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=Text=
=Text=
{{#Wiki_filter:United States Nuclear Regulatory Commission Official Hearing Exhibit In the Matter of
{{#Wiki_filter:United States Nuclear Regulatory Commission Official Hearing Exhibit                                                 5,9$
: Entergy Nuclear Operations, Inc. (Indian Point Nuclear Generating Units 2 and 3)
In the Matter of:
ASLBP #:07-858-03-LR-BD01 Docket #:05000247 l 05000286 Exhibit #:
Entergy Nuclear Operations, Inc.                                 6XEPLWWHG'HFHPEHU
Identified:
(Indian Point Nuclear Generating Units 2 and 3)
Admitted: Withdrawn:
ASLBP #: 07-858-03-LR-BD01 Docket #: 05000247 l 05000286 Exhibit #: RIV00052A-00-BD01                 Identified: 10/15/2012 Admitted: 10/15/2012                         Withdrawn:
Rejected: Stricken: Other: RIV00052A-00-BD01 10/15/2012 10/15/2012 COMBUSTION ENGINEERING, INC. CHATTANOOGA, TENN. IPEC00069599 C E N C -1110 Bro ZOl ANALYTICAL REPORT FOR I L/j' INDIAN POINT REACTOR VESSEL UNIT NO. 2 .i: Ii, 1:_ Cockrell Lowry*
Rejected:                                      Stricken:
I PEC00069600 
Other:
*
C E N C - 1110
* IPEC00069601 REPORT NUMBER 1110 SUBJECT CATEGORY "ANALYTICAL REPORT" COMBUSTION ENGINEERING, INC. NUCLEAR COMPONENTS ENGINEERING DEPARTMENT C.E. CONTRACT NO. 17765 ANALYTICAL REPORT FOR INDIAN POINT REACTOR VESSEL UNIT NO. 2 C. R. COCKRELL AND J. C. LOWRY
                                                                                                          ~\\\\I\\\\\'
* *
Bro ZOl I
* IPEC00069602
L/j' ANALYTICAL REPORT FOR INDIAN POINT REACTOR VESSEL UNIT NO. 2 COMBUSTION ENGINEERING, INC.                                .i: Ii, 1:_         Cockrell CHATTANOOGA, TENN.                                                  Lowry*
* *
IPEC00069599
* I PEC00069603
 
'rHI:) l)()CUMF,H'I' r:'i 'rEE PROPEilTY OF OIJ :INGINEERIW;, urc., ,'IDP):;O 1, COHN. Atm 1::', Wl,[, TO BE IU;:PRO\)UCED, f)i\ mmD TO PUlmC'J ,r, ry FOHMATIO].r Fon MAKItIG OF DW\.'dINGS 0;\ APPf,['\A'J'U::
RIV000052A Submitted: December 22, 2011 IPEC00069600
EXCEP'!' lmERE PROVIDED FOR BY AGHEE;*1J::IJT  
 
',lITH :3AID  
RIV000052A Submitted: December 22, 2011
*
* REPORT NUMBER 1110 SUBJECT CATEGORY "ANALYTICAL REPORT" COMBUSTION ENGINEERING, INC.
* *
NUCLEAR COMPONENTS ENGINEERING DEPARTMENT C.E. CONTRACT NO. 17765 ANALYTICAL REPORT FOR INDIAN POINT REACTOR VESSEL
* I PEC00069604 
* UNIT NO. 2 C. R. COCKRELL AND J. C. LOWRY IPEC00069601
.-* *
 
* I PEC00069605 Acknowledgement is hereby made of the important contributions rendered by the following individuals:.
RIV000052A Submitted: December 22, 2011
                            *
                            *
* IPEC00069602
 
RIV000052A Submitted: December 22, 2011
          *
                            'rHI:) l)()CUMF,H'I' r:'i 'rEE PROPEilTY OF corI[BU~)'l'I OIJ :INGINEERIW;, urc.,       ,'IDP):;O 1, COHN.
Atm 1::', Wl,[, TO BE IU;:PRO\)UCED, f)i\ mmD TO PUlmC'J ,r, ry LI-FOHMATIO].r Fon MAKItIG OF DW\.'dINGS 0;\ APPf,['\A'J'U:: EXCEP'!'
lmERE PROVIDED FOR BY AGHEE;*1J::IJT ',lITH :3AID CCMPjl,~I': *
          *
* IPEC00069603
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069604
 
RIV000052A Submitted: December 22, 2011
          *
          .-
Acknowledgement is hereby made of the important contributions rendered by the following individuals:.
Project Enginee.&:
Project Enginee.&:
J. S. Meek Structural Analysis M. W. Alexander J. K. Allison R. J. Caudle W. R. Ferguson W. J. Heilker F
J. S. Meek Structural Analysis M. W. Alexander J. K. Allison R. J. Caudle W. R. Ferguson W. J. Heilker F* P. Hill
* P. Hill Des ign. Endneer B. R. Moss
* Des ign. Endneer B. R. Moss
* *
* IPEC00069605
* I PEC00069606
 
* DISIRIBUTDpN LIST No. Ot COEies w. G. Benz, Jr. 1 D. w. Sher 1 H. w. Dolfi 1 J. w. Alden 3 F. P. Hill 2 T. Halvorsen 1 J. S. Meek 1 w . B. Bunn 1
RIV000052A Submitted: December 22, 2011
* J. w. Harper 1 B. R. Moss 1 J. K. Allison 1 C. R. Cockrell 1 w. J. Heilker 1 J. C. Lowry 1 Westinghouse-APD 20 Library 1
                          *
* IPEC00069607
                          *
* *
* IPEC00069606
* I PEC00069608 
 
*
RIV000052A Submitted: December 22, 2011
* I PEC00069609 1.000 ABSTRACT The structural integrity of the 173 in. 1.0. Indian Point Reactor Vessel -Unit No. 2 designed and fabricated under contract to the Atomic Power Division of the Westinghouse Electric Corporation is established by the results of the detailed structural and thermal analysis contained in this report. PREPARED BY C. R. Cockrell And 9'(]* f8J7 J.C. Lowry APPROVED BY £;,)?M:
* DISIRIBUTDpN LIST No. Ot COEies
{/!. S. F. P. Hill . Project Engineer Supervisor of Analytical Design Group H. W. Dolfi """-, Supervisor of Contract Engineering Section CERTIFIED BY -4imJ I? ;;ttl! { CERTIFICATE NO. . ,.::r?' 76 .jf STATE OF TENNESSEE
: w. G. Benz, Jr.                         1 D. w. Sher                               1 H. w. Dolfi                             1 J. w. Alden 3
* *
F. P. Hill 2
* IPEC00069610
T. Halvorsen 1
*
J. S. Meek 1
* IPEC00069611 TABLE OF comus 1
: w. B. Bunn 1
* 000 ABS TRA.C'f" ......."......"........"....""....."".....".
* J. w. Harper B. R. Moss J. K. Allison 1
1 2 000 IM'TR.ODUCTION  
1 1
.***.* "." .......... " *** " ***** _ * * * * * * * *
C. R. Cockrell 1
* 4 2'.010 Subject .................  
: w. J. Heilker 1
"." .............. " ............ " ... ""..... 4 2.020 P\lrpoae ...........  
J. C. Lowry 1
"" ................................. " ...........  
Westinghouse-APD                         20 Library 1
".... 4 2 .. 030 Scope ................... " ... " ............................................. " 4 3
* IPEC00069607
* 000 DES IGN CRITERIA *********************.************
 
5 4.000 GEOMETRY AND GENERAL CONFIGURATION  
RIV000052A Submitted: December 22, 2011
****************
                            *
6 5.000  
                            *
* IPEC00069608
 
RIV000052A Submitted: December 22, 2011 1
1.000 ABSTRACT The structural integrity of the 173 in. 1.0. Indian Point Reactor Vessel - Unit No. 2 designed and fabricated under contract to the Atomic Power Division of the Westinghouse Electric Corporation is established by the results of the detailed structural and thermal analysis contained in this report.
PREPARED BY
                                  ?,(&~
C. R. Cockrell And 9'(]* f8J7
* J.C. Lowry APPROVED BY
(~e £;,)?M:
{/!. S. ~ek
                                ~R?/J!I F. P. Hill cfu~~-Qf H. W. Dolfi   """-,
            . Project Engineer    Supervisor of            Supervisor of Analytical              Contract Design Group            Engineering Section CERTIFIED BY -4imJ I? ;;ttl!.jf{
CERTIFICATE NO. . ,.::r?' 76 STATE OF TENNESSEE
* IPEC00069609
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069610
 
RIV000052A Submitted: December 22, 2011 2
TABLE OF comus 1
* 000 ABS TRA.C'f" ......."......"........"....""....."".....".                                 1 2 ~ 000 IM'TR.ODUCTION .***.* "." .......... " *** " ***** _ * * * * * * * *
* 4 2'.010 Subject ................. "." .............. " ............ "... "".....         4 2.020 P\lrpoae ........... "" ................................. "........... "....       4 2 .. 030 Scope ................... "... "............................................. " 4 3 *000 DES IGN CRITERIA *********************.************                                         5 4.000 GEOMETRY AND GENERAL CONFIGURATION ****************                                         6 5.000  


==SUMMARY==
==SUMMARY==
OF RESULTS ****.*****.*****...**.********..
OF RESULTS ****.*****.*****...**.********..                                         7 5.010 Control Rod Housings *.*******************. 7-8 5.020 Closure Head Flange and Shell **.******.*****                                       9 5.030 Vessel Flange and Shell ********************* 10
7 5.010 Control Rod Housings *.*******************.
* 5.040 Main Closure Studs **********************.*** 11 5.050 Inlet Nozzle and Vessel Support ************* 12 5.060 Outlet Nozzle and Vessel Support *********** 13 5.070 Vessel Wall Transition ********************* 14 5.080 Core Barrel Support Pads *******.*********** 15 5.090 Bottom Head to Shell Juncture ****.******.** 16 5.100 Bottom Head Instrumentation Penetrations *.* 17 6.000 DISCUSSION OF RESULTS AND METHOD OF ANALYSIS ***** 18 6.010 Control Rod Housings ....................... 18-20 6.020 Closure Head Flange and Shell ************** 20 6.030 Vessel Flange and Shell ******************** 21
7-8 5.020 Closure Head Flange and Shell **.******.*****
* 6.040 Main Closure Studs ************************* Zl-22 6.050 Inlet Nozzle and Vessel Support ************* 22~23 IPEC00069611
9 5.030 Vessel Flange and Shell *********************
 
10 5.040 Main Closure Studs **********************.***
RIV000052A Submitted: December 22, 2011
11 5.050 Inlet Nozzle and Vessel Support *************
                          *
12 5.060 Outlet Nozzle and Vessel Support ***********
                            *
13 5.070 Vessel Wall Transition  
* IPEC00069612
*********************
 
14 5.080 Core Barrel Support Pads *******.***********
RIV000052A Submitted: December 22, 2011 3
15 5.090 Bottom Head to Shell Juncture ****.******.**
TABLE OF CONTENTS (Cont I d)
16 5.100 Bottom Head Instrumentation Penetrations  
* 6.060 6.070 Outlet Nozzle and Vessel Support ********** 23-24 Vessel Wall Transition ******************** 24-25 6.080 Core Barrel Support Pads ****************** 25-26 6.090 Bottom Read to Shell Juncture ************* 26 6.100 Bottom Head Instrumentation Penetrations ** 27 7.000 REFERENCES ...................................................... .jj ........ ..
*.* 17 6.000 DISCUSSION OF RESULTS AND METHOD OF ANALYSIS ***** 18 6.010 Control Rod Housings .......................
28-29 8.000 APPENDICES A. Detailed Structural Analysis Calculations ****** Al - A367 B. Thermal Analys is ***************************.** Bl - B124 C. Drawings - Combustion Engineering, Inc ******** Cl - C13
18-20 6.020 Closure Head Flange and Shell **************
        *
20 6.030 Vessel Flange and Shell ********************
* IPEC00069613
21 6.040 Main Closure Studs *************************
 
Zl-22 6.050 Inlet Nozzle and Vessel Support *************
RIV000052A Submitted: December 22, 2011
                          *
* *
                            *
* IPEC00069612
* *
* IPEC00069613 TABLE OF CONTENTS (Cont I d) 6.060 Outlet Nozzle and Vessel Support **********
23-24 6.070 Vessel Wall Transition  
********************
24-25 6.080 Core Barrel Support Pads ******************
25-26 6.090 Bottom Read to Shell Juncture *************
26 6.100 Bottom Head Instrumentation Penetrations  
** 27 7.000 REFERENCES  
...................................................... .jj ........ .. 28-29 8.000 APPENDICES A. Detailed Structural Analysis Calculations  
****** Al -A367 B. Thermal Analys is ***************************.**
Bl -B124 C. Drawings -Combustion Engineering, Inc ******** Cl -C13
* *
* IPEC00069614
* IPEC00069614
* 2.000 nmQDUCTION 2.010 SubJ@ct The Indian Point Reactor Vessel -Unit No. 2 is a 173 in. I.D. pressurized water reactor. The vessel is of cylindrical shape terminating in a hemispherical head at the bottom and a bolted flange at the top. Four inlet and four outlet nozzles are located in the cylindrical wall section. The vessel is supported by four weld built-up pads located on the underside of two inlet nozzles and two outlet nozzles. The closure head is of the hemispherical type. The closure seal is of the O-ring type. 2.020 Purpose This report contains the detailed structural and thermal analysis required to substantiate the adequacy of the design of the 173 in. I.D. Indian Point Reactor Vessel. 2.030 The detailed analytical work necessary to justify the reactor vessel and its associated parts included in the contract are contained in this report. All equations used are shown and intermediate answers and final answers are usually presented in tabular form *
 
* IPEC00069615 4
RIV000052A Submitted: December 22, 2011 4
IPEC00069616 J,ooQ p2S1GN CRITERIA The design shall be in accordance with the ASME'Boiler and Pressure Vessel Code Section III, Nuclear Vessels and Special Case Rulings in effect on the date of purchase order. The design parameters used were Design Pressure ................................... . Normal Operating Pressure **********.*******
2.000 nmQDUCTION
Design Temperature  
* 2.010 SubJ@ct The Indian Point Reactor Vessel - Unit No. 2 is a 173 in. I.D. pressurized water reactor.
..........................  
The vessel is of cylindrical shape terminating in a hemispherical head at the bottom and a bolted flange at the top. Four inlet and four outlet nozzles are located in the cylindrical wall section.
.. Normal Operating Inlet Water Temp ***********
The vessel is supported by four weld built-up pads located on the underside of two inlet nozzles and two outlet nozzles. The closure head is of the hemispherical type. The closure seal is of the O-ring type.
Normal Operating Outlet Water Temp **.*******
2.020 Purpose This report contains the detailed structural and thermal analysis required to substantiate the adequacy of the design of the 173 in. I.D. Indian Point Reactor Vessel.
6 psia 5 psig 50 0 F 57°F .7 o F 5 Des ign Life ******************.*.***.*******.
2.030 ~
40 years 1. 2. 3. 4.
        ~              The detailed analytical work necessary to justify the reactor vessel and its associated parts included in the contract are contained in this report. All equations used are shown and intermediate answers and final answers are usually presented in tabular form *
* 5. 6. 7. 8. 9. 10. 11. 12. 13. 14.
* IPEC00069615
* IPEC00069617 Transient Condition Occurrences Plant heatup at 100°F/Hr.
 
