months before it is turned off. Once the air circulation is turned off, a maximum duration of 6 hours6.944444e-5 days 0.00167 hours 9.920635e-6 weeks 2.283e-6 months is available to complete the transfer to the HSM-HB or re-establish the fan airflow.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 28 of 35

If air circulation is initiated and maintained for a minimum duration of 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months before if it is turned off, a maximum duration of 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months is available to complete the transfer to the HSM-HB or re-establish the fan airflow.

As seen the above table and the discussion presented in APPENDIX B, all design criteria specified in Section 4.4 are herein satisfied.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AR EVA Page: 29 of 35 8.0 LISTING OF COMPUTER FILES Revision 0 and Revision 1: All the runs are performed using ANSYS version 10.0 [3] with operating system "Linux RedHat ES 5.1", and CPU "Opteron 275 DC 2.2 GHz" / "Xeon 5160 DC 3.0 GHz".

Revision 2: All the ANSYS runs are performed using ANSYS version 10.0 [3] with operating system "RHEL5.6x64"on the AREVA HPC cluster with Intel X5675 CPUs A summary of ANSYS runs is shown in Table 8-1.

Table 8-1 Summary of ANSYS Runs Date / Time for Run Name Description Output File Flow Rate Model to determine the mass flow rates 11/25/2009 FlowRate_32PHB_29kW for 29.6 kW Heat Load. 11:04 AM CCNPP-FC TC with 32PHB DSC and 11/25/2009 TR_32PHB_29kW Forced Convection- 29.6 kW 11:21 AM TR_32PHB_29kW-Map Run for Mapping the 32PHB DSC Shell 11/25/2009 Temperature Profiles for off-normal hot load case 11:33 AM Run for Mapping the CCNPP-FC TC Temperature 11/25/2009 TR_32PHB_29kW-TC-Map Profiles for Loss of Forced Airflow load case 11:33 AM CCNPP-FC TC with 32PHB DSC and 11/25/2009 32PHB_LOSSFC_OFN_TRANS Loss of Forced Airflow- 29.6 kW 11:43 AM Run for Mapping the 32PHB DSC Shell 11/25/2009 32PHBLOSSFCOFNTRANSMap Temperature Profiles for Loss of Forced Airflow 11:48 AM load case at 8 hrs 11:48_AM Load 1: 32PHB DSC Basket for Off-Normal Hot 11/25/2009 32PHBTC4M Transfer with Forced Convection Load 2: 32PHB DSC Basket for Loss of Forced 1:42 PM airflow @ 8 hrs Runs for Minimum Time to Reach Steady-State with Air Circulation Run to map temperatures of TC from Load Case # 02/11/2015 32PHBTCOFN_TRANS-TC-Map 6 of [6] at 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months . 12:10 PM CCNPP-FC TC with 32PHB DSC and 02/11/2015 TR_32PHB_29kW_TRANS Forced Convection- 29.6 kW, Transient 03:16 PM TR_32PHB_29kWTRANS-Map Run to map the 32PHB DSC shell temperature 02/11/2015 profiles at 10 hours1.157407e-4 days 0.00278 hours 1.653439e-5 weeks 3.805e-6 months and 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months 11:10 PM 32PHB DSC basket for off-normal hot transfer with 02/12/2015 2PB CFCRNforced convection at 10 hours1.157407e-4 days 0.00278 hours 1.653439e-5 weeks 3.805e-6 months and 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months 12:23 AM Runs for Time Limit to Complete Transfer after 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months of Air Circulation CCNPP-FC TC with 32PHB DSC, 29.6 kW, TR 32PHB 29kW TRANS 8HR transient, 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months with forced cooling and 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months 02/11/2015 without forced cooling. For initial conditions see 04:20 PM Run ID: 32PHB TC OFN TRANS-TC-Map Run to map the 32PHB DSC shell temperature 02/11/2015 TR_32PHB_29kW_TRANS-Map-8HR profiles at 4 hours4.62963e-5 days 0.00111 hours 6.613757e-6 weeks 1.522e-6 months and 6 hours6.944444e-5 days 0.00167 hours 9.920635e-6 weeks 2.283e-6 months after air circulation 11:12 PM is stopped 32PHB DSC basket for off-normal hot transfer 02/12/2015

- P without air circulation at 4 hours4.62963e-5 days 0.00111 hours 6.613757e-6 weeks 1.522e-6 months and 6 hours6.944444e-5 days 0.00167 hours 9.920635e-6 weeks 2.283e-6 months 12:20 AM

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 30 of 35 ANSYS macros, and associated files used in this calculation are shown in Table 8-2.