200 Plant cooldown at 100°F/Hr.
RIV000052A Submitted: December 22, 2011 IPEC00069616
200 Plant loading at 5% of 14,500 full power per min. Plant unloading at 5% of full power per min. 14,500 Step load increase 10% 2,000 of full power -not to exceed full power Step load decrease of 2,000 from 50% power Step load decrease of 200 50% of full power Reactor trip 400 Hydro test 3125 pSia 5 Hydro test 2500 pSia 5 Steady state fluctuations 10 6 Loss of flow, one pump 80 Loss of load 80 Steam break 5 See Material Al1owlb1es Sm @ 70°F C: J S/o SA-240 Typ. 316 20.0 KSI 30/) SA-102B 26.7 SA-J36 26.7 4_;:;" ASTM-A540-B24 43.3 3JJ Inconel -, 23.3 4 4.2 4 4.3 4 4 .8 .9 27 in Sm @ 550 0 F 17 6 KSI 26 7 26 7 36 8 23 3 ,:," (
 
:",
RIV000052A Submitted: December 22, 2011 5
* *
J,ooQ   p2S1GN CRITERIA
* IPEC00069618
          ~          The design shall be in accordance with the ASME'Boiler and Pressure Vessel Code Section III, Nuclear Vessels and Special Case Rulings in effect on the date of purchase order.
* *
The design parameters used were Design Pressure ................................... .         psia Normal Operating Pressure **********.*******               5 psig Design Temperature .......................... ..         50 0 F Normal Operating Inlet Water Temp ***********             57°F Normal Operating Outlet Water Temp **.******* 6           .7 o F Des ign Life ******************.*.***.*******.           40 years Transient Condition         Occurrences                         in
* IPEC00069619 4.000 GEOMETRY AND GENERAL CONFIGURATION I CQt1l'TIfIJI.  
: 1. Plant heatup at 100°F/Hr.         200
"?r>o }/t?W'lil/&  
: 2. Plant cooldown at 100°F/Hr.       200
..-SHELL locations This sketch shows the configuration and relati of component parts. The shown is used consis out this report. drawings of component Appendix C. Reference Drawings l'.llk 1. Control Rod Mechanism Housing Details E 232-051 2. Control Rod E 232-052 Penetration Details 3. Closure Head Form-E 232-046 ing 6. We lding 4. Closure Head Machining
: 3. Plant loading at 5% of           14,500 full power per min.
: 5. Stud, Nut 6. Washer Detail 6. Pressure Vessel Forming & Welding 7. Pressure Vessel Final Machining
: 4. Plant unloading at 5%           14,500                  4 4.2
: 8. Nozzle Details 9. Miscellaneous Attachments
* of full power per min.
: 10. Miscellaneous Details E-32-055 ll. Bottom Head E-2-043 Forming & Welding 12. Instrumentation Penet. Assembly 6. E-32-056 Details -Bottom Head 6 
: 5. Step load increase 10%           2,000 of full power - not to                                 4 4.3 exceed full power
* *
: 6. Step load decrease of             2,000                 4 lO~ from 50% power
* I PEC00069620 
: 7. Step load decrease of 200                 4 50% of full power
* *
: 8. Reactor trip 400
* IPEC00069621 5.000 5.010 SUm1ARY OF RESULTS Results of the detailed structural analysis in Appendix A are summarized on Pages 7 through /7 for locations of major interest.
: 9. Hydro test 3125 pSia
CONTROL ROD HOUSINGS Location -1 *Stresses Due to Operating Pressure of 2.25 KSI The maximum stress intensity for pressure is 09 -a r= 6.45 KSI on surface. The overall usage factor for Location -2 Stresses Due to Operating and Design Temperature of The maximum stress intensity for design pressure of 2.5 the design temperature of 650 0 F is /"Til -(Tr 25.6 KSI and located on the inside surface of the inconel tube The overall usage factor for fatigue was U O. o. 7 
: 10. Hydro test 2500 pSia                     5
* *
: 11. Steady state fluctuations               5 106
* I PEC00069622
: 12. Loss of flow, one pump
* Location -3 Stresses Due to Operating Pressure of 2.25 KSI Minimum Interference Fit with Closure Head The maximum stress intensity is "'x -(To '" 46.7 KSI and for the condition of maximum interference and zero pressure.
: 13. Loss of load                           80                     .8
This stress intensity is on the inside sur
: 14. Steam break                           80                    .9 5           See     27 Material Al1owlb1es           Sm @ 70°F   C: S/o                     ,:," ( (1'~
SA-240 Typ. 316                             J        Sm @ 5500 F 20.0 KSI     30/)
17 6 KSI          :",3 SA-102B                       26.7         ~u,o SA-J36                                                 26 7 26.7         4_;:;"     26 7 ASTM-A540-B24                 43.3         3JJ Inconel -                                             36 8
                              ,
23.3                     23 3
* IPEC00069617
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069618
 
RIV000052A Submitted: December 22, 2011 6
* 4.000 GEOMETRY AND GENERAL CONFIGURATION I
CQt1l'TIfIJI. "?r>o
                        }/t?W'lil/&               This sketch shows the o~n""'''l configuration and relati     locations of component parts. The shown is used consis out this report.
drawings of component Appendix C.
Reference Drawings l'.llk
: 1. Control Rod           E 232-051 Mechanism Housing Details
: 2. Control Rod           E 232-052 Penetration Details
: 3. Closure Head Form-   E 232-046 ing 6. We lding
        *
: 4. Closure Head Machining
: 5. Stud, Nut 6.
Washer Detail
                                          -~,..,
                                      ..-  SHELL
: 6. Pressure Vessel Forming & Welding
: 7. Pressure Vessel Final Machining
: 8. Nozzle Details
: 9. Miscellaneous Attachments
: 10. Miscellaneous         E- 32-055 Details ll. Bottom Head           E- 2-043 Forming & Welding
* 12. Instrumentation Penet. Assembly 6.
Details - Bottom Head E- 32-056 IPEC00069619
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069620
 
RIV000052A Submitted: December 22, 2011 7
* 5.000 SUm1ARY OF RESULTS Results of the detailed structural analysis pre~pnrpn in Appendix A are summarized on Pages 7 through /7 for locations of major interest.
5.010  CONTROL ROD HOUSINGS Location - 1
                                  *Stresses Due to Operating Pressure of 2.25 KSI The maximum stress intensity for pressure is 09 - a r = 6.45 KSI on
* surface.
The overall usage factor for                 o.
Location - 2 Stresses Due to Operating and Design Temperature of The maximum stress intensity for design pressure of 2.5 the design temperature of 6500 F is /"Til - (Tr ~ 25.6 KSI and
* located on the inside surface of the inconel tube The overall usage factor for fatigue was U       ~ O.
IPEC00069621
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069622
 
RIV000052A Submitted: December 22, 2011 8
* Location - 3 Stresses Due to Operating Pressure of 2.25 KSI Minimum Interference Fit with Closure Head The maximum stress intensity is "'x - (To '" 46.7 KSI and for the condition of maximum interference and zero pressure. This stress intensity is on the inside sur
* The maximum range of stress is 55.3 KSI and occurs on inside surface.
* The maximum range of stress is 55.3 KSI and occurs on inside surface.
* I PEC00069623 The overall usage factor for fatigue was U = 0.0003. l&caUon -4 The maximum stress intensity for the J-weld is 0x-0B KSI and occurs on the inside surface. The maximum stress intensity is 42.8 at the same location.
The overall usage factor for fatigue was     U = 0.0003.
The overall usage factor for. fatigue was U '" 0.06 and red on the outside surface
l&caUon - 4 The maximum stress intensity for the J-weld is 0x-     0B KSI and occurs on the inside surface. The maximum stress intensity is 42.8 at the same location.
*
The overall usage factor for. fatigue was   U '" 0.06 and   red on the outside surface *
* *
* IPEC00069623
* I PEC00069624 
 
* *
RIV000052A Submitted: December 22, 2011
* I PEC00069625 5.020 CLOSURE HEAD FLANGE AND SHELL Primary Stress Intensities Range of Stress Intensity The highest range of stress intensity for the head closure head juncture was located on the inside surface (Location  
                          *
-1). The value of this range of stress in is 50.4 KSI and compares favorably with the allowable 0 Fatigue Evaluation to The following overall usage factors were calculated at two above locations:
                            *
Location -1 U '" 0.004 Location -2 U '" 0.015 The maximum allowable usage factor is 1.0.
* IPEC00069624
* *
 
* I PEC00069626 
RIV000052A Submitted: December 22, 2011 9
* *
* 5.020   CLOSURE HEAD FLANGE AND SHELL Primary Stress Intensities Range of Stress Intensity
* IPEC00069627 5.030 VESSEL FLANGE AND SHELL Primary Stress Intensity 2 Range of Stress Intensity The highest range of stress intensity for the vessel vessel shell juncture was located on the inside surface (Location  
* The highest range of stress intensity for the head closure head juncture was located on the inside surface (Location - 1). The value of this range of stress in is 50.4 KSI and compares favorably with the allowable 0 to Fatigue Evaluation The following overall usage factors were calculated at   two above locations:
-l). The value of this range of stress is 45.4 KSI and compares favorably with the allowable of Fatigue EyaluatiQn The following overall usage factors were calculated at above locations:
Location - 1       U '" 0.004 Location - 2       U '" 0.015 The maximum allowable usage factor is 1.0.
Location -1 u 0.005 Location -2 u 0.00002 The maximum allowable usage factor is 1.0
* IPEC00069625
* 10 to ity 80 KSI. e two 
 
* *
RIV000052A Submitted: December 22, 2011
* I PEC00069628 
                          *
* * ** I PEC00069629 5.040 MAIN CLOSUJY; SIJ.!!2S j \
                          *
Stress; \ \ The average bolt stress \ from the design pressure \ \ \ load plus O-ring seat \ \ I , Z 34.4 KS!. The allowable , 34.8 KS!. \ "-\ \ \ The maximum average bolt \ stress for the bolt-up was 36.8 KSI compared to of 86.6 KS!. For the bo operating pressure cond! I 3 stress was 39.6 KSI j allowable of 73.5 KSI. , I The bolt , ,--I This occurred dur , / up cycle of the 2500 psi \ I \ / test. This stress \ I with the allowable of 1 \ I I I I L ...
* IPEC00069626
,--J EatiilUil Elliluation The maxUnum overall usage factor for the closure studs and occurred at the point where it enters the vessel f (Location  
 
-3). This usage factor compares favorably allowable of 1.0. MaxLffiurn Bearing Stress the The maximum bearing stress between the closure stud closure head flange was 39.8 KSI and compares with the of 40 KS! for the flange material.
RIV000052A Submitted: December 22, 2011 10
This value occurred during the heatup cycle of the 2500 psi hydrostatic test
* 5.030 VESSEL FLANGE AND SHELL Primary Stress Intensity 2
* 11 3
Range of Stress Intensity
* 0.313 
* The highest range of stress intensity for the vessel vessel shell juncture was located on the inside surface (Location - l ) . The value of this range of stress     ity to is 45.4 KSI and compares favorably with the allowable of 80 KSI.
* *
Fatigue EyaluatiQn The following overall usage factors were calculated at   e two above locations:
* I PEC00069630 
Location - 1     u 0.005 Location - 2     u 0.00002 The maximum allowable usage factor is 1.0 *
*
* IPEC00069627
* 5.050 INLET NOZZLE AND VESSEL SUPPORT Primary Membrane Stress Intensity The maximum average primary membrane stress intensity or the inlet nozzle was at the juncture of the nozzles to th wall on the longitudinal axis. The value of this stre intensity was 21.1 KSI and compares favorably with the able of KSI. The same location gave the highest value of average pr plus local primary stress. The value of this stress was 32.3 KSI and compares favorably with the allowable
 
: 1. 5 Sm = 40 KS 1. Range of Stress Intensity The highest range of stress intensity occurred at the of the nozzle to vessel wall on the outside surface in longitudinal direction.
RIV000052A Submitted: December 22, 2011
The value of this range of s intenSity was 45.5 KSI and compares favorably with the able of 80 KS!. Bearing Stress on Support Pad The bearing stress on the underside of the support pad Weight and thermal pipe reactions only was 3.0 KSI. was not to exceed 5.0 KSI for this condition.
                            *
Fatigue Evaluation uncture the ess allow-The maximum overall usage factor for the inlet nozzle U = 0.042 and occurred at the nozzle-vessel wall junct the outside surface in the circumferential direction.
                            *
* compares favorably with the allowable of 1.0. IPEC00069631 12 
* IPEC00069628
* *
 
* IPEC00069632
RIV000052A Submitted: December 22, 2011 11 5.040
* *
* MAIN CLOSUJY; SIJ.!!2S A2~~ag~ Bol~ Stress; j   \
* I PEC00069633 5.060 OUTLET NOZZLE AND VESSEL SUPPORT Primary Membrane Stress Intensity The maximum average primary membrane stress intensity r the outlet nozzle was at the juncture of the nozzLe to the vessel wall on the longitudinal axis. The value of this stre s intensity was 21.1 KSI and compares favorably with the able of 26.7 KSI. The same location gave the highest value of average plus local primary stress. TI1e value of this stress i was 32.3 KSI and compares favorably with the allowable 1.5 Sm = 40 KS!. Range of Stress Intensity The highest range of stress intensity Occurred at the of the nozzle to vessel wall on the outside surface in longitudinal direction.
                \          \
The value of this range of s intensity was 45.5 KSI and compares favorably with the able of 80 KSI. Bearing Stress on Support Pad The bearing stress on the underside of the support pad weight and thermal pipe reactions only was 3.6 KSI. was not to exceed 5.0 KSI for this condition.
                  \
Fatigue Eyaluation The maximum overall usage factor for the outlet nozzle U = 0.022 and Occurred at the nozzle-vesseL juncture on inside surface in the longitudinal direction.
The average bolt stress
This val compares favorably with the allowable of U = 1.0. y 13 
                                    \                                           from the design pressure
* *
                                        \
* I PEC00069634 
                      \
* *
                        ,                \
* I PEC00069635 5.070 VESSEL WALL TRANSITION 3---I I I I Range of Stress Intensity The maximum average pr stress intensity for transition occurs in of the vessel wall. stress intensity was compares favorably with th stress intensity of 26.7 The highest range of streSS intensity Occurred at Locat shown above.* The value of this range of stress intensi KSI and compares favorably with the allowable of 80 KSI Fatigue Evaluation The maximum overall usage factor for the vessel wall U 0.002 and occurredat Location -2 as shown above. compares favorably with the allowable of U 1.0. in portion lue of this I and allowable
                                              \ I
: 1. -1 as was 37.9 ition was is value 14 
                                                ,                          Z load plus O-ring seat 34.4 KS!. The allowable 34.8 KS!.
* *
                          \                       "-
* I PEC00069636 
                            \
*
                              \
* IPEC00069637 15 5.080 CORE BARREL SUPPORT PADS. A ) ),) ) )))) r (' ( ( ( ( ( 1 ( ( r r (' ( ( ( (' / r y Stresses Due to Steady Loads The most critical streSs intensity for the side load and steady 125 KIP vertical load (due o-r ,[lW ,-n ) occurred at the vessel wall (Location -Y as shown value of this stress intensity was 31.1 KSI and with the allowable of 35 KSI. Range of Stress Intensitx The highest range of stress intensity occured at Locat as shown above. The value of this range of stress in 40.8 KSI and compares favorably with the allowable of Fatigue Evaluation The fatigue evaluation disclosed that the highest factor for the pads was 0.02 and occurred at the upper of the pad at the pad-to-vessel juncture Location -A. value compares favorably with the allowable of U 0: 1.0 The favorably -c ity was 9.9 KSI. -I 
                                \                                             The maximum average bolt
* *
                                \                                             stress for the bolt-up was 36.8 KSI compared to of 86.6 KS!. For the bo operating pressure cond!
* I PEC00069638 
I                                           stress was 39.6 KSI
* *
                                  ,
* IPEC00069639 5.090 BOTTOM HEADTa SHELL JUNCTURE I z f Range of Stress Intensity The maximum average primar stress intensity for the bo to shell juncture occurs in cylindrical shell portion 0 juncture.
j
The value of th intensity was 26.3 KSI and favorably with the allowabl 26.7 KSI. The highest range of stress intensity occurred at Loca as shown above. The value of this range of stress 34.1 KSI and compares favorably to the allowable range intensity of 80 KSI
                                    ~T-3                          allowable of 73.5 KSI.
* Eyaluation The fatigue evaluation disclosed that the highest over factor for the bottom head to shell juncture was 0.003 ion -3 nsity was of stress occurred at Location -3 as shown above. This value es favorably with the allowable of U = 1.0
          *                      ,--,
* 16 
I                                 The         bolt 3*
* *
I     This stre~s occurred dur
* I PEC00069640 
                                ,
*
                                  \                                  I
* IPEC00069641 5.100 ftOTIQM HEAD INSTRUMENTATlOH PENETRATIONS Range of Stress Intensity The maximum average membrane stress in in the bottom head into consideration efficiency.
                                                                      /       up cycle of the 2500 psi
The va stress intensity is and compares favora the allowable of 26. The highest range of stress intensity occurred on the surface of the tube -Location -1 as shown above. The of this range of stress intenSity is 53.9 KSI and with the allowable of 69.9 KSI. Fatigue Eya1 ua tion The fatigue evaluation disclosed that the highest overa factor for the bottom head instrumentation was 0.14 and on the outside surface of the tube -Location -2 as The value compares favorably with the allowable of U imary sity occurs en taking ligament of the .5 KSI Y with KSI. 17 
                                      \
* *
                                        \
* IPEC00069642
                                                                  /           test. This stress I
* *
                                          \
* I PEC00069643 6.000 DISCUSSION OF RESULTS & METHOD OF ANALYSIS 6.010 Control Rod HoUSinis A. Discussion of Results Location -1 For the juncture of the CRDM flange to tube, stress intensity for design pressure is 7.2 KSI occurs on the inside surface. The allowable 304 stainless steel at the design temperature Sm 23 KSI. Location -2 For the 304 stainless steel at the bi-metallic maximum primary plus secondary stress intensity KSI on the inside surface. This stress intens for the design temperature and pressure.
I             with the allowable of 1 I
For t conditions, the maximum range of stress intensi KSI and compares favorably with the allowable 0 45.9 KS!. . For the inconel portion of the tube, the max intensity for the design conditions occurred on surface. The value of this stress intensity wa For the operating transients, the maximum range intensity was 21.8 KSI and compares favorably wi allowable of 3 Sm 69.9 KS!. Location -3 At the point where the CRDM housing enters the c head, stresses are induced in the tube at zero due to the interference fit. The stress intens maximum interference and zero pressure is 46.7 stress the the operating transients, the maximum range of s ss intensity was 55.3 KSI and compares favorably wi the allowable of 3 Sm c 69.9 KSr. The fatigue evaluation revealed that the highest cumulative usage factor was 0.0003 for the inside surface. This pares favorably with the allowable of 1.0
I I
* 18 
L. .-"""\_/,-~- ,--J EatiilUil Elliluation The maxUnum overall usage factor for the closure studs                                           0.313 and occurred at the point where it enters the vessel f (Location - 3). This usage factor compares favorably                                         the allowable of 1.0.
* *
MaxLffiurn Bearing Stress The maximum bearing stress between the closure stud closure head flange was 39.8 KSI and compares with the of 40 KS! for the flange material. This value occurred during
* IPEC00069644
        **
* *
the heatup cycle of the 2500 psi hydrostatic test
* IPEC00069645 Location -4 At the location where the CRDM housing is at the closure head by the J-weld, the maximum stress intensity is 42.8 KSI and compares fa with the allowable of 3 8m = 69.9 KSI. This of stress intensity occurs on the inside sur From the standpoint of fatigue, the most crit location will be on the outside portion of the where a stress concentration factor of four was The cumulative usage factor at this location and compares favorably with the allowable of 1. B. Method of Analysis Location -1 An interaction analysis was performed at the CRDM housing flange to be a ring and cylinder.
* IPEC00069629
Location -2 An interaction analysis was performed at cut into consideration that elements 2 and 3 are 10 having different values of Young's Modulus of E and coefficients of thermal expansion.
 
Location -3 An interaction analysis was performed at cut th taking the housing as a cylinder and setting equal to the deflection of the radius of the tration and conservatively assuming its rotat to the local flexibility as if it were solidly It was assumed that the forces exerted on the h tube have negligible effect on the head. Location -4 An interaction analysis was performed by divid actual structure into the following analytical closure head was treated as a perforated spheri with modified elastic constants and the CRDM h long cylinder.
RIV000052A Submitted: December 22, 2011
The effects of the redundants head were assumed to be local only
                          *
* assuming e a long taking cylinders sticity ee by deflection d equal ttached. by the shell 19 
                            *
* *
* IPEC00069630
* I PEC00069646 
 
* *
RIV000052A Submitted: December 22, 2011 12
* IPEC00069647 for. any condition wpere there is interference the tube and head, no bending at the weld can Using mechanical and thermal stresses from th a fatigue evaluation was made for the J-weld. 6.020 CLOSUllE HEAD FLANGE AND SHELL A. Discussion of Results tween ist. analysis, The maximum primary stress intensity at the ClnHIITP flange to shell juncture was 35.8 KSI for the plus design pressure condition.
* 5.050 INLET NOZZLE AND VESSEL SUPPORT Primary Membrane Stress Intensity The maximum average primary membrane stress intensity or the inlet nozzle was at the juncture of the nozzles to th wall on the longitudinal axis. The value of this stre intensity was 21.1 KSI and compares favorably with the able of 2~.7 KSI.
This stress the outside surface of the juncture of the head and compares favorably with the allowable of 1. 40 .KSI. The highest range of stress intensity for this 50.4 KSI on the inside surface and compares fa the allowable of 3 Sm = 80 KEI. The fatigue evaluation revealed that the higbes usage factor was 0.015 and occurred for the out This value compares favorably with the allowab B. Method of Analysis The closure head, closure head flange, vessel f vessel shell, and closure studs were all evalua same analysis.
The same location gave the highest value of average pr
The actual structure was di following elements:
* plus local primary stress. The value of this stress was 32.3 KSI and compares favorably with the allowable
the closure head dome was a long sphere, the closure head flange was trea ring, the vessel flange and studs were combined element with the flange treated as a ring and as cantilever beams fixed to the flange, and the shell was treated as a long cylinder.
: 1. 5 Sm = 40 KS 1.
Using the above described analytical model, an analysis was performed to determine the stresses the mechanical and thermal loadings for tbe h cooldown cycle. For the remaining transients, servative skin stress method was used for de thermal stresses.
Range of Stress Intensity The highest range of stress intensity occurred at the   uncture of the nozzle to vessel wall on the outside surface in the longitudinal direction. The value of this range of s   ess intenSity was 45.5 KSI and compares favorably with the allow-able of 80 KS!.
These stresses were evaluated of the strength and fatigue requirements of the Boiler and Pressure Vessel Code, Section III . s on to flange the the as 20 
Bearing Stress on Support Pad The bearing stress on the underside of the support pad Weight and thermal pipe reactions only was 3.0 KSI.
* *
was not to exceed 5.0 KSI for this condition.
* I PEC00069648 
Fatigue Evaluation The maximum overall usage factor for the inlet nozzle U = 0.042 and occurred at the nozzle-vessel wall junct the outside surface in the circumferential direction.
* *
* compares favorably with the allowable of 1.0.
* IPEC00069649 6.030 VESSEL FLANGE AND SHELL A. Discussion of Results The maxtffium primary stress intensity at the flange to vessel shell juncture was 28.8 KSI boltup plus design pressure condition.
IPEC00069631
This occurred on the outside surface of the junc flange to vessel shell and compares favorably allowable of 1.5 Sm 40 KSI. The highest range of stress intensity was 45.4 KSI on the inside surface and with the allowable of 3 8m = 80 KSI. The fatigue evaluation revealed that the h tive usage factor was 0.005 and occurred for surface. This value compareS favorably with of 1.0. juncture s favorably cumula-e inside allowable B. Method of Analysis See Section 6.020-B, Method of Analysis, CIa Head Flange and Shell
 
* 6.040 MAIN CLOSURE STUDS A. Discussion of Results The maximum average bolt service stress for boltup condition was 3608 KS! and compares with the allowable of 2 Sm = 86.6 KSL For." plus operating pressure, the average bolt serv is 39.6 KSI and compares favorably with the al 2 Sm = 73.5 KS! at temperature.
RIV000052A Submitted: December 22, 2011
The maximum bolt service stress was 95.9 KS! stress ble of on the inside surface of the stud where it ent vessel flange. This stress occurred during th cycle of the 2500 PSI hydrostatic test and favorably with the allowable of 3 3m = 116.4 A fatigue evaluation was performed on the stud the method outlined in Para. N-416.2 of the and Pressure Vessel Code, Section Ill. The cumulative usage factor for the studs was 0.31 inside surface of the stud where it enters the flange. The allowable usage factor is 1.0. 21 
                            *
* *
                            *
* I PEC00069650 
* IPEC00069632
* *
 
* IPEC00069651 The maximum bearing stress between the closure tud washers and closure head flange was 39,3 KSI. is stress occurred during the heatup cycle of the 500 PSI hydrostatic test and compares favorably wit the allowable of 1.5 Sm for the flange material.
RIV000052A Submitted: December 22, 2011 13
B. Method of Analysis See Section 6.020-B, Method of Analysis, Closur Head Flange and Shell. 6.050 INLET NOZZLE AND VESSEL SUPPORTS A. Discussion of Results The maximum average primary membrane stress int the inlet nozzle occurred at the juncture of the to the vessel wall on the LongitUdinal axis. Th of this stress intensity was 21.1 KS! and co ably with the allowable of 26.7 KSI. The same location gave the highest value plus local primary stress. The value of sity was 32.3 KSI and compares favorably of 1.5 Sm 40 KSI . The highest range of stress intensity for the op transients occurred at the juncture of the nozzl wall on the outside surface in the longitudinaL The value of this range of stress intensity was and compares favorably with the allowable of 80 22 for The bearing stress on the underside of the supp dead weight and the thermal pipe reactions only This stress was to be limited to 5.0 KS! under th condition.
* 5.060 OUTLET NOZZLE AND VESSEL SUPPORT Primary Membrane Stress Intensity The maximum average primary membrane stress intensity   r the outlet nozzle was at the juncture of the nozzLe to the vessel wall on the longitudinal axis. The value of this stre s intensity was 21.1 KSI and compares favorably with the allow-able of 26.7 KSI.
B. TI1e fatigue evaluation revealed that the highest usage factor was 0.042 and occurred at the nozzle wall juncture on the outside surface in the cir direction.
The same location gave the highest value of average
This value compares favorably with th able of 1.0. The cumulative usage factor through nozzle wall and weld built-up support pad was fa 0.007 on the outside surface of the pad. Method of Analysis to be For the analysis of the nozzle and nozzle to shel juncture, the loads conSidered were internal pressure, oper ting Sients, thermally induced and seismic pipe react ,static
* y plus local primary stress. TI1e value of this stress i was 32.3 KSI and compares favorably with the allowable 1.5 Sm = 40 KS!.
* *
Range of Stress Intensity The highest range of stress intensity Occurred at the of the nozzle to vessel wall on the outside surface in longitudinal direction. The value of this range of s intensity was 45.5 KSI and compares favorably with the able of 80 KSI.
* IPEC00069652
Bearing Stress on Support Pad The bearing stress on the underside of the support pad weight and thermal pipe reactions only was 3.6 KSI.
*
was not to exceed 5.0 KSI for this condition.
* 6.060 A.
Fatigue Eyaluation The maximum overall usage factor for the outlet nozzle U = 0.022 and Occurred at the nozzle-vesseL juncture on
* I PEC00069653 weight of vessel, earthquake loading, and and contraction
* inside surface in the longitudinal direction. This val compares favorably with the allowable of U = 1.0.
* The stresses resulting determined in the nozzle by the use of the st formula for direct stress plus bending stress beam. At the juncture of the nozzle to vessel these stresses were determined by the methods in references 19, 20, and 21. The pressure stresses were determined in the performing an interaction analysis.
IPEC00069633
The was divided into the following elements:
 
of the nozzle was treated as a cylinder, was treated as a tapered cylinder, the reinfor was treated as a cylinder, and the vessel was idealizing it as a spherical segment of the as the vessel and with a mid-radius 1.5 times radius of the vessel. The thermal stresses for the operating transie determined by performing an interaction with analytical model . For the fatigue evaluation, pressure stresses ed by the stress index method set forth in Art the ASME Boiler and Pressure Vessel Code, Sect Peak stresses resulting from the external load thermal transients were determined by concentr stresses as determined by the above described Combining these stresses enabled the fatigue e to be performed.
RIV000052A Submitted: December 22, 2011
OUTLET NOZZLE AND VESSEL SUPPORT Discussion of Results The maximum average primary membrane stress int the outlet nozzle occurred at the juncture of th to the vessel wall on the longitudinal axis. of this intensity Was 21.1 KSI and campa ably with the allowable of 26.7 KSI. The same location gave the highest value of a primary plus local primary stress. The value 0 stress intensity was 32.3 KSI and compares fa with the allowable of 1.5 Sm : 40 KSI
                          *
* n a wall, resented structure 23 in portion pered portion portion eated by th ickness actual ity for nozzle 
                          *
* *
* IPEC00069634
* I PEC00069654 
 
* *
RIV000052A Submitted: December 22, 2011 14
* I PEC00069655 The highest range of stress intensity for the transients occurred at the juncture of the n02Z wall on the outside surface in the longitudinal The value of this range of stress intensity was and compares favorably with the allowable of 80 The bearing stress on the underside of the the dead weight and the thermal pipe reactions 3.6 KSI. This stress was to be limited to 5.0 this condition.
* 5.070   VESSEL WALL TRANSITION The maximum average pr stress intensity for transition occurs in       in portion of the vessel wall.       lue of this stress intensity was       I and 3---    I I ~4          compares favorably with th allowable stress intensity of 26.7   1.
rating to vessel for y was I under cumulative
I I
(' to vesse t tudinal 24 The fatigue evaluation revealed that the highes usage factor was 0.022 and occurred at the nozz wall juncture on the inside surface in the long direction.
Range of Stress Intensity
This value compares favorably with of 1.0. The cumulative usage factor through wall and the weld built-up support pad was 0.011 on the outside surface of the pad. e allowable nozzle B. Method of Analysis See Section 6.050, Method of Analysis, Inlet Vessel Supports for the method of analysis.
* The highest range of streSS intensity Occurred at Locat shown above.* The value of this range of stress intensi KSI and compares favorably with the allowable of 80 KSI Fatigue Evaluation
6.070 VESSEL WALL TRANSITION A. Discussion of Results The maximum average primary stress intensity for wall transition occurs in the thin portion of th wall. The value of this stress intensity is 26. compares favorably with the Sm value of 26.7 KSI The highest range of stress intensity for the transients occurred on inside surface at the the taper. The value of this range of stress was 37.9 KSI and compares favorably with the al 3 8m = 80 KSI. to be Ie and the vessel vesse 1 KSI and ating end of ensity able of The fatigue evaluation revealed that the highest cumulative usage factor was 0.002 and occurred on the outs e surface at the large end of the taper. This value is we 1 below the allowable of L.O. B. Method of Analysis Stresses due to internal pressure were determ of a standard interaction analysis.
                                                                            - 1 as was 37.9 The maximum overall usage factor for the vessel wall         ition was U ~ 0.002 and occurredat Location - 2 as shown above.       is value compares favorably with the allowable of U ~ 1.0.
For the pur this analysis, the actual structure was divided by means se of to 
* IPEC00069635
* *
 
* I PEC00069656 
RIV000052A Submitted: December 22, 2011
* *
                          *
* IPEC00069657 the following elements:
                            *
the thick portion of was treated as a cylinder, the tapered portion treated as a short tapered cylinder, and the th of the vessel wall was treated as a long cyl The thermal stresses were determined by the s method where it is assumed that the inside sur the vessel is at the same temperature-as the r coolant and the mean temperature of the shell the state temperature.
* IPEC00069636
This method conservative.
 
RIV000052A Submitted: December 22, 2011 15
* 5.080   CORE BARREL SUPPORT PADS.
A
                    ) ),) )           ))))
r                   ('
(
(
( ( (                   ( ( r     r 1
(
('
(
(                   ('                                       -I
                              /                 r y
Stresses Due to Steady Loads The most   critical streSs intensity for the                       side
* load and occurred value of with the steady 125 KIP vertical load (due at the vessel wall (Location - Y as shown o-r ,[lW ,- n )
this stress intensity was 31.1 KSI and COlmp<lr~ favorably allowable of 35 KSI.
Range of Stress Intensitx The The highest range of stress intensity occured at Locat             - c as shown above. The value of this range of stress in             ity was 40.8 KSI and compares favorably with the allowable of 9.9 KSI.
Fatigue Evaluation The fatigue evaluation disclosed that the highest factor for the pads was 0.02 and occurred at the upper of the pad at the pad-to-vessel juncture Location - A.
value compares favorably with the allowable of U 1.0 0:
IPEC00069637
 
RIV000052A Submitted: December 22, 2011
                          *
                          *
* IPEC00069638
 
RIV000052A Submitted: December 22, 2011 16 5.090   BOTTOM HEADTa SHELL JUNCTURE
* The maximum average primar stress intensity for the bo I          z        to shell juncture occurs in cylindrical shell portion 0 juncture. The value of th intensity was 26.3 KSI and ~VlllU<'Les favorably with the allowabl 26.7 KSI.
f Range of Stress Intensity The highest range of stress intensity occurred at Loca ion - 3 as shown above. The value of this range of stress       nsity was 34.1 KSI and compares favorably to the allowable range of stress
* intensity of 80 KSI
* Fatigu~  Eyaluation The fatigue evaluation disclosed that the highest over factor for the bottom head to shell juncture was 0.003 occurred at Location - 3 as shown above. This value           es favorably with the allowable of U = 1.0 *
* IPEC00069639
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069640
 
RIV000052A Submitted: December 22, 2011 17
* 5.100 ftOTIQM HEAD INSTRUMENTATlOH PENETRATIONS The maximum average   imary membrane stress in   sity occurs in the bottom head   en taking into consideration     ligament efficiency. The va     of the stress intensity is   .5 KSI and compares favora Y with the allowable of 26. KSI.
Range of Stress Intensity
* The highest range of stress intensity occurred on the surface of the tube - Location - 1 as shown above. The of this range of stress intenSity is 53.9 KSI and with the allowable of 69.9 KSI.
Fatigue Eya1 ua tion The fatigue evaluation disclosed that the highest overa factor for the bottom head instrumentation was 0.14 and on the outside surface of the tube - Location - 2 as The value compares favorably with the allowable of U ~
IPEC00069641
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069642
 
RIV000052A Submitted: December 22, 2011 18 6.000 DISCUSSION OF RESULTS & METHOD OF ANALYSIS
* 6.010 Control Rod HoUSinis A. Discussion of Results Location - 1 For the juncture of the CRDM flange to tube, stress intensity for design pressure is 7.2 KSI occurs on the inside surface. The allowable 304 stainless steel at the design temperature         Sm 23 KSI.
Location - 2 For the 304 stainless steel at the bi-metallic maximum primary plus secondary stress intensity KSI on the inside surface. This stress intens for the design temperature and pressure. For t conditions, the maximum range of stress intensi KSI and compares favorably with the allowable 0 45.9 KS!.                 .
* For the inconel portion of the tube, the max intensity for the design conditions occurred on surface. The value of this stress intensity wa For the operating transients, the maximum range intensity was 21.8 KSI and compares favorably wi allowable of 3 Sm ~ 69.9 KS!.
stress the Location - 3 At the point where the CRDM housing enters the c head, stresses are induced in the tube at zero due to the interference fit. The stress intens maximum interference and zero pressure is 46.7 the operating transients, the maximum range of s   ss intensity was 55.3 KSI and compares favorably wi   the allowable of 3 Sm c 69.9 KSr.
The fatigue evaluation revealed that the highest cumulative usage factor was 0.0003 for the inside surface. This com-pares favorably with the allowable of 1.0 *
* IPEC00069643
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069644
 
RIV000052A Submitted: December 22, 2011 19 Location - 4
* At the location where the CRDM housing is at the closure head by the J-weld, the maximum stress intensity is 42.8 KSI and compares fa with the allowable of 3 8m = 69.9 KSI. This of stress intensity occurs on the inside sur From the standpoint of fatigue, the most crit location will be on the outside portion of the where a stress concentration factor of four was The cumulative usage factor at this location and compares favorably with the allowable of 1.
B. Method of Analysis Location - 1 An interaction analysis was performed at         assuming the CRDM housing flange to be a ring and       e a long cylinder.
Location - 2
* An interaction analysis was performed at cut into consideration that elements 2 and 3 are 10 having different values of Young's Modulus of E and coefficients of thermal expansion.
taking cylinders sticity Location - 3 An interaction analysis was performed at cut th ee by taking the housing as a cylinder and setting     deflection equal to the deflection of the radius of the   d pene-tration and conservatively assuming its rotat   equal to the local flexibility as if it were solidly ttached.
It was assumed that the forces exerted on the h   by the tube have negligible effect on the head.
Location - 4 An interaction analysis was performed by divid actual structure into the following analytical         ~e closure head was treated as a perforated spheri   shell with modified elastic constants and the CRDM h long cylinder. The effects of the redundants
* head were assumed to be local only
* IPEC00069645
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069646
 
RIV000052A Submitted: December 22, 2011 20
* for. any condition wpere there is interference the tube and head, no bending at the weld can Using mechanical and thermal stresses from th a fatigue evaluation was made for the J-weld.
tween ist.
analysis, 6.020 CLOSUllE HEAD FLANGE AND SHELL A. Discussion of Results The maximum primary stress intensity at the ClnHIITP flange to shell juncture was 35.8 KSI for the plus design pressure condition. This stress       s on the outside surface of the juncture of the head to flange and compares favorably with the allowable of 1. Sm~
40 .KSI.
The highest range of stress intensity for this 50.4 KSI on the inside surface and compares fa the allowable of 3 Sm = 80 KEI.
The fatigue evaluation revealed that the higbes
* usage factor was 0.015 and occurred for the out This value compares favorably with the allowab B. Method of Analysis The closure head, closure head flange, vessel f vessel shell, and closure studs were all evalua         the same analysis. The actual structure was di             the following elements: the closure head dome was           as a long sphere, the closure head flange was trea ring, the vessel flange and studs were combined element with the flange treated as a ring and as cantilever beams fixed to the flange, and the shell was treated as a long cylinder.
Using the above described analytical model, an analysis was performed to determine the stresses the mechanical and thermal loadings for tbe h cooldown cycle. For the remaining transients, servative skin stress method was used for de thermal stresses. These stresses were evaluated of the strength and fatigue requirements of the
* Boiler and Pressure Vessel Code, Section III .
IPEC00069647
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069648
 