Table 8-2 Associated Files and Macros File Name Description Date / Time HTOTHCL.MAC [6] Total heat transfer coefficients for horizontal 2/19/2009 cylindrical surface 12:37 PM Total heat transfer coefficients for vertical flat 2/19/2009 HTOT_VPL.MAC [6] surface 12:37 PM 10/21/2009 6071PM 32PHBTCMat.inp [6] Material properties for CCNPP-FC Cask 6:07 PM B _RADHorizontal.inp [61* Macro for Creating Radiation Exchange between the 10/21/2009 32PHBTO RDSC/TC when the TC is in Horizontal Orientation 4:46 PM 32PHBMatl.inp [5] Material properties for 32PHB DSC with Helium 09/09/09 09:54 AM 32PHBHLZC2.MAC [5] Heat generation for 32PHB DSC, 29.6 kW 09/03/09 08:56 AM Macro [5] Macro to get Maximum/Minimum temperatures 05/20/05 12:03 PM Results.mac [5] Macro to list maximum and average 32PHB DSC 07/22/09 component temperatures 11:52 AM CCNPP-FC-TC.db [6] ANSYS thermal model for CCNPP-FC TC 08/28/09 2:41 P0M 32PHBModel.db [5] ANSYS thermal model for 32PHB DSC 07/10/09

- 7:49 PM 11/11/2009 5:07P 32PHB TC PPLFC.inp Macros for Post-Processing Transient Runs 5:07 PM Spreadsheet for calculating the hydraulic diameters, 11/25/2009 MassFIowConvCoeff_32PHB_29.6kW.xls friction factors, mass flow rates and heat transfer 4:01 PM coefficients 11/25/2009 Pressure Drop-CCNPP-FC-TC.xls Spreadsheet for Pressure Drop Calculation 4:00P 4:00 PM Macro for creating radiation exchange between the 10/28/2009 32PHBTCORADHorizontal.inp* DSC/TC when the TC is in horizontal orientation for 05:47 PM runs with air circulation 32PHBTCO_ NTRANS.db [6] ANSYS thermal database file from 10/21/2009 32HBTCOF_ TRANS_____db__[6]Load Case # 6 of [6] 06:18 PM 32PHBTCQENTRANS.rth [6] ANSYS thermal results file from Load Case # 6 of 10/21/2009

[6] 06:28 PM 02/11/2015 32PHB TC PPFC.inp Macros for post-processing transient runs 02:25 02:25 PM

Athough both files have the same name, the time stamps should be used to select the appropriate file based on the description.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 31 of 35 APPENDIX A FORCED AIR PRESSURE DROP The pressure drop experienced by the forced air from the fan discharge, through the DSC and cask annulus, and its subsequent exhausting back into the ambient is computed assuming 1-D flow pipe flow relationships. Table A-1 presents the build up of the 'fittings' assumed along the flow path, the effective hydraulic diameter, the assumed loss coefficients from [11] and [12], and the resultant pressure drop. A pressure drop of approximately 5.64 inches water gauge is expected. For conservatism and to account for operational modifications, a design fan rating of 8 inches water gauge is recommended.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 32 of 35 AR EVA Page:

PROPRIETARY

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 33 of 35 APPENDIX B TIME LIMIT TO COMPLETE TRANSFER OPERATIONS AFTER FORCED COOLING IS TURNED OFF For the CCNPP-FC TC loaded with 32PHB DSC at the maximum heat load of 29.6 kW, if the air circulation is initiated as a recovery operation during transfer, the air circulation needs to be turned off before transferring the 32PHB DSC into the HSM-HB storage module.