RIV000052A Submitted: December 22, 2011 21 6.030 VESSEL FLANGE AND SHELL
* A. Discussion of Results The maxtffium primary stress intensity at the flange to vessel shell juncture was 28.8 KSI boltup plus design pressure condition. This occurred on the outside surface of the junc flange to vessel shell and compares favorably allowable of 1.5 Sm ~ 40 KSI.
The highest range of stress intensity           juncture was 45.4 KSI on the inside surface and         s favorably with the allowable of 3 8m = 80 KSI.
The fatigue evaluation revealed that the h       cumula-tive usage factor was 0.005 and occurred for   e inside surface. This value compareS favorably with       allowable of 1.0.
B. Method of Analysis See Section 6.020-B, Method of Analysis, CIa     Head Flange and Shell *
* 6.040 A.
MAIN CLOSURE STUDS Discussion of Results The maximum average bolt service stress for boltup condition was 3608 KS! and compares with the allowable of 2 Sm = 86.6 KSL For."
plus operating pressure, the average bolt serv     stress is 39.6 KSI and compares favorably with the al     ble of 2 Sm = 73.5 KS! at temperature.
The maximum bolt service stress was 95.9 KS!
on the inside surface of the stud where it ent vessel flange. This stress occurred during th cycle of the 2500 PSI hydrostatic test and cam~ares favorably with the allowable of 3 3m = 116.4 A fatigue evaluation was performed on the stud the method outlined in Para. N-416.2 of the and Pressure Vessel Code, Section Ill. The cumulative usage factor for the studs was 0.31
* inside surface of the stud where it enters the ~essel flange. The allowable usage factor is 1.0.
IPEC00069649
 
RIV000052A Submitted: December 22, 2011
                            *
                            *
* IPEC00069650
 
RIV000052A Submitted: December 22, 2011 22 The maximum bearing stress between the closure tud
* washers and closure head flange was 39,3 KSI. is stress occurred during the heatup cycle of the 500 PSI hydrostatic test and compares favorably wit the allowable of 1.5 Sm for the flange material.
B. Method of Analysis See Section 6.020-B, Method of Analysis, Closur Head Flange and Shell.
6.050     INLET NOZZLE AND VESSEL SUPPORTS A. Discussion of Results The maximum average primary membrane stress int       for the inlet nozzle occurred at the juncture of the to the vessel wall on the LongitUdinal axis. Th of this stress intensity was 21.1 KS! and co ably with the allowable of 26.7 KSI.
The same location gave the highest value plus local primary stress. The value of
* sity was 32.3 KSI and compares favorably of 1.5 Sm ~ 40 KSI .
The highest range of stress intensity for the op transients occurred at the juncture of the nozzl wall on the outside surface in the longitudinaL The value of this range of stress intensity was and compares favorably with the allowable of 80 The bearing stress on the underside of the supp dead weight and the thermal pipe reactions only This stress was to be limited to 5.0 KS! under th   condition.
TI1e fatigue evaluation revealed that the highest usage factor was 0.042 and occurred at the nozzle wall juncture on the outside surface in the cir direction. This value compares favorably with th able of 1.0. The cumulative usage factor through nozzle wall and weld built-up support pad was fa     to be 0.007 on the outside surface of the pad.
B. Method of Analysis
* For the analysis of the nozzle and nozzle to shel juncture, the loads conSidered were internal pressure, oper ting tran-Sients, thermally induced and seismic pipe react     ,static IPEC00069651
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069652
 
RIV000052A Submitted: December 22, 2011 23
* weight of vessel, earthquake loading, and and contraction
* The stresses resulting determined in the nozzle by the use of the st formula for direct stress plus bending stress n a beam. At the juncture of the nozzle to vessel wall, these stresses were determined by the methods resented in references 19, 20, and 21.
The pressure stresses were determined in the performing an interaction analysis. The         structure was divided into the following elements:         in portion of the nozzle was treated as a cylinder,       pered portion was treated as a tapered cylinder, the reinfor         portion was treated as a cylinder, and the vessel was     eated by idealizing it as a spherical segment of the       th ickness as the vessel and with a mid-radius 1.5 times       actual radius of the vessel.
The thermal stresses for the operating transie determined by performing an interaction with analytical model .
* For the fatigue evaluation, pressure stresses ed by the stress index method set forth in Art the ASME Boiler and Pressure Vessel Code, Sect Peak stresses resulting from the external load thermal transients were determined by concentr stresses as determined by the above described Combining these stresses enabled the fatigue e to be performed.
6.060 OUTLET NOZZLE AND VESSEL SUPPORT A. Discussion of Results The maximum average primary membrane stress int     ity for the outlet nozzle occurred at the juncture of th   nozzle to the vessel wall on the longitudinal axis.
of this str~ss intensity Was 21.1 KSI and campa ably with the allowable of 26.7 KSI.
The same location gave the highest value of a primary plus local primary stress. The value   0
* stress intensity was 32.3 KSI and compares fa with the allowable of 1.5 Sm : 40 KSI
* IPEC00069653
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069654
 
RIV000052A Submitted: December 22, 2011 24 The highest range of stress intensity for the     rating
* transients occurred at the juncture of the n02Z wall on the outside surface in the longitudinal The value of this range of stress intensity was and compares favorably with the allowable of 80 The bearing stress on the underside of the to vessel for the dead weight and the thermal pipe reactions       y was 3.6 KSI. This stress was to be limited to 5.0     I under this condition.
The fatigue evaluation revealed that the highes cumulative usage factor was 0.022 and occurred at the nozz (' to vesse t wall juncture on the inside surface in the long tudinal direction. This value compares favorably with     e allowable of 1.0. The cumulative usage factor through     nozzle wall and the weld built-up support pad was         to be 0.011 on the outside surface of the pad.
B. Method of Analysis See Section 6.050, Method of Analysis, Inlet     Ie and Vessel Supports for the method of analysis.
* 6.070 VESSEL WALL TRANSITION A. Discussion of Results The maximum average primary stress intensity for the vessel wall transition occurs in the thin portion of th vesse 1 wall. The value of this stress intensity is 26. KSI and compares favorably with the Sm value of 26.7 KSI The highest range of stress intensity for the       ating transients occurred on inside surface at the         end of the taper. The value of this range of stress     ensity was 37.9 KSI and compares favorably with the al     able of 3 8m = 80 KSI.
The fatigue evaluation revealed that the highest cumulative usage factor was 0.002 and occurred on the outs e surface at the large end of the taper. This value is we 1 below the allowable of L.O.
B. Method of Analysis
* Stresses due to internal pressure were determ of a standard interaction analysis. For the pur this analysis, the actual structure was divided by means se of to IPEC00069655
 
RIV000052A Submitted: December 22, 2011
                          *
                          *
* IPEC00069656
 
RIV000052A Submitted: December 22, 2011 25
* the following elements: the thick portion of was treated as a cylinder, the tapered portion treated as a short tapered cylinder, and the th of the vessel wall was treated as a long cyl The thermal stresses were determined by the s method where it is assumed that the inside sur the vessel is at the same temperature-as the r coolant and the mean temperature of the shell the ~teady state temperature. This method conservative.
The fatigue evaluation was made on a where superposition of all transients consideration.
The fatigue evaluation was made on a where superposition of all transients consideration.
6.080 CORE BARREL SUPPORT PADS A. Dis.cussion of Results The most critical stress intensity occurred for 125 KIP side load and steady 125 KIP vertical stress intensity of 31.1 KSI occurred at the corner of the juncture of the pad to the compares favorably with the allowable of The highest range of stress intensity occurred upper outside corner of the juncture of the pad wall. The value of this range of stress intens 40.8 KSI and compares favorably with the 3 3m of 69.9 KS!. The fatigue evaluation revealed that the highes usage factor was 0.02 and occurred at the upper corner of the juncture of the pad to vessel wal
6.080 CORE BARREL SUPPORT PADS A. Dis.cussion of Results The most critical stress intensity occurred for   e steady 125 KIP side load and steady 125 KIP vertical       This stress intensity of 31.1 KSI occurred at the
* value is well below the allowable of 1.0. B. Method of Analysis Thermal, mechanical, and pressure stresses at various locations on the pad and at the for the loads specified in reference
* corner of the juncture of the pad to the compares favorably with the allowable of The highest range of stress intensity occurred upper outside corner of the juncture of the pad wall. The value of this range of stress intens 40.8 KSI and compares favorably with the 3 3m of 69.9 KS!.
: 10. Mechanical stresses were calculated by the for bending stress in a beam, pressure stresses from the analysis of the vessel to bottom head j and thermal stresses were determined by the e steady This taken 25 
The fatigue evaluation revealed that the highes usage factor was 0.02 and occurred at the upper corner of the juncture of the pad to vessel wal
* *
* value is well below the allowable of 1.0.
* I PEC00069658 
B. Method of Analysis Thermal, mechanical, and pressure stresses at various locations on the pad and at the for the loads specified in reference 10.
"' *
Mechanical stresses were calculated by the for bending stress in a beam, pressure stresses     taken
* IPEC00069659 6.090 "method of skin stresses.
* from the analysis of the vessel to bottom head j and thermal stresses were determined by the IPEC00069657
These stresses were into stress intensities and compared with the set forth in reference  
 
-/. Stresses due to the loads were multiplied"by a stress concentratio where applicable and used in a fatigue evaluat BOTTOM HEAD TO SHELL JUNCTURE A. Discussion of Results The maximum average primary stress intensity bottom head to shell juncture occurs in the cy shell portion of the juncture.
RIV000052A Submitted: December 22, 2011
The value of stress intensity is 26-.3 KSI and compares fa with the Sm value of 26.7 KSI. The highest range of stress intensity for transients occurred on the inside surface of the hemispherical shell. The value of stress intensity was 34.1 KSI and the allowable of 3 Sm 80 KSI. The fatigue evaluation revealed that the high usage factor was 0.003 and occurred on the ins at the start of the hemispherical shell. This well below the allowable of 1.0. B. Method of Analysis Stresses due to internal pressure Were de of a standard interaction ana.lysis.
                            *
this analysis, the actual structure was divided following elements:
                            *
the cylindrical shell was as a long cylinder, the tapered portion of the shell tvas treated as a short tapered cylinder, hemispherical section was treated as a long sph shell. The thermal stresses were determined by the sk method it is assumed that the inside sur vessel is at the same temperature as the and the mean temperature of the shell remains steady state temperature.
* IPEC00069658
This method is cons conservative.
 
RIV000052A Submitted: December 22, 2011 26 "method of skin stresses. These stresses were
        *"'
6.090 into stress intensities and compared with the set forth in reference -/. Stresses due to the loads were multiplied"by a stress concentratio where applicable and used in a fatigue evaluat BOTTOM HEAD TO SHELL JUNCTURE A. Discussion of Results The maximum average primary stress intensity bottom head to shell juncture occurs in the cy shell portion of the juncture. The value of stress intensity is 26-.3 KSI and compares fa with the Sm value of 26.7 KSI.
The highest range of stress intensity for transients occurred on the inside surface of the hemispherical shell. The value of stress intensity was 34.1 KSI and the allowable of 3 Sm ~ 80 KSI.
The fatigue evaluation revealed that the high usage factor was 0.003 and occurred on the ins
* at the start of the hemispherical shell. This well below the allowable of 1.0.
B. Method of Analysis is Stresses due to internal pressure Were de         means of a standard interaction ana.lysis.             of this analysis, the actual structure was divided   the following elements: the cylindrical shell was as a long cylinder, the tapered portion of the shell tvas treated as a short tapered cylinder, hemispherical section was treated as a long sph shell.
The thermal stresses were determined by the sk method ~ere it is assumed that the inside sur vessel is at the same temperature as the and the mean temperature of the shell remains steady state temperature. This method is cons conservative.
The fatigue evaluation was made on a cumulative where superposition of all transients is taken consideration.
The fatigue evaluation was made on a cumulative where superposition of all transients is taken consideration.
is means of the 26 
IPEC00069659
* *
 
* I PEC00069660 
RIV000052A Submitted: December 22, 2011
* *
                          *
* IPEC00069661 6.100 BOTTOM HEAP INSTRUMENTATION PENETRATIONS A. Discussion of Results The maximum average primary membrane stress in ensity for the bottom head is 26.5 KSI when taking in consideration of the ligament efficiency.
                          *
compares favorably with the Sm value of 26.7 At the location where the instrumentation attached to the bottOm head by the J-weld, the range of stress intensity is 53.9 KSI. This stress intensity Occurs on the inside surface favorably with the allowable of 69.9 KSI. The fatigue evaluation revealed that the highe usage factor was 0.14 and occurred on the outs of the tube. This value compares favorably wi allowable of 1.0. B. Method of Analysis An interaction analysis was performed by divid actual structure into the following analytical bottom head was treated as a perforated spheri with modified elastic constants and the inst tube as a long cylinder.
* IPEC00069660
The effects of the re on the bottom head were assumed to be local onl assumed that for any condition where there is between the tube and head, no bending at the we exist. Using mechanical and thermal stresses analysis, a fatigue evaluation was made for the 27 
 
* *
RIV000052A Submitted: December 22, 2011 27 6.100 BOTTOM HEAP INSTRUMENTATION PENETRATIONS
* IPEC00069662
* A. Discussion of Results The maximum average primary membrane stress in ensity for the bottom head is 26.5 KSI when taking in consideration of the ligament efficiency.
* *
compares favorably with the Sm value of 26.7 At the location where the instrumentation nononr'~
* I PEC00069663 7.000 REFERENCES
attached to the bottOm head by the J-weld, the range of stress intensity is 53.9 KSI. This stress intensity Occurs on the inside surface favorably with the allowable of 69.9 KSI.
: 1. ASME Boiler and Pressure Vessel Code, Sec for Nuclear Vessels 2. Section III Code Case 1332-3 3. Section III Code Case 1335-2 4. Section III Code Case 1336 5. Section III Code Case 1366 III 6. Tentative Structural Design Basis for Reac Pressure Vessels and Directly Associated (Pressurized, Water Cooled Systems) PBI51 . Department of Commerce.
The fatigue evaluation revealed that the highe usage factor was 0.14 and occurred on the outs of the tube. This value compares favorably wi allowable of 1.0.
: 7. Screw-Thread Standard for Federal Service, 8. Code for Pressure Piping, ASA-B 31.1-1953
B. Method of Analysis An interaction analysis was performed by divid
: 9. Westinghouse Equipment Spec. 676497 dated 10. Westinghouse PAR's 11. S. Timoshenko and J. N. "Theory of Elasticity", McGraw-Hill, 1934 12. S. Timoshenko and S. Woinowsky Krieger, "Theory of Plates and Shells", McGraw-Hill, 1940 13. R. B. Heywood, "Design by Photoeiasticity", Chapman and Hill Ltd., 1952 14. R. E. Peterson, "Stress Concentration Fac John Wiley and Sons, Inc., New York 1953 15. E. F. Bruhn, "Analysis and Design of Structures", 1949 16. P. G. Lawson, W. J. Cox, of John Wiley & Sons, Inc., New York, 1947 17. B. F. Langer, "Applications of Stress I..Ol[1CEIn Factors", WAPD-BT-18 ion 28 
* actual structure into the following analytical bottom head was treated as a perforated spheri with modified elastic constants and the inst tube as a long cylinder. The effects of the re on the bottom head were assumed to be local onl assumed that for any condition where there is between the tube and head, no bending at the we exist. Using mechanical and thermal stresses analysis, a fatigue evaluation was made for the
* *
* IPEC00069661
* I PEC00069664 
 
*
RIV000052A Submitted: December 22, 2011
* I PEC00069665
                            *
: 18. W. J. "The Effects of Local Flexibility on Stresses in a Structure", WAPD(CE)-170
                            *
: 19. P. O. Bijlaard, "Stresses from Radial Loads in Cylindrical Pressure Vessels".
* IPEC00069662
The Journal. Research Supplement.
 
Dec., 1954 20. P. O. Bijlaard, "Stresses from Radial Loads and External Moments in Cylindrical Pres Vessels", The Welding Journal, Dec., 1954 21. Welding Research Council Bulletin No. 107, Local Stresses in Spherical and Cylindrical Shells due to External Loadings, K. R. A. G. Hooper, and J. L. Mershon, August 196
RIV000052A Submitted: December 22, 2011 28
* 22. Sampson, R. C., "Photoelastic Investigation Stress Distribution in a Perforated Hemisph Head .0&#xa3; Reduced Thickness" Westinghouse Re"''''''-'-l:;l1 Report 100FF996-R4
* 7.000   REFERENCES
* 29 
: 1. ASME Boiler and Pressure Vessel Code, Sec       III for Nuclear Vessels
* *
: 2. Section III Code Case 1332-3
* I PEC00069666 
: 3. Section III Code Case 1335-2
.' APPENDIX A
: 4. Section III Code Case 1336
: 5. Section III Code Case 1366
: 6. Tentative Structural Design Basis for Reac Pressure Vessels and Directly Associated rn~n(~n~
(Pressurized, Water Cooled Systems) PBI51
                        . Department of Commerce.
: 7. Screw-Thread Standard for Federal Service,
: 8. Code for Pressure Piping, ASA-B 31.1-1953
: 9. Westinghouse Equipment Spec. 676497 dated
* 10.
11.
Westinghouse PAR's S. Timoshenko and J. N.
                          "Theory of Elasticity", McGraw-Hill, 1934
: 12. S. Timoshenko and S. Woinowsky Krieger, "Theory of Plates and Shells", McGraw-Hill, 1940
: 13. R. B. Heywood, "Design by Photoeiasticity",
Chapman and Hill Ltd., 1952
: 14. R. E. Peterson, "Stress Concentration Fac John Wiley and Sons, Inc., New York 1953
: 15. E. F. Bruhn, "Analysis and Design of Structures", 1949
: 16. P. G. Lawson, W. J. Cox, '~chanics of John Wiley & Sons, Inc., New York, 1947
: 17. B. F. Langer, "Applications of Stress   I..Ol[1CEIn ion
* Factors", WAPD-BT-18 IPEC00069663
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069664
 
RIV000052A Submitted: December 22, 2011 29
: 18. W. J. O'Donne1l~ "The Effects of Local Flexibility on Stresses in a Structure",
WAPD(CE)-170
: 19. P. O. Bijlaard, "Stresses from Radial Loads in Cylindrical Pressure Vessels". The Journal. Research Supplement. Dec., 1954
: 20. P. O. Bijlaard, "Stresses from Radial Loads and External Moments in Cylindrical Pres Vessels", The Welding Journal, Dec., 1954
: 21. Welding Research Council Bulletin No. 107, Local Stresses in Spherical and Cylindrical Shells due to External Loadings, K. R.
A. G. Hooper, and J. L. Mershon, August 196 *
: 22. Sampson, R. C., "Photoelastic Investigation Stress Distribution in a Perforated Hemisph Head .0&#xa3; Reduced Thickness" Westinghouse Re"''''''-'-l:;l1 Report 100FF996-R4 *
          *
* IPEC00069665
 
RIV000052A Submitted: December 22, 2011
                          *
                            *
* IPEC00069666
 
RIV000052A Submitted: December 22, 2011
          .'
APPENDIX A
* DETAILED STRUCTURAL ANALYSIS r
* DETAILED STRUCTURAL ANALYSIS r
* IPEC00069667 
* IPEC00069667
* *
 
* I PEC00069668 
RIV000052A Submitted: December 22, 2011
*
                            *
* IPEC00069669 APPENDIX A DETAILED STRUCTURAL ANALYSIS TABLE OF CONTENTS 1. Control Rod Housing Stress Analysis and Fatigue Evaluation
                            *
: 2. Structural Analysis of the Closure Head and Vessel Assembly 3. Fatigue Evaluation of Head Flange, Vessel Flange and Closure Studs 4. Nozzle Code calculations
* IPEC00069668
: 5. Thermal Stress Analysis and Fatigue Evaluation of Inlet Nozzle 6. Thermal Stress Analysis and Fatigue Evaluation of Outlet Nozzle 7. Structural Analysis of Inlet and Outlet Nozzles and Vessel Supports Under Pipe Break Loads 8. Fatigue Evaluation of Vessel Support Pads 9. Structural and Fatigue Analysis of the Vessel Wall Transition
 
: 10. Structural Analysis of the Core Support Pads 11. Structural Analysis of Vessel and Bottom Head Juncture 12. Fatigue Evaluation of Bottom Head to Shell Juncture 13. Structural and Fatigue Analysis of Bottom Head Instrumentation Penetrations
RIV000052A Submitted: December 22, 2011 A-I APPENDIX A DETAILED STRUCTURAL ANALYSIS TABLE OF CONTENTS
: 14. Nomenclature A-I A2 -A24 A2 -A5S -AlOZ -All3 -Al77 -A2S2 -A267 -A2BO -A30l -A328 -A340 A34 -A353 A3 -A366 COMBUSTION ENGINEERING.
: 1. Control Rod Housing Stress Analysis and      A2 - A24 Fatigue Evaluation
INC. IENGINEIERINCI CHATTANOOGA.
: 2. Structural Analysis of the Closure Head      A2  - A5S and Vessel Assembly
TENN. .HEII:T' __
: 3. Fatigue Evaluation of Head Flange, Vessel        - AlOZ Flange and Closure Studs
__ O",_-'2o...1.!.-.
: 4. Nozzle Code calculations                          - All3
__ CHAItGIE NO. DATE 7 DESCRlnloN
: 5. Thermal Stress Analysis and Fatigue                  - Al77 Evaluation of Inlet Nozzle
??41 liCeL ,@,z.Q M,4/StV6=
: 6. Thermal Stress Analysis and Fatigue                - A2S2 Evaluation of Outlet Nozzle
$Tft::'U A.wz <. J&sect;IS CHECK DATE /.
* 7. Structural Analysis of Inlet and Outlet Nozzles and Vessel Supports Under Pipe Break Loads
7 AV./2 iAmrvE EV.4L<<.9T1tW BY //)Ot?? /:' IPEC00069670 5-OEWLEO .4&//11. >'$/5,' C2. -SYS'TEe? GEonET"er:
                                                                    - A267
,-/ L CX/JT/eAi-4-MJ9URI'1L:
: 8. Fatigue Evaluation of Vessel Support Pads          - A2BO
FLFJAH;'*:
: 9. Structural and Fatigue Analysis of the              - A30l Vessel Wall Transition
SA-I":? TYPE30&#xa2; S>I'1//JU$;
: 10. Structural Analysis of the Core Support Pads        - A328
7t.18 c : 5/3-167 /A/CO,v&#xa3;L COMBUSTION ENGINEERING, INC. IINOINEIERINO DE,.ARTMENT.
: 11. Structural Analysis of Vessel and Bottom            - A340 Head Juncture
CHATTANOOGA.
: 12. Fatigue Evaluation of Bottom Head to Shell    A34  - A353 Juncture
TENN. CHARG.NO, ____ __ ---DUCRlflTlON
: 13. Structural and Fatigue Analysis of Bottom      A3  - A366 Head Instrumentation Penetrations
&,(/7@'= ROD /hv.fij.I{r A0""Y,5/5cHECK
: 14. Nomenclature
'. be rr971MIE EJ//i/..vl9w1"l
* IPEC00069669
* IPEC00069671 5_ LJU&L.g.q, AU(k A,' b. 5Y57g,v; LtMQS,' 'l;;e &VT,eOL y 5,Y"'I<JA/
 
Oft,/ ->>tEG'T 5 8.&#xa3; 1A/1/&#xa3;$r/&rJT&#xa3;O .t'iiR?He' "c/u,(!)w/JV&
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.
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IENGINEIERINCI DE~ARTMIENT. CHATTANOOGA. TENN.              .HEII:
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.
ENGINEERING DEPARTMENT. CHATTANOOGA, TENN.
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Submitted: December 22, 2011
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.                                    NUMBER ~-/t:JO-P                    I A-22 ENGINEERING DEPARTMENT. CHATTANOOGA.. TENN.                      .HEET__~2~5~__~OFc___2~1____
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: 67. 91:S1 @5S0"r          [b-e PoouT -zJ S'<:c  S,vcO,5      21 ~22
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* IPEC00069690
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.
ENGINEERING DEPARTMENT. CHATTANOOGA. TENN.                                8H"'&1~_ _    -='--__t-'.. _--",,-,-_ _
CHARGE NO,_ _ _ _ _ __
DESCRIPTION (OUTgO'-      ~Q      j/p(/$/(>/6-    Sr,egs 4-7EA&sect;llr'            CHECK    gA*TIL--.!.~'4_ _I ' T - ' = =
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.                                                          NUMBER $-/Otl-P                        I  A-24 ENGINEERING DEPARTMENT. CHATTANOOGA. TENN.                                              .HEET_____Z_7____0p__~2~1_____
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEEf4!ING, INC.
IENGINEER/NG DEPARTMENT. CHATTANOOGA. TENN.
CHARGE NO'_ _ _ _ _ _ __
DDcRIPI'ION 57,...1/(17"<<&#xa3;8L      AuAt!YS/s i?F ,wE 4p.fPRe
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.                                                            NUMBER      5-/5t:>-P                    I A-26 ENGINEERING            DE~ARTM.NT.          CHATTANOOGA. TaNN.                            8H.ET'~&~~_ _ OF'_...:;::'..L.,'t'_ _
CHARGE NO                                                                  CATa            I~-  ') 2-(,,5            8y6c.ek'ea DESCRIPTION 57RV&#xa2;7vgRL                      Au.94YS/f            <2r 1#,      t'UJSI/IU      CHIECK DAT"          /t?-Z'7-'''S ByA"E\;..z,U.o6e'
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IPEC00069694
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC.
ENGINEERING DEPARTMENT. CHATTANOOGA. TENN.                                SHEET___~______ I~~--~-----
CHARGE NO'______________
DESCRIPTION      5'"7-e(/<7(/~m_      AA/r1LY515      CJF  7(Je- &asvee    CHECK  DATE---f.~!::..!:...~~-BY I/I'/O      Ilvo    JlES5EL.. A.5SrH(f2  y 5_ OC'rPILD AA/4L Y5'I.5:
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.                                                          NUMBER~:~,-~/~~O~-~~_____LI~A~-~2~8~
ENGINEERING DEPARTMENT. CHATTANOOGA. TENN.                                              SHEET__~B~______'OF __~2~f~___
CHARGE NO ______________                                                    DAT~E______;._V_-~2~2~-~b=S~_IBY<!~**KK"LI.
                            ~RVCTVR/JL            ,4VIU. ySfS O,e ?HE c!'1.~Sb'&#xa3;G                                            1Ii-1Z-",r; By~tI$l;
* DESCRIPTION                                                                                  CHECK DATE IIIf'I1P      AVIJ ($"$5 ~L 4SSt"MB L y' 5_  !?Em/LEo 4/./4<'. ">'SIS:
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RIV000052A Submitted: December 22, 2011 CO~SUSTION              ENGINEERING. INC.
IQ\IGlN~ING D~ARTMIENT.              CHATTANOOGA. TENN.
CHARG. No,_ _ _- -_ _
* D~~IPTION ST,ev4rv,e;'U            "MLYSIs {?,r        Me'" 4arUU'"
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RIV000052A Submitted: December 22, 2011
                                      -
COMBUSTION ENGINEERING, INC.
ENGINEERING    DJ:~ARTMENT.
r< ;,
                                                      ,",    ..
CHATTANOOGA. TENN.
NUMBER 5'-/50...,0 SHEET      i 0 IA-:30 0f'_-"2""'9'--__
CHARGE NO _ _ _ _ _ __                                DATE            J{)-2'2-~        By(1ocKRC.!L DIUCRIP'TION 5'r~l/t: 7(/&#xa3;,rIL IIfllO A,v1U. 'ISIS ~~ Z{,:r
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC.
ENGINEERING DEPARTMENT. CHAlTANOOGA. TENN.
CHARGE 1-/0._ _ _ _ _ __
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.                                          SHEET__    ~  ______OF____          ~  ___
ENGINEERING OEPARTMENl". CHATTANOOGA. TENN.
DATE          1&- 2 2--{;S        BY~U.
CHARGE NO' ______________
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RIV000052A Submitted: December 22, 2011
                                                                                                        ... -
                    ~ION ENGINEERING, INC.
lIN. . . . . . . . DEPARTMENT. CHAtTANOOGA. TIENN.
_ _ NO_ _ _ _ _ __
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RIV000052A Submitted: December 22, 2011 NUMBER 5-15tJ-P I A-34    ,-"'
COMBUSTION ENGINEERING. INC.
SHEET        H-            0.. 21 ENGINEERING DIEPAtri'MIlNT. CHATTANOOGA. TIENN.
DATE            10- 12-6>5    ByCO-"RR&'LL CHAROK    NO'_ _ _ _- - -
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COMBUSTION ENGINEERING.
 
lINe. NUM.E"-'-S
RIV000052A Submitted: December 22, 2011
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I!NGINEERING DEPARTMaNT.
lENGU... 'c~~Na D.~AIITMDIT. CHATrANOOGIA. T.NN.
CHATTANOOGA.
CHAIIa& NO_ _ _ _ _ __
TENN. SHIEItT II 01"_--:;;.5...;..'
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RIV000052A Submitted: December 22, 2011
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COMBUSTION ENGINEERING, INC.
DEPAaTM&#xa3;IU'; TlIIIINO CHARGIl NO, ______ _ DaCl!tlII'I'IQN
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RIV000052A Submitted: December 22, 2011 COMlIUST'ON ENGINEERING, INC.
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.                                              NUMBER 5-/5t:J-p                    IA-38 ENGINEERING        DE~AJtTM.NT. CHAtTANOOGA. TENN.                       SHEET      1t3            Op*_ _2::..L9_ _
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.
DlGtNURING DEPAIITMKNT. CHATTANOOGA. TKNN.
CHARGE NO_ _ _ _ _ __
* DPCRIPTtON SreMTV.t'A? .44'e~t.us .tJ,.: ME ~ps""...e-
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                                                  - 229, 9tH-/        p IPEC00069707
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC.                                                                NUMBER &sect;-(;;tJ-P                  IA-4D ENGINEERING DEPARTMENT. CHATrANOOGA. TENN.                                                    SHEU*_.....:;.2;:..CJ_ _ O I"      2. 9 C  H  A  ~  G  E  N  O  '  _____________                                                It}* 2 2-(,,5      BY~Ck"ReU DATE gUCRIf'TION    S*7RVC7WM4                            ,4""&tY~/f    tJ""  7#E Ct.tJS?,,e4"      CHECK gATE        /tJ-]Z-t,5 By.4L.~,("''''.t:JGR
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e- lJGVFJ.t)PctEN'T v;: Co/,lTIAlI//ry EOWl"T{4A1S:
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IPEC00069708
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.
IiNGINEIiRING DEPARTMENT. CHATTANOOGA. TENN.
                                                                                                                  "".
CHARGE NO'_ _ _ _ _ __
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* IPEC00069709
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.                                            NUMBER 5-/5&-P                    I A-42 ENGINEERING DE ..ARTMENT. CHATTANOOGA. TENN.                                SHEET        :2 Z          01"';"    2' CHARGE NO, _ _ _ _ _ __                                      DATE            /t?-22-b~        By("<X~ReU
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                                                                                                                                                                              > f'II
                                                                                                                                      ~~            ~ ~
                                                                                                                                      ~ ~          ~        "'i              ~ ~
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27 ('2ZS              (;)                    24,t)433                                                                ~ ~                    "-
8GI *~
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                  -2, Zit!              0                      -/.9Z5r."                ",3/6/
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                                                                                                                                      ~ ~
                                                                                                                                              ~                                .> z-
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1.fIZ.39'Jo
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5, 174-7            $.~51b                  5.11!z-              -33.#Zb                                                ~
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              -38. ON'?            -~/'3zIS                  - fl . .fZI.J          &#xa2;-93.776'7
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                                                                                    -3ZS. 9z7'5                                      "'" ~
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RIV000052A
                                                                                                                                      ~
t.:
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Submitted: December 22, 2011
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.                                                    NUMBER        S -15P-P                  IA-M-ENGINEERING DEPARTMENT. CHATfANOOGA. TENN.                                            SHEET        2+                  OF      21 CHARGE NO,_ _ _ _ _ __                                                DATE              /0-27.-(".5          Byda:"&#xa2;<fU DQCRIPTION        .:5r,etJcrtJg"14 #118' ~I.S .?'r              7H  Ct..PSCJR        CHECK DATI'              /1P-n~b5 By4u"M.vt/F,{'
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I/. 0. l'YII'tr- 23.2120              -O.OO8MW~        -d. MZ4    0.171535 '" P.21304                -O.04Wlp: -O"()~5 11,    -2.12711>"- -J2'U'f.t"            ~.f)~"6~ w~      O. IJ770(' -2.lI-tIZ5"* -J.(141151            -3, 5nz",pe -Z(7.1~S7 Jfz    O,tJZ'MT-        3.317"        tJ.rJ432<i W"# d,OHfJt P.o3+345*- CJ.04zr,,5 -/.O'lozt>,po- 2,7257 f1t.  -IJ./b44P.J r,-I1.lb7Z            -tJ, 57'21 IfW: - tJ. 726f; 1 -#.2(.Z555.- -d. 32bll /1.(J'IOI9f< 41.1255 Jh    -P./SHIT: -IB.2221              -O./7102 W ' -~.tm()            t),/7I7K5" - O. 2133"-            I. '2 nz'1P= 3. {);;~ 1 M;      -3355b-f1--'31/.03<ff- -]. 61'13Zw':- 4,Sf6,4- ?,h157/f*- -4.5(,,57.3                              '1. ~49rzP~ ;';'.I'tZ B V                /V                                  /lJ                        /V                    iJ/tOt.67P: cJ.7hh'1
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* IPEC00069712
 
RIV000052A Submitted: December 22, 2011
                    ~JON ENG~G;                                            INC.
ENGtNCIllRlNGI' DEPARTMENT. CHATtANOOGA. TEltN'.
CHARGe NO_ _ _ _ _ __
DUc:ltIPTION  5'UV{TPr2~f      4VOL tft" P""        7h~. &~.:I<!"""
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Submitted: December 22, 2011
          *                                                                                                  *
* RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.
ENGINEERING DEPARTMENT. CHATTANOOGA. TENN.
CHARGKNO_____________
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* IPEC00069715
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.                                                  NUMBER 5'-/5&-,0                    I A*48 ENGINEERING DE~ARTMENT. cHATTANOOGA. TENN.                                      .HEU        1.8            01"      Z '7 CHARG.NO'______________                                              DATE          1~"22jf5            BY~~
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IPEC00069716
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.
ENGINEERING DEP'ARTMIENT. CHATrANOOGA. TENN.
CHARGI!: NO,_ _ _ _ _ __
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.                                    NUMBER      s"-IS()-,D hA          I A-50
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IPEC00069718
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.
IENGINIEI:RING DE..ARTMENT, CHATTANOOGA, TENN.
CHAROIENO_____________
DDCRIPTION            Ilp~e&a!)(      70      s-/s{)-P
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IPEC00069719
 