Further, with the air circulation turned on another postulated scenario considered is evaluation of the system performance for the case wherein steady-state conditions are established with the air circulation in operation and, subsequently the air circulation is lost. To minimize the occurrence of this condition, the CCNPP-FC TC skid is equipped with redundant industrial grade blowers and each one of these blowers is capable of supplying the required minimum air flow rate. These blowers are also powered with a redundant power supply.

In both the above scenarios i.e. turning off air circulation to offload the 32PHB DSC to HSM-HB or failure of the air circulation will decrease the heat dissipation and will result in a gradual increase of the maximum temperatures of the TC/DSC components.

Minimum Time to Operate Air Circulation to reach Steady-State Conditions To bound the above scenarios, an additional time limit of 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months is established in Section 6.0 to either restore the air circulation or to complete the transfer of the 32PHB DSC at 29.6 kW in CCNPP-FC TC to the storage module to ensure that the peak fuel cladding temperature remains below the temperature limit of 752°F [8]. This off-normal analysis (Load Case # 5) assumes that the transient begins with TC/DSC at steady-state conditions from Load Case # 3 and that at time = 0, the air circulation is lost and the system starts to heat up.

In order to estimate the duration needed for the 32PHB DSC to reach the steady-state conditions of Load Case # 3 (See Table 4-1), transient thermal evaluation after air circulation is turned on during horizontal transfer is performed. For this evaluation the initial conditions are obtained from off-normal hot, horizontal transfer Load Case # 6 at 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months from [6]. The initial conditions are mapped using ANSYS Run ID: "32PHBTCOFNTRANS-TC-Map" listed in Table 8-1. This transient evaluation utilizes the same thermal model used to evaluate the steady-state condition with air circulation. The maximum fuel cladding temperature and basket component temperatures are used as the primary criteria to reach the steady-state condition for this transient evaluation. As seen from the results of the thermal evaluation in Table 7-1, the TC components have a much larger margin to their limits compared to the fuel cladding.

Therefore, only the fuel cladding and DSC components are presented in this evaluation.

To determine the time to reach steady-state conditions, the transient thermal evaluation of the CCNPP-FC TC with air circulation is performed for a duration of 42 hours4.861111e-4 days 0.0117 hours 6.944444e-5 weeks 1.5981e-5 months (See Run ID:

TR_32PHB_29kWTRANS in Table 8-1). From this evaluation, the DSC shell temperature profile at 10 hours1.157407e-4 days 0.00278 hours 1.653439e-5 weeks 3.805e-6 months and 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months after the air circulation is initiated is retrieved and applied to the 32PHB DSC/basket model from Reference [5] to determine the maximum fuel cladding temperature and basket component temperatures based on the methodology presented in Section 5.4.

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 34 of 35 Table B-1 presents the maximum fuel cladding and basket component temperatures at 10 hours1.157407e-4 days 0.00278 hours 1.653439e-5 weeks 3.805e-6 months and 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months after the initiation of the air circulation (See Run ID:

32PHBDSCFCTRANS in Table 8-1). A comparison of the maximum fuel cladding temperature determined at 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months after the initiation of the air circulation to that determined under steady-state conditions (with air circulation) shows that the temperature difference is 30 F. This small difference shows that the system is very close to steady-state conditions.

In addition, a review of the maximum fuel cladding temperature between 10 hours1.157407e-4 days 0.00278 hours 1.653439e-5 weeks 3.805e-6 months and 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months after initiation of the air circulation in Table B-1 shows that the maximum fuel cladding temperature is only lowered by 20 F during 10 hours1.157407e-4 days 0.00278 hours 1.653439e-5 weeks 3.805e-6 months . This small magnitude of change in the fuel cladding temperature shows that the system is very close to steady-state conditions in 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months .

Therefore, if the air circulation is turned on for 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months , the 32PHB DSC can be considered to be at steady-state conditions and 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months is available to complete the transfer operations based on the evaluation results presented in Section 6.0.