RIV000052A Submitted: December 22, 2011 I
COMBUSTION ENGINEERING. INC.                                            NUMBERS-ISO--/'            Ike, .&/ A 52 ENGINEERING DEPARTMENT. CHATTANOOGA. TENN.                                  SHEET          2              OF---'3"'-_ __
CHARGE NO _ _ _ _ _ __                                          DAT~E_ _2-1_-~2~6:...-.:::6~B_ _ IBY {'OO.'.I?C:U
* DESCRIPTION      ilPPE,/JQ/'(    :z,  S-/,5'tJ-P                              CHECK DATE          4-2f,12e.          BY !lFlL/o"!:;<'
Avo      57RES5ES            dT ME /,;,.0                ('/r- /h'E "c; -"k"~a        LJp  4      s;,#~,,->/ .."'lL. 3E<:: 7'/cMJ
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                                                                              .e, ': :  81;S t, = ..,"
                                                                              ~,    = ,gs'7!/
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                                                                                                                                                      *
                        -I- ~ + 4w.;~              tZ,Zp d',K = -    i/'          t-,      T 2R,c,    = ~ O';ZZ44#e              f-:20M71-& f-s.&7z~oP ff" "  + ~L      f- -r-4t. (ose  T ~ -+              E &#xa3;/Cca.f9. r        ell P V.;;>  -    t,"          t-,        t::;5/,vfP  -    .!If$/>>;)            ZR, It, 0;    ~  -p    0
          ~--------_/_-------------------- ---------------~
* IPEC00069720
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.
ENOINIEIERINO    CE~ARTMIENT.      CHATTANOOGA. TENN.
CHAROIENO'_____________
Cac:RIPTION        /lpeEl/alX'      ze    5-/.>tJ-,P
                ,tteP&sect;VJ2tJ(      8:
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                    /AlSII}'&#xa3;      S(')RP/'JCF .        p()~
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L -_________._________________________________________.________                                          +-______          ~
IPEC00069721
 
RIV000052A Submitted: December 22, 2011 INC. NUM
* CHATTANOOGA. TENN. SHEET 1      OF 2
CHARGE Net                          DATE  4-2')-68    BY Cockrell DESCRIPTION  AE:E:eildix to S-l50-P              CHECK DATE        BY_ _ _
CLOSURE HEAD PENETRATION SPACING:
* The general requirements for spacing of openings in spherical shells (such as a closure head) are given in Paragraph N-45l of the ASME Code Section III.
Additional requirements are given in Article 1-6 of Section III as referenced in N-45l(e).
The spacing of the closure head penetrations meet the requirements of Paragraph N-45l with the exception of 1-6l3(b) of Article 1-6. Paragraph 1-6l3(b) states that tiThe arc-distance measured between the center lines of adjacent nozzles along the inside surface of the shell is not less than three times the sum of                :>~r~\
                                                                                            ': ~ :i*~ ,,:.
their inside radii for openings in a head **** ".
This requirement would restrict the ligament efficiency to a minimum of 66.7%. The actual ligament efficiency of the closure head is 66.6%. Since the actual ligament
* efficiency deviates slightly from the required minimum ligament efficiency, Paragraph 1-620 of Article 1-6 must be met. Paragraph 1-622 of Article 1-6 states that 'lIn accordance with 1-1012, re-evaluation is not required for configurations for which there are available detailed experimental results that are consistent with the requirements of Article 1-10."
The purpose here is to use the results of Westinghouse Research Report 100FF996-R4 to show that the closure head penetration spacing is satisfactory for the closure head. The ligament efficienty of the penetration spac-ing in this experiment was 38% which should more than suffice to show that the closure head's ligament efficiency of 66.6% is adequate.
The results from the above report show that the membrane portion of the stress due to internal pressure can be accurately calculated by dividing the primary membrane stress in the unperforated region by the ligament efficiency. See the discussion and results given on pages 23 and 24 of the above report. It is shown there
* IPEC00069722
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.
ENGINEERING DEPARTMENT. CHATTANOOGA. TENN.
CHARGE            NO'_______
DESc:RI""IONI--!A=pJ::p.:::e.!.!n:.:::d~ix=-...!:t:.::o:.....:S=---=1::.,5::..:0::...--=P=-______ CHECK ..A.T...._ _-+__ .n CLOSURE HEAD PENETRATION SPACING:
that the calculated value of the average primary membrane stress deviates from the experimental va by only 2%. The higher value being the calculate value; hence, the method of dividing the required thickness in the unperforated region by the lia~m~nr efficiency is valid and reasonable. This method used to obtain the thickness of the closure head.
The stress indices to be applied to the computed membrane stress intensities for a fatigue analys as determined from the results of the experiment 1.05 and 1.44 for the inside and outside surfaces respectively. These values are well below the required index of 2 for both the inside and outs surfaces from Article 1-6 of Section III. It is, therefore, concluded that the slight deviation the spacing requirement in I-613(b) is insigni
* both from the standpoint of establishing the requ head thickness and for fatigue considerations .
* IPEC00069723
 
RIV000052A Submitted: December 22, 2011
                                                            ..-;.
COMBUSTIO~ ENGINEERING, INC.                                                  NUMBER    $-/5/-;:;>          *t43~
ENGINEERING DEPARTMENT. CHATTANOOGA. TENN.                                        8HEET'__~5~____'OF                SI CHARGK,NO'_______________                                          DATK~__~5~-~/Z~-'~~~_____ BY~'4
* DIESCRIPrION Fi?TKcVE Ea:y.V9??ftr<.!                        &    PFA'.o F4f&E,        CHECK DATE      5'-Il. -G';'      BY~
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* IPEC00069724
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERI",G. INC.
ENGINEERING DEPARTMENT. CHATTANOOGA. TENN.
CHARGIENO'______________
DEllCIlIPTION h            T/&V<""      AMtfl&#xa3; Y4b          c2E  &/'10 n/'lMc.-.rr
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                    //-14. A5/4L ~06 Se ('" 770Al Ill' IPEC00069725
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENCINEERING, INC.                                                                              IA 58 ENGINEERING D~AltTMaNT. CHATTANOOGA. TENN.                                          .HKET*____~7_____ op,___~51____
CHARGE NO'_ _ _ _ _ __
                                                                                                                                    ~
DATW~  ___9~~~-~/1~*~~~~__ BY~~
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IPEC00069726
 
RIV000052A Submitted: December 22, 2011
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                    & (1//            ;t IPEC00069727
 
RIV000052A Submitted: December 22, 2011 i
COMBUSTION ENGiNEERING. INC.                                      ';NUM**,{t.)$'!~,o :<''-            IA'O
_GINEERING DEPARTMENT, CHATTANOOGA. TCNH. '                              .HUT """9                0.. 5/
                              ~GKNO'            ____________
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AND &t?i.flRF Slll125
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I IPEC00069728
 
RIV000052A Submitted: December 22, 2011 COMBUSTION                f;NGU1i~J:RING,                      INC.
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IPEC00069729
 
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. lINe.                                    NUM.E"-'-S.....
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* i IPEC00069730
 
RIV000052A Submitted: December 22, 2011 COMBUSTIQN                ~                        INC..
81G11&ERlNCJ. DEPAaTM&#xa3;IU'; ~ TlIIIINO CHARGIl NO,_ _ _ _ _ __
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                                                                                                                                                                                                                                          ~~ (;;~
                                /t!J,t.                                                      In.
                                                                                                                                                                                                                                          ~ ~
S.oO                                              IF/                                                -tl.48'1 -22$111 ZP4'4Uo 51-7/PO iz.r-lllo 5-17bo l#l"'oi a _ z
                                                                                                                                                                                                                                          ~        '"                     )0  x    C
                                                                                                                                                                                                                                          ~ $\.                                 III  I:
                                                                                                                                                                                                                                          ~ ~                                  !!I  =
ill
                                                                                                                                                                                                                                          ~\                                            t{I
                                                                                                                                                                                                                                          ~ ~
                                                                                                                                                                                                                                          ~~
                                                                                                                                                                                                                                          ~ ~
                                                                                                                                                                                                                                                                                  'I" VI I0
                                                                                                                                                                                                                                                                                ..
i' "t,
RIV000052A
                                                                                                                                                                                                                                          ~ "I
                                                                                                                                                                                                                                                                    ~ ~ ~
tl.           I
                                                                                                                                                                                                                                          ~        ......
                                                                                                                                                                                                                                          '"       .....
                                                                                                                                                                                                                                                  \,.
                                                                                                                                                                                                                                          ~~                      ~r"""
                                                                                                                                                                                                                                                                    ~ ~
It
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Submitted: December 22, 2011
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* _ _ or}}

Revision as of 19:11, 11 November 2019

Official Exhibit - RIV00052A-00-BD01 - Combustion Engineering, Inc., CENC-1110
ML12335A575
Person / Time
Site: Indian Point  Entergy icon.png
Issue date: 12/22/2011
From:
Combustion Engineering
To:
Atomic Safety and Licensing Board Panel
SECY RAS
References
RAS 21634, 50-247-LR, 50-286-LR, ASLBP 07-858-03-LR-BD01
Download: ML12335A575 (134)


Text

{{#Wiki_filter:United States Nuclear Regulatory Commission Official Hearing Exhibit 5,9$ In the Matter of: Entergy Nuclear Operations, Inc. 6XEPLWWHG'HFHPEHU (Indian Point Nuclear Generating Units 2 and 3) ASLBP #: 07-858-03-LR-BD01 Docket #: 05000247 l 05000286 Exhibit #: RIV00052A-00-BD01 Identified: 10/15/2012 Admitted: 10/15/2012 Withdrawn: Rejected: Stricken: Other: C E N C - 1110

                                                                                                         ~\\\\I\\\\\'

Bro ZOl I L/j' ANALYTICAL REPORT FOR INDIAN POINT REACTOR VESSEL UNIT NO. 2 COMBUSTION ENGINEERING, INC. .i: Ii, 1:_ Cockrell CHATTANOOGA, TENN. Lowry* IPEC00069599

RIV000052A Submitted: December 22, 2011 IPEC00069600

RIV000052A Submitted: December 22, 2011

  • REPORT NUMBER 1110 SUBJECT CATEGORY "ANALYTICAL REPORT" COMBUSTION ENGINEERING, INC.

NUCLEAR COMPONENTS ENGINEERING DEPARTMENT C.E. CONTRACT NO. 17765 ANALYTICAL REPORT FOR INDIAN POINT REACTOR VESSEL

  • UNIT NO. 2 C. R. COCKRELL AND J. C. LOWRY IPEC00069601

RIV000052A Submitted: December 22, 2011

                           *
                           *
  • IPEC00069602

RIV000052A Submitted: December 22, 2011

         *
                            'rHI:) l)()CUMF,H'I' r:'i 'rEE PROPEilTY OF corI[BU~)'l'I OIJ :INGINEERIW;, urc.,       ,'IDP):;O 1, COHN.

Atm 1::', Wl,[, TO BE IU;:PRO\)UCED, f)i\ mmD TO PUlmC'J ,r, ry LI-FOHMATIO].r Fon MAKItIG OF DW\.'dINGS 0;\ APPf,['\A'J'U:: EXCEP'!' lmERE PROVIDED FOR BY AGHEE;*1J::IJT ',lITH :3AID CCMPjl,~I': *

         *
  • IPEC00069603

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069604

RIV000052A Submitted: December 22, 2011

         *
          .-

Acknowledgement is hereby made of the important contributions rendered by the following individuals:. Project Enginee.&: J. S. Meek Structural Analysis M. W. Alexander J. K. Allison R. J. Caudle W. R. Ferguson W. J. Heilker F* P. Hill

  • Des ign. Endneer B. R. Moss
  • IPEC00069605

RIV000052A Submitted: December 22, 2011

                          *
                          *
  • IPEC00069606

RIV000052A Submitted: December 22, 2011

  • DISIRIBUTDpN LIST No. Ot COEies
w. G. Benz, Jr. 1 D. w. Sher 1 H. w. Dolfi 1 J. w. Alden 3

F. P. Hill 2 T. Halvorsen 1 J. S. Meek 1

w. B. Bunn 1
  • J. w. Harper B. R. Moss J. K. Allison 1

1 1 C. R. Cockrell 1

w. J. Heilker 1

J. C. Lowry 1 Westinghouse-APD 20 Library 1

  • IPEC00069607

RIV000052A Submitted: December 22, 2011

                           *
                           *
  • IPEC00069608

RIV000052A Submitted: December 22, 2011 1 1.000 ABSTRACT The structural integrity of the 173 in. 1.0. Indian Point Reactor Vessel - Unit No. 2 designed and fabricated under contract to the Atomic Power Division of the Westinghouse Electric Corporation is established by the results of the detailed structural and thermal analysis contained in this report. PREPARED BY

                                 ?,(&~

C. R. Cockrell And 9'(]* f8J7

  • J.C. Lowry APPROVED BY

(~e £;,)?M: {/!. S. ~ek

                               ~R?/J!I F. P. Hill cfu~~-Qf H. W. Dolfi   """-,
            . Project Engineer    Supervisor of            Supervisor of Analytical               Contract Design Group             Engineering Section CERTIFIED BY  -4imJ I? ;;ttl!.jf{

CERTIFICATE NO. . ,.::r?' 76 STATE OF TENNESSEE

  • IPEC00069609

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069610

RIV000052A Submitted: December 22, 2011 2 TABLE OF comus 1

  • 000 ABS TRA.C'f" ......."......"........"....""....."".....". 1 2 ~ 000 IM'TR.ODUCTION .***.* "." .......... " *** " ***** _ * * * * * * * *
  • 4 2'.010 Subject ................. "." .............. " ............ "... ""..... 4 2.020 P\lrpoae ........... "" ................................. "........... ".... 4 2 .. 030 Scope ................... "... "............................................. " 4 3 *000 DES IGN CRITERIA *********************.************ 5 4.000 GEOMETRY AND GENERAL CONFIGURATION **************** 6 5.000

SUMMARY

OF RESULTS ****.*****.*****...**.********.. 7 5.010 Control Rod Housings *.*******************. 7-8 5.020 Closure Head Flange and Shell **.******.***** 9 5.030 Vessel Flange and Shell ********************* 10

  • 5.040 Main Closure Studs **********************.*** 11 5.050 Inlet Nozzle and Vessel Support ************* 12 5.060 Outlet Nozzle and Vessel Support *********** 13 5.070 Vessel Wall Transition ********************* 14 5.080 Core Barrel Support Pads *******.*********** 15 5.090 Bottom Head to Shell Juncture ****.******.** 16 5.100 Bottom Head Instrumentation Penetrations *.* 17 6.000 DISCUSSION OF RESULTS AND METHOD OF ANALYSIS ***** 18 6.010 Control Rod Housings ....................... 18-20 6.020 Closure Head Flange and Shell ************** 20 6.030 Vessel Flange and Shell ******************** 21
  • 6.040 Main Closure Studs ************************* Zl-22 6.050 Inlet Nozzle and Vessel Support ************* 22~23 IPEC00069611

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069612

RIV000052A Submitted: December 22, 2011 3 TABLE OF CONTENTS (Cont I d)

  • 6.060 6.070 Outlet Nozzle and Vessel Support ********** 23-24 Vessel Wall Transition ******************** 24-25 6.080 Core Barrel Support Pads ****************** 25-26 6.090 Bottom Read to Shell Juncture ************* 26 6.100 Bottom Head Instrumentation Penetrations ** 27 7.000 REFERENCES ...................................................... .jj ........ ..

28-29 8.000 APPENDICES A. Detailed Structural Analysis Calculations ****** Al - A367 B. Thermal Analys is ***************************.** Bl - B124 C. Drawings - Combustion Engineering, Inc ******** Cl - C13

        *
  • IPEC00069613

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069614

RIV000052A Submitted: December 22, 2011 4 2.000 nmQDUCTION

  • 2.010 SubJ@ct The Indian Point Reactor Vessel - Unit No. 2 is a 173 in. I.D. pressurized water reactor.

The vessel is of cylindrical shape terminating in a hemispherical head at the bottom and a bolted flange at the top. Four inlet and four outlet nozzles are located in the cylindrical wall section. The vessel is supported by four weld built-up pads located on the underside of two inlet nozzles and two outlet nozzles. The closure head is of the hemispherical type. The closure seal is of the O-ring type. 2.020 Purpose This report contains the detailed structural and thermal analysis required to substantiate the adequacy of the design of the 173 in. I.D. Indian Point Reactor Vessel. 2.030 ~

        ~               The detailed analytical work necessary to justify the reactor vessel and its associated parts included in the contract are contained in this report. All equations used are shown and intermediate answers and final answers are usually presented in tabular form *
  • IPEC00069615

RIV000052A Submitted: December 22, 2011 IPEC00069616

RIV000052A Submitted: December 22, 2011 5 J,ooQ p2S1GN CRITERIA

          ~          The design shall be in accordance with the ASME'Boiler and Pressure Vessel Code Section III, Nuclear Vessels and Special Case Rulings in effect on the date of purchase order.

The design parameters used were Design Pressure ................................... . psia Normal Operating Pressure **********.******* 5 psig Design Temperature .......................... .. 50 0 F Normal Operating Inlet Water Temp *********** 57°F Normal Operating Outlet Water Temp **.******* 6 .7 o F Des ign Life ******************.*.***.*******. 40 years Transient Condition Occurrences in

1. Plant heatup at 100°F/Hr. 200
2. Plant cooldown at 100°F/Hr. 200
3. Plant loading at 5% of 14,500 full power per min.
4. Plant unloading at 5% 14,500 4 4.2
  • of full power per min.
5. Step load increase 10% 2,000 of full power - not to 4 4.3 exceed full power
6. Step load decrease of 2,000 4 lO~ from 50% power
7. Step load decrease of 200 4 50% of full power
8. Reactor trip 400
9. Hydro test 3125 pSia
10. Hydro test 2500 pSia 5
11. Steady state fluctuations 5 106
12. Loss of flow, one pump
13. Loss of load 80 .8
14. Steam break 80 .9 5 See 27 Material Al1owlb1es Sm @ 70°F C: S/o ,:," ( (1'~

SA-240 Typ. 316 J Sm @ 5500 F 20.0 KSI 30/) 17 6 KSI  :",3 SA-102B 26.7 ~u,o SA-J36 26 7 26.7 4_;:;" 26 7 ASTM-A540-B24 43.3 3JJ Inconel - 36 8

                              ,

23.3 23 3

  • IPEC00069617

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069618

RIV000052A Submitted: December 22, 2011 6

  • 4.000 GEOMETRY AND GENERAL CONFIGURATION I

CQt1l'TIfIJI. "?r>o

                       }/t?W'lil/&                This sketch shows the o~n""l configuration and relati     locations of component parts. The shown is used consis out this report.

drawings of component Appendix C. Reference Drawings l'.llk

1. Control Rod E 232-051 Mechanism Housing Details
2. Control Rod E 232-052 Penetration Details
3. Closure Head Form- E 232-046 ing 6. We lding
        *
4. Closure Head Machining
5. Stud, Nut 6.