Table B-1 Maximum Fuel Cladding and Basket Component Temperatures after Air Circulation is Initiated Temnernture [°F]

Off-Normal Hot, Off-Normal Hot, Off-Normal Hot, 10 hours1.157407e-4 days 0.00278 hours 1.653439e-5 weeks 3.805e-6 months 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months Steady-State with AT, after air after air Air Circulation AT, circulation circulation (Load Case # 3) T20 hoursTsteady-State Component is initiated is initiated (See Table 7-1)

Fuel Cladding 694 692 689 3 BasketBakt673 670 667 (Guide Sleeve) 3 Al/Poison Plate 672 669 666 3 Basket Rails 444 449 451 -2 Top Shield Plug 349 360 366 -6 Bottom Shield 259 251 247 4 Plug

Calculation No.: NUH32PHB-0401 Calculation Revision No.: 2 AREVA Page: 35 of 35 Time to Complete the Transfer Operations if Air Circulation is Turned Off after 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months Using the same methodology presented above to determine the minimum time to reach steady-state conditions, a transient thermal evaluation (See Run ID:

TR_32PHB_29kWTRANS_8HR in Table 8-1) of the CCNPP-FC TC with 32PHB DSC at 29.6 kW heat load is performed by considering that the air circulation is available for a duration of 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months . After 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months , the air circulation is turned off and the system begins to heat up. This evaluation is performed for a total of 1.6 hours6.944444e-5 days 0.00167 hours 9.920635e-6 weeks 2.283e-6 months during which air circulation is available for the first 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months and is then turned off for the remaining duration. The initial conditions before initiating the air circulation are obtained from off-normal hot, horizontal transfer Load Case # 6 at 20 hours2.314815e-4 days 0.00556 hours 3.306878e-5 weeks 7.61e-6 months from [6] similar to the evaluation to determine the minimum time to reach steady-state conditions (ANSYS Run ID: "32PHBTCOFNTRANS-TC-Map" listed in Table 8-1).

To determine the time limit to complete the transfer operations once the air circulation is turned off after 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months , the DSC shell profiles at 4 hours4.62963e-5 days 0.00111 hours 6.613757e-6 weeks 1.522e-6 months and 6 hours6.944444e-5 days 0.00167 hours 9.920635e-6 weeks 2.283e-6 months after the air circulation is turned off are retrieved. These DSC shell profiles are then applied to the 32PHB DSC/basket model from Reference [5] to determine the maximum fuel cladding temperature and basket component temperatures based on the methodology presented in Section 5.4 evaluation (See Run ID: 32PHBDSC_FCTRANS-8HR in Table 8-1).

Table B-2 presents the maximum temperature for the condition, wherein the air circulation is available for 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months and is then turned off to off load the DSC into the storage module or is lost. As seen from Table B-2, the maximum fuel cladding temperature is 7260 F and 735 0 F after the air circulation is turned off for 4 hours4.62963e-5 days 0.00111 hours 6.613757e-6 weeks 1.522e-6 months and 6 hours6.944444e-5 days 0.00167 hours 9.920635e-6 weeks 2.283e-6 months , respectively with large margin to the fuel cladding temperature limit of 7520 F.

Table B-2 Maximum Fuel Cladding and Basket Component Temperatures, Air Circulation Turned off after 8 Hours Temperature [°F]

Component Loss of forced cooling(1 ) Loss of forced cooling(l) Max. Allowable time = 4 hours4.62963e-5 days 0.00111 hours 6.613757e-6 weeks 1.522e-6 months time = 6 hours6.944444e-5 days 0.00167 hours 9.920635e-6 weeks 2.283e-6 months Fuel Cladding 726 735 752 [4, 8]

Basket (Guide Sleeve) 708 716 Al/Poison Plate 707 716 Basket Rails 465 471 Top Shield Plug 364 370 Bottom Shield Plug 293 304 Note:

1) Air circulation is either turned off or lost after 8 hours9.259259e-5 days 0.00222 hours 1.322751e-5 weeks 3.044e-6 months .

ML15075A348

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ML15075A348

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