Washer Detail

                                         -~,..,
                                     ..-  SHELL
6. Pressure Vessel Forming & Welding
7. Pressure Vessel Final Machining
8. Nozzle Details
9. Miscellaneous Attachments
10. Miscellaneous E- 32-055 Details ll. Bottom Head E- 2-043 Forming & Welding
  • 12. Instrumentation Penet. Assembly 6.

Details - Bottom Head E- 32-056 IPEC00069619

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069620

RIV000052A Submitted: December 22, 2011 7

  • 5.000 SUm1ARY OF RESULTS Results of the detailed structural analysis pre~pnrpn in Appendix A are summarized on Pages 7 through /7 for locations of major interest.

5.010 CONTROL ROD HOUSINGS Location - 1

                                  *Stresses Due to Operating Pressure of 2.25 KSI The maximum stress intensity for pressure is 09 - a r = 6.45 KSI on
  • surface.

The overall usage factor for o. Location - 2 Stresses Due to Operating and Design Temperature of The maximum stress intensity for design pressure of 2.5 the design temperature of 6500 F is /"Til - (Tr ~ 25.6 KSI and

  • located on the inside surface of the inconel tube The overall usage factor for fatigue was U ~ O.

IPEC00069621

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069622

RIV000052A Submitted: December 22, 2011 8

  • Location - 3 Stresses Due to Operating Pressure of 2.25 KSI Minimum Interference Fit with Closure Head The maximum stress intensity is "'x - (To '" 46.7 KSI and for the condition of maximum interference and zero pressure. This stress intensity is on the inside sur
  • The maximum range of stress is 55.3 KSI and occurs on inside surface.

The overall usage factor for fatigue was U = 0.0003. l&caUon - 4 The maximum stress intensity for the J-weld is 0x- 0B KSI and occurs on the inside surface. The maximum stress intensity is 42.8 at the same location. The overall usage factor for. fatigue was U '" 0.06 and red on the outside surface *

  • IPEC00069623

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069624

RIV000052A Submitted: December 22, 2011 9

  • 5.020 CLOSURE HEAD FLANGE AND SHELL Primary Stress Intensities Range of Stress Intensity
  • The highest range of stress intensity for the head closure head juncture was located on the inside surface (Location - 1). The value of this range of stress in is 50.4 KSI and compares favorably with the allowable 0 to Fatigue Evaluation The following overall usage factors were calculated at two above locations:

Location - 1 U '" 0.004 Location - 2 U '" 0.015 The maximum allowable usage factor is 1.0.

  • IPEC00069625

RIV000052A Submitted: December 22, 2011

                          *
                          *
  • IPEC00069626

RIV000052A Submitted: December 22, 2011 10

  • 5.030 VESSEL FLANGE AND SHELL Primary Stress Intensity 2

Range of Stress Intensity

  • The highest range of stress intensity for the vessel vessel shell juncture was located on the inside surface (Location - l ) . The value of this range of stress ity to is 45.4 KSI and compares favorably with the allowable of 80 KSI.

Fatigue EyaluatiQn The following overall usage factors were calculated at e two above locations: Location - 1 u 0.005 Location - 2 u 0.00002 The maximum allowable usage factor is 1.0 *

  • IPEC00069627

RIV000052A Submitted: December 22, 2011

                           *
                           *
  • IPEC00069628

RIV000052A Submitted: December 22, 2011 11 5.040

  • MAIN CLOSUJY; SIJ.!!2S A2~~ag~ Bol~ Stress; j \
                \           \
                  \

The average bolt stress

                                   \                                           from the design pressure
                                       \
                      \
                        ,                 \
                                              \ I
                                               ,                           Z load plus O-ring seat 34.4 KS!. The allowable 34.8 KS!.
                         \                       "-
                           \
                             \
                               \                                              The maximum average bolt
                                \                                             stress for the bolt-up was 36.8 KSI compared to of 86.6 KS!. For the bo operating pressure cond!

I stress was 39.6 KSI

                                 ,

j

                                   ~T-3                          allowable of 73.5 KSI.
         *                      ,--,

I The bolt 3* I This stre~s occurred dur

                                ,
                                 \                                  I
                                                                      /       up cycle of the 2500 psi
                                     \
                                        \
                                                                  /           test. This stress I
                                          \

I with the allowable of 1 I I I L. .-"""\_/,-~- ,--J EatiilUil Elliluation The maxUnum overall usage factor for the closure studs 0.313 and occurred at the point where it enters the vessel f (Location - 3). This usage factor compares favorably the allowable of 1.0. MaxLffiurn Bearing Stress The maximum bearing stress between the closure stud closure head flange was 39.8 KSI and compares with the of 40 KS! for the flange material. This value occurred during

        **

the heatup cycle of the 2500 psi hydrostatic test

  • IPEC00069629

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069630

RIV000052A Submitted: December 22, 2011 12

  • 5.050 INLET NOZZLE AND VESSEL SUPPORT Primary Membrane Stress Intensity The maximum average primary membrane stress intensity or the inlet nozzle was at the juncture of the nozzles to th wall on the longitudinal axis. The value of this stre intensity was 21.1 KSI and compares favorably with the able of 2~.7 KSI.

The same location gave the highest value of average pr

  • plus local primary stress. The value of this stress was 32.3 KSI and compares favorably with the allowable
1. 5 Sm = 40 KS 1.

Range of Stress Intensity The highest range of stress intensity occurred at the uncture of the nozzle to vessel wall on the outside surface in the longitudinal direction. The value of this range of s ess intenSity was 45.5 KSI and compares favorably with the allow-able of 80 KS!. Bearing Stress on Support Pad The bearing stress on the underside of the support pad Weight and thermal pipe reactions only was 3.0 KSI. was not to exceed 5.0 KSI for this condition. Fatigue Evaluation The maximum overall usage factor for the inlet nozzle U = 0.042 and occurred at the nozzle-vessel wall junct the outside surface in the circumferential direction.

  • compares favorably with the allowable of 1.0.

IPEC00069631

RIV000052A Submitted: December 22, 2011

                           *
                           *
  • IPEC00069632

RIV000052A Submitted: December 22, 2011 13

  • 5.060 OUTLET NOZZLE AND VESSEL SUPPORT Primary Membrane Stress Intensity The maximum average primary membrane stress intensity r the outlet nozzle was at the juncture of the nozzLe to the vessel wall on the longitudinal axis. The value of this stre s intensity was 21.1 KSI and compares favorably with the allow-able of 26.7 KSI.

The same location gave the highest value of average

  • y plus local primary stress. TI1e value of this stress i was 32.3 KSI and compares favorably with the allowable 1.5 Sm = 40 KS!.

Range of Stress Intensity The highest range of stress intensity Occurred at the of the nozzle to vessel wall on the outside surface in longitudinal direction. The value of this range of s intensity was 45.5 KSI and compares favorably with the able of 80 KSI. Bearing Stress on Support Pad The bearing stress on the underside of the support pad weight and thermal pipe reactions only was 3.6 KSI. was not to exceed 5.0 KSI for this condition. Fatigue Eyaluation The maximum overall usage factor for the outlet nozzle U = 0.022 and Occurred at the nozzle-vesseL juncture on

  • inside surface in the longitudinal direction. This val compares favorably with the allowable of U = 1.0.

IPEC00069633

RIV000052A Submitted: December 22, 2011

                          *
                          *
  • IPEC00069634

RIV000052A Submitted: December 22, 2011 14

  • 5.070 VESSEL WALL TRANSITION The maximum average pr stress intensity for transition occurs in in portion of the vessel wall. lue of this stress intensity was I and 3--- I I ~4 compares favorably with th allowable stress intensity of 26.7 1.

I I Range of Stress Intensity

  • The highest range of streSS intensity Occurred at Locat shown above.* The value of this range of stress intensi KSI and compares favorably with the allowable of 80 KSI Fatigue Evaluation
                                                                           - 1 as was 37.9 The maximum overall usage factor for the vessel wall         ition was U ~ 0.002 and occurredat Location - 2 as shown above.       is value compares favorably with the allowable of U ~ 1.0.
  • IPEC00069635

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069636

RIV000052A Submitted: December 22, 2011 15

  • 5.080 CORE BARREL SUPPORT PADS.

A

                    ) ),) )           ))))

r (' ( ( ( ( ( ( ( r r 1 ( (' ( ( (' -I

                              /                  r y

Stresses Due to Steady Loads The most critical streSs intensity for the side

  • load and occurred value of with the steady 125 KIP vertical load (due at the vessel wall (Location - Y as shown o-r ,[lW ,- n )

this stress intensity was 31.1 KSI and COlmp<lr~ favorably allowable of 35 KSI. Range of Stress Intensitx The The highest range of stress intensity occured at Locat - c as shown above. The value of this range of stress in ity was 40.8 KSI and compares favorably with the allowable of 9.9 KSI. Fatigue Evaluation The fatigue evaluation disclosed that the highest factor for the pads was 0.02 and occurred at the upper of the pad at the pad-to-vessel juncture Location - A. value compares favorably with the allowable of U 1.0 0: IPEC00069637

RIV000052A Submitted: December 22, 2011

                          *
                          *
  • IPEC00069638

RIV000052A Submitted: December 22, 2011 16 5.090 BOTTOM HEADTa SHELL JUNCTURE

  • The maximum average primar stress intensity for the bo I z to shell juncture occurs in cylindrical shell portion 0 juncture. The value of th intensity was 26.3 KSI and ~VlllU<'Les favorably with the allowabl 26.7 KSI.

f Range of Stress Intensity The highest range of stress intensity occurred at Loca ion - 3 as shown above. The value of this range of stress nsity was 34.1 KSI and compares favorably to the allowable range of stress

  • intensity of 80 KSI
  • Fatigu~ Eyaluation The fatigue evaluation disclosed that the highest over factor for the bottom head to shell juncture was 0.003 occurred at Location - 3 as shown above. This value es favorably with the allowable of U = 1.0 *
  • IPEC00069639

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069640

RIV000052A Submitted: December 22, 2011 17

  • 5.100 ftOTIQM HEAD INSTRUMENTATlOH PENETRATIONS The maximum average imary membrane stress in sity occurs in the bottom head en taking into consideration ligament efficiency. The va of the stress intensity is .5 KSI and compares favora Y with the allowable of 26. KSI.

Range of Stress Intensity

  • The highest range of stress intensity occurred on the surface of the tube - Location - 1 as shown above. The of this range of stress intenSity is 53.9 KSI and with the allowable of 69.9 KSI.

Fatigue Eya1 ua tion The fatigue evaluation disclosed that the highest overa factor for the bottom head instrumentation was 0.14 and on the outside surface of the tube - Location - 2 as The value compares favorably with the allowable of U ~ IPEC00069641

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069642

RIV000052A Submitted: December 22, 2011 18 6.000 DISCUSSION OF RESULTS & METHOD OF ANALYSIS

  • 6.010 Control Rod HoUSinis A. Discussion of Results Location - 1 For the juncture of the CRDM flange to tube, stress intensity for design pressure is 7.2 KSI occurs on the inside surface. The allowable 304 stainless steel at the design temperature Sm 23 KSI.

Location - 2 For the 304 stainless steel at the bi-metallic maximum primary plus secondary stress intensity KSI on the inside surface. This stress intens for the design temperature and pressure. For t conditions, the maximum range of stress intensi KSI and compares favorably with the allowable 0 45.9 KS!. .

  • For the inconel portion of the tube, the max intensity for the design conditions occurred on surface. The value of this stress intensity wa For the operating transients, the maximum range intensity was 21.8 KSI and compares favorably wi allowable of 3 Sm ~ 69.9 KS!.

stress the Location - 3 At the point where the CRDM housing enters the c head, stresses are induced in the tube at zero due to the interference fit. The stress intens maximum interference and zero pressure is 46.7 the operating transients, the maximum range of s ss intensity was 55.3 KSI and compares favorably wi the allowable of 3 Sm c 69.9 KSr. The fatigue evaluation revealed that the highest cumulative usage factor was 0.0003 for the inside surface. This com-pares favorably with the allowable of 1.0 *

  • IPEC00069643

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069644

RIV000052A Submitted: December 22, 2011 19 Location - 4

  • At the location where the CRDM housing is at the closure head by the J-weld, the maximum stress intensity is 42.8 KSI and compares fa with the allowable of 3 8m = 69.9 KSI. This of stress intensity occurs on the inside sur From the standpoint of fatigue, the most crit location will be on the outside portion of the where a stress concentration factor of four was The cumulative usage factor at this location and compares favorably with the allowable of 1.

B. Method of Analysis Location - 1 An interaction analysis was performed at assuming the CRDM housing flange to be a ring and e a long cylinder. Location - 2

  • An interaction analysis was performed at cut into consideration that elements 2 and 3 are 10 having different values of Young's Modulus of E and coefficients of thermal expansion.

taking cylinders sticity Location - 3 An interaction analysis was performed at cut th ee by taking the housing as a cylinder and setting deflection equal to the deflection of the radius of the d pene-tration and conservatively assuming its rotat equal to the local flexibility as if it were solidly ttached. It was assumed that the forces exerted on the h by the tube have negligible effect on the head. Location - 4 An interaction analysis was performed by divid actual structure into the following analytical ~e closure head was treated as a perforated spheri shell with modified elastic constants and the CRDM h long cylinder. The effects of the redundants

  • head were assumed to be local only
  • IPEC00069645

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069646

RIV000052A Submitted: December 22, 2011 20

  • for. any condition wpere there is interference the tube and head, no bending at the weld can Using mechanical and thermal stresses from th a fatigue evaluation was made for the J-weld.

tween ist. analysis, 6.020 CLOSUllE HEAD FLANGE AND SHELL A. Discussion of Results The maximum primary stress intensity at the ClnHIITP flange to shell juncture was 35.8 KSI for the plus design pressure condition. This stress s on the outside surface of the juncture of the head to flange and compares favorably with the allowable of 1. Sm~ 40 .KSI. The highest range of stress intensity for this 50.4 KSI on the inside surface and compares fa the allowable of 3 Sm = 80 KEI. The fatigue evaluation revealed that the higbes

  • usage factor was 0.015 and occurred for the out This value compares favorably with the allowab B. Method of Analysis The closure head, closure head flange, vessel f vessel shell, and closure studs were all evalua the same analysis. The actual structure was di the following elements: the closure head dome was as a long sphere, the closure head flange was trea ring, the vessel flange and studs were combined element with the flange treated as a ring and as cantilever beams fixed to the flange, and the shell was treated as a long cylinder.

Using the above described analytical model, an analysis was performed to determine the stresses the mechanical and thermal loadings for tbe h cooldown cycle. For the remaining transients, servative skin stress method was used for de thermal stresses. These stresses were evaluated of the strength and fatigue requirements of the

  • Boiler and Pressure Vessel Code, Section III .

IPEC00069647

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069648

RIV000052A Submitted: December 22, 2011 21 6.030 VESSEL FLANGE AND SHELL

  • A. Discussion of Results The maxtffium primary stress intensity at the flange to vessel shell juncture was 28.8 KSI boltup plus design pressure condition. This occurred on the outside surface of the junc flange to vessel shell and compares favorably allowable of 1.5 Sm ~ 40 KSI.

The highest range of stress intensity juncture was 45.4 KSI on the inside surface and s favorably with the allowable of 3 8m = 80 KSI. The fatigue evaluation revealed that the h cumula-tive usage factor was 0.005 and occurred for e inside surface. This value compareS favorably with allowable of 1.0. B. Method of Analysis See Section 6.020-B, Method of Analysis, CIa Head Flange and Shell *

  • 6.040 A.

MAIN CLOSURE STUDS Discussion of Results The maximum average bolt service stress for boltup condition was 3608 KS! and compares with the allowable of 2 Sm = 86.6 KSL For." plus operating pressure, the average bolt serv stress is 39.6 KSI and compares favorably with the al ble of 2 Sm = 73.5 KS! at temperature. The maximum bolt service stress was 95.9 KS! on the inside surface of the stud where it ent vessel flange. This stress occurred during th cycle of the 2500 PSI hydrostatic test and cam~ares favorably with the allowable of 3 3m = 116.4 A fatigue evaluation was performed on the stud the method outlined in Para. N-416.2 of the and Pressure Vessel Code, Section Ill. The cumulative usage factor for the studs was 0.31

  • inside surface of the stud where it enters the ~essel flange. The allowable usage factor is 1.0.

IPEC00069649

RIV000052A Submitted: December 22, 2011

                           *
                           *
  • IPEC00069650

RIV000052A Submitted: December 22, 2011 22 The maximum bearing stress between the closure tud

  • washers and closure head flange was 39,3 KSI. is stress occurred during the heatup cycle of the 500 PSI hydrostatic test and compares favorably wit the allowable of 1.5 Sm for the flange material.

B. Method of Analysis See Section 6.020-B, Method of Analysis, Closur Head Flange and Shell. 6.050 INLET NOZZLE AND VESSEL SUPPORTS A. Discussion of Results The maximum average primary membrane stress int for the inlet nozzle occurred at the juncture of the to the vessel wall on the LongitUdinal axis. Th of this stress intensity was 21.1 KS! and co ably with the allowable of 26.7 KSI. The same location gave the highest value plus local primary stress. The value of

  • sity was 32.3 KSI and compares favorably of 1.5 Sm ~ 40 KSI .

The highest range of stress intensity for the op transients occurred at the juncture of the nozzl wall on the outside surface in the longitudinaL The value of this range of stress intensity was and compares favorably with the allowable of 80 The bearing stress on the underside of the supp dead weight and the thermal pipe reactions only This stress was to be limited to 5.0 KS! under th condition. TI1e fatigue evaluation revealed that the highest usage factor was 0.042 and occurred at the nozzle wall juncture on the outside surface in the cir direction. This value compares favorably with th able of 1.0. The cumulative usage factor through nozzle wall and weld built-up support pad was fa to be 0.007 on the outside surface of the pad. B. Method of Analysis

  • For the analysis of the nozzle and nozzle to shel juncture, the loads conSidered were internal pressure, oper ting tran-Sients, thermally induced and seismic pipe react ,static IPEC00069651

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069652

RIV000052A Submitted: December 22, 2011 23

  • weight of vessel, earthquake loading, and and contraction
  • The stresses resulting determined in the nozzle by the use of the st formula for direct stress plus bending stress n a beam. At the juncture of the nozzle to vessel wall, these stresses were determined by the methods resented in references 19, 20, and 21.

The pressure stresses were determined in the performing an interaction analysis. The structure was divided into the following elements: in portion of the nozzle was treated as a cylinder, pered portion was treated as a tapered cylinder, the reinfor portion was treated as a cylinder, and the vessel was eated by idealizing it as a spherical segment of the th ickness as the vessel and with a mid-radius 1.5 times actual radius of the vessel. The thermal stresses for the operating transie determined by performing an interaction with analytical model .

  • For the fatigue evaluation, pressure stresses ed by the stress index method set forth in Art the ASME Boiler and Pressure Vessel Code, Sect Peak stresses resulting from the external load thermal transients were determined by concentr stresses as determined by the above described Combining these stresses enabled the fatigue e to be performed.

6.060 OUTLET NOZZLE AND VESSEL SUPPORT A. Discussion of Results The maximum average primary membrane stress int ity for the outlet nozzle occurred at the juncture of th nozzle to the vessel wall on the longitudinal axis. of this str~ss intensity Was 21.1 KSI and campa ably with the allowable of 26.7 KSI. The same location gave the highest value of a primary plus local primary stress. The value 0

  • stress intensity was 32.3 KSI and compares fa with the allowable of 1.5 Sm : 40 KSI
  • IPEC00069653

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069654

RIV000052A Submitted: December 22, 2011 24 The highest range of stress intensity for the rating

  • transients occurred at the juncture of the n02Z wall on the outside surface in the longitudinal The value of this range of stress intensity was and compares favorably with the allowable of 80 The bearing stress on the underside of the to vessel for the dead weight and the thermal pipe reactions y was 3.6 KSI. This stress was to be limited to 5.0 I under this condition.

The fatigue evaluation revealed that the highes cumulative usage factor was 0.022 and occurred at the nozz (' to vesse t wall juncture on the inside surface in the long tudinal direction. This value compares favorably with e allowable of 1.0. The cumulative usage factor through nozzle wall and the weld built-up support pad was to be 0.011 on the outside surface of the pad. B. Method of Analysis See Section 6.050, Method of Analysis, Inlet Ie and Vessel Supports for the method of analysis.

  • 6.070 VESSEL WALL TRANSITION A. Discussion of Results The maximum average primary stress intensity for the vessel wall transition occurs in the thin portion of th vesse 1 wall. The value of this stress intensity is 26. KSI and compares favorably with the Sm value of 26.7 KSI The highest range of stress intensity for the ating transients occurred on inside surface at the end of the taper. The value of this range of stress ensity was 37.9 KSI and compares favorably with the al able of 3 8m = 80 KSI.

The fatigue evaluation revealed that the highest cumulative usage factor was 0.002 and occurred on the outs e surface at the large end of the taper. This value is we 1 below the allowable of L.O. B. Method of Analysis

  • Stresses due to internal pressure were determ of a standard interaction analysis. For the pur this analysis, the actual structure was divided by means se of to IPEC00069655

RIV000052A Submitted: December 22, 2011

                          *
                          *
  • IPEC00069656

RIV000052A Submitted: December 22, 2011 25

  • the following elements: the thick portion of was treated as a cylinder, the tapered portion treated as a short tapered cylinder, and the th of the vessel wall was treated as a long cyl The thermal stresses were determined by the s method where it is assumed that the inside sur the vessel is at the same temperature-as the r coolant and the mean temperature of the shell the ~teady state temperature. This method conservative.

The fatigue evaluation was made on a where superposition of all transients consideration. 6.080 CORE BARREL SUPPORT PADS A. Dis.cussion of Results The most critical stress intensity occurred for e steady 125 KIP side load and steady 125 KIP vertical This stress intensity of 31.1 KSI occurred at the

  • corner of the juncture of the pad to the compares favorably with the allowable of The highest range of stress intensity occurred upper outside corner of the juncture of the pad wall. The value of this range of stress intens 40.8 KSI and compares favorably with the 3 3m of 69.9 KS!.

The fatigue evaluation revealed that the highes usage factor was 0.02 and occurred at the upper corner of the juncture of the pad to vessel wal

  • value is well below the allowable of 1.0.

B. Method of Analysis Thermal, mechanical, and pressure stresses at various locations on the pad and at the for the loads specified in reference 10. Mechanical stresses were calculated by the for bending stress in a beam, pressure stresses taken

  • from the analysis of the vessel to bottom head j and thermal stresses were determined by the IPEC00069657

RIV000052A Submitted: December 22, 2011

                           *
                           *
  • IPEC00069658

RIV000052A Submitted: December 22, 2011 26 "method of skin stresses. These stresses were

        *"'

6.090 into stress intensities and compared with the set forth in reference -/. Stresses due to the loads were multiplied"by a stress concentratio where applicable and used in a fatigue evaluat BOTTOM HEAD TO SHELL JUNCTURE A. Discussion of Results The maximum average primary stress intensity bottom head to shell juncture occurs in the cy shell portion of the juncture. The value of stress intensity is 26-.3 KSI and compares fa with the Sm value of 26.7 KSI. The highest range of stress intensity for transients occurred on the inside surface of the hemispherical shell. The value of stress intensity was 34.1 KSI and the allowable of 3 Sm ~ 80 KSI. The fatigue evaluation revealed that the high usage factor was 0.003 and occurred on the ins

  • at the start of the hemispherical shell. This well below the allowable of 1.0.

B. Method of Analysis is Stresses due to internal pressure Were de means of a standard interaction ana.lysis. of this analysis, the actual structure was divided the following elements: the cylindrical shell was as a long cylinder, the tapered portion of the shell tvas treated as a short tapered cylinder, hemispherical section was treated as a long sph shell. The thermal stresses were determined by the sk method ~ere it is assumed that the inside sur vessel is at the same temperature as the and the mean temperature of the shell remains steady state temperature. This method is cons conservative. The fatigue evaluation was made on a cumulative where superposition of all transients is taken consideration. IPEC00069659

RIV000052A Submitted: December 22, 2011

                          *
                          *
  • IPEC00069660

RIV000052A Submitted: December 22, 2011 27 6.100 BOTTOM HEAP INSTRUMENTATION PENETRATIONS

  • A. Discussion of Results The maximum average primary membrane stress in ensity for the bottom head is 26.5 KSI when taking in consideration of the ligament efficiency.

compares favorably with the Sm value of 26.7 At the location where the instrumentation nononr'~ attached to the bottOm head by the J-weld, the range of stress intensity is 53.9 KSI. This stress intensity Occurs on the inside surface favorably with the allowable of 69.9 KSI. The fatigue evaluation revealed that the highe usage factor was 0.14 and occurred on the outs of the tube. This value compares favorably wi allowable of 1.0. B. Method of Analysis An interaction analysis was performed by divid

  • actual structure into the following analytical bottom head was treated as a perforated spheri with modified elastic constants and the inst tube as a long cylinder. The effects of the re on the bottom head were assumed to be local onl assumed that for any condition where there is between the tube and head, no bending at the we exist. Using mechanical and thermal stresses analysis, a fatigue evaluation was made for the
  • IPEC00069661

RIV000052A Submitted: December 22, 2011

                           *
                           *
  • IPEC00069662

RIV000052A Submitted: December 22, 2011 28

  • 7.000 REFERENCES
1. ASME Boiler and Pressure Vessel Code, Sec III for Nuclear Vessels
2. Section III Code Case 1332-3
3. Section III Code Case 1335-2
4. Section III Code Case 1336
5. Section III Code Case 1366
6. Tentative Structural Design Basis for Reac Pressure Vessels and Directly Associated rn~n(~n~

(Pressurized, Water Cooled Systems) PBI51

                       . Department of Commerce.
7. Screw-Thread Standard for Federal Service,
8. Code for Pressure Piping, ASA-B 31.1-1953
9. Westinghouse Equipment Spec. 676497 dated
  • 10.

11. Westinghouse PAR's S. Timoshenko and J. N.

                         "Theory of Elasticity", McGraw-Hill, 1934
12. S. Timoshenko and S. Woinowsky Krieger, "Theory of Plates and Shells", McGraw-Hill, 1940
13. R. B. Heywood, "Design by Photoeiasticity",

Chapman and Hill Ltd., 1952

14. R. E. Peterson, "Stress Concentration Fac John Wiley and Sons, Inc., New York 1953
15. E. F. Bruhn, "Analysis and Design of Structures", 1949
16. P. G. Lawson, W. J. Cox, '~chanics of John Wiley & Sons, Inc., New York, 1947
17. B. F. Langer, "Applications of Stress I..Ol[1CEIn ion
  • Factors", WAPD-BT-18 IPEC00069663

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069664

RIV000052A Submitted: December 22, 2011 29

18. W. J. O'Donne1l~ "The Effects of Local Flexibility on Stresses in a Structure",

WAPD(CE)-170

19. P. O. Bijlaard, "Stresses from Radial Loads in Cylindrical Pressure Vessels". The Journal. Research Supplement. Dec., 1954
20. P. O. Bijlaard, "Stresses from Radial Loads and External Moments in Cylindrical Pres Vessels", The Welding Journal, Dec., 1954
21. Welding Research Council Bulletin No. 107, Local Stresses in Spherical and Cylindrical Shells due to External Loadings, K. R.

A. G. Hooper, and J. L. Mershon, August 196 *

22. Sampson, R. C., "Photoelastic Investigation Stress Distribution in a Perforated Hemisph Head .0£ Reduced Thickness" Westinghouse Re"'-'-l:;l1 Report 100FF996-R4 *
          *
  • IPEC00069665

RIV000052A Submitted: December 22, 2011

                          *
                           *
  • IPEC00069666

RIV000052A Submitted: December 22, 2011

         .'

APPENDIX A

  • DETAILED STRUCTURAL ANALYSIS r
  • IPEC00069667

RIV000052A Submitted: December 22, 2011

                           *
                           *
  • IPEC00069668

RIV000052A Submitted: December 22, 2011 A-I APPENDIX A DETAILED STRUCTURAL ANALYSIS TABLE OF CONTENTS

1. Control Rod Housing Stress Analysis and A2 - A24 Fatigue Evaluation
2. Structural Analysis of the Closure Head A2 - A5S and Vessel Assembly
3. Fatigue Evaluation of Head Flange, Vessel - AlOZ Flange and Closure Studs
4. Nozzle Code calculations - All3
5. Thermal Stress Analysis and Fatigue - Al77 Evaluation of Inlet Nozzle
6. Thermal Stress Analysis and Fatigue - A2S2 Evaluation of Outlet Nozzle
  • 7. Structural Analysis of Inlet and Outlet Nozzles and Vessel Supports Under Pipe Break Loads
                                                                    - A267
8. Fatigue Evaluation of Vessel Support Pads - A2BO
9. Structural and Fatigue Analysis of the - A30l Vessel Wall Transition
10. Structural Analysis of the Core Support Pads - A328
11. Structural Analysis of Vessel and Bottom - A340 Head Juncture
12. Fatigue Evaluation of Bottom Head to Shell A34 - A353 Juncture
13. Structural and Fatigue Analysis of Bottom A3 - A366 Head Instrumentation Penetrations
14. Nomenclature
  • IPEC00069669

RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. IENGINEIERINCI DE~ARTMIENT. CHATTANOOGA. TENN. .HEII:T'_ _....:;5~__ O",_-'2o...1.!.-.__ CHAItGIE NO. DATE 1-2-1-~ 7 BY~L..:' DESCRlnloN  ??41liCeL ,@,z.Q M,4/StV6= $Tft::'U A.wz <. J§IS CHECK DATE /. 2-1-~ 7 BY //)Ot?? /:' AV./2 iAmrvE EV.4L<<.9T1tW 5- OEWLEO .4&//11. >'$/5,' C2. - SYS'TEe? GEonET"er:

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7t.18 c : 5/3-167 /A/CO,v£L IPEC00069670

RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC. IINOINEIERINO DE,.ARTMENT. CHATTANOOGA. TENN. CHARG.NO,____~--__- - - DUCRlflTlON &,(/7@'= ROD /hv.fij.I{r '>7.e~S5 A0""Y,5/5cHECK

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  • 1- /#£ AYEKnc;£ 5,t/l}u Mr PIt'Essp,ee ExeE£D 2.5,kil, 2_ THE laAI.. Ptf?I"""';~Y P,e/,H4,RY Sn?/?'s5
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                /v'- /5.2 r1/,c ~C71(}Af N.

IPEC00069671

RIV000052A Submitted: December 22, 2011

                           ,

COMBUSTION ENGINEERING. INC. NUMBIEI' S-/W-P I A-4 IENGINEIERING DIEJOAIITMIENT, CHATTANOOGA. TIENN. .HIEIET_____1~ ___op,____Z~1____ CHARGI: NO DATE /-2~-~7 By~a DDCRIIPTION tCwrgoL &0 JJUS/Jlj';;' fiRE$'£ AwtL >$/S CHECK DATE /- 2<1-t4 1 BY~ Ava brtTlWE £VQLt.l'i 7lRA./

  • 5_ Lk14JL9 44/11.. >ISIS' d_ US/(r,v .5/Z/NtT :

I i)SICrAi h~$$ veet = l? 5 Ks I

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I I t 5A IfZ-Ffhf, S",,, /S..3,k'SI(FRdA-/ Sr,;} i?'" 1.37S*' f.9c!T ::. t'J;r'OZ5" I I P ~ Z>.i!.J1 I

  • THE tJ.~2S" /leTlNIL /N/l!,e,vns Is AL/~<?M TE' hI? &-1-1 f1FfTE~II'ILS ; J/EM!e:, (RI7E"f?/tJ.(I S"-C-I /5 S'",7Isne-o.
  • IPEC00069672

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC. ENGINEERING DEPARTMENT. CHATTANOOGA. TENN. CHARGaNO'_____________ DESCRIPTION COAl7&a<. & 0 4(.)$1&16'= .>'TR§S d,vAL.YSlS

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RIV000052A Submitted: December 22, 2011 I COMBUSTION ENGINEERING, INC. NUMBER 5'-IPO-P I A-/4 ItNGINEERING DEPARTMENT. CHATTANOOGA, TENN. SHEET'--_ _ '_1_ _ OF'_-,:,-,}7'--___ ______________ DATE/:z{.-~ 7 BY~ CHA~G.NO'

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEEf4!ING, INC. IENGINEER/NG DEPARTMENT. CHATTANOOGA. TENN. CHARGE NO'_ _ _ _ _ _ __ DDcRIPI'ION 57,...1/(17"<<£8L AuAt!YS/s i?F ,wE 4p.fPRe _~ ,APQ kffssa /?SSG".#I5L y 5_ L).£7f(/t.FO ANALYsIS:

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC. ENGINEERING DEPARTMENT. CHATTANOOGA. TENN. SHEET___~______ I~~--~----- CHARGE NO'______________ DESCRIPTION 5'"7-e(/<7(/~m_ AA/r1LY515 CJF 7(Je- &asvee CHECK DATE---f.~!::..!:...~~-BY I/I'/O Ilvo JlES5EL.. A.5SrH(f2 y 5_ OC'rPILD AA/4L Y5'I.5: c_ SYS?£M dLL"WFJ{fLE$: 8_ 7Ht?' !1V/?e/l&<2' .t?E/l-eIU($. STRess SHAU. ~7 EXtfcFJ1) 47.4en.Ml. HET" 7E;JfP£~FJ7VKc. nil TEA~II1L

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. NUMBER~:~,-~/~~O~-~~_____LI~A~-~2~8~ ENGINEERING DEPARTMENT. CHATTANOOGA. TENN. SHEET__~B~______'OF __~2~f~___ CHARGE NO ______________ DAT~E______;._V_-~2~2~-~b=S~_IBY<!~**KK"LI.

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RIV000052A Submitted: December 22, 2011 CO~SUSTION ENGINEERING. INC. IQ\IGlN~ING D~ARTMIENT. CHATTANOOGA. TENN. CHARG. No,_ _ _- -_ _

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RIV000052A Submitted: December 22, 2011

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC. ENGINEERING DEPARTMENT. CHAlTANOOGA. TENN. CHARGE 1-/0._ _ _ _ _ __ 5i£W7(/Rf)~ @at. y's"x Uk mE ~a5'¥,C

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. SHEET__ ~ ______OF____ ~ ___ ENGINEERING OEPARTMENl". CHATTANOOGA. TENN. DATE 1&- 2 2--{;S BY~U. CHARGE NO' ______________

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RIV000052A Submitted: December 22, 2011

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                    ~ION ENGINEERING, INC.

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                      £J;; ,. 0 IPEC00069702

RIV000052A Submitted: December 22, 2011

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RIV000052A Submitted: December 22, 2011

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RIV000052A Submitted: December 22, 2011 COMlIUST'ON ENGINEERING, INC. DlGlN....ING Da-ARTMIENT. CHAlTANOOGA,'TENN. CHAIICNE NO _ _ _ _ _ __ aucItIPrION 5tru4T!.1KIJ' AIVIU. 'ISIS t!F 7#F 44SVtE'~

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. NUMBER 5-/5t:J-p IA-38 ENGINEERING DE~AJtTM.NT. CHAtTANOOGA. TENN. SHEET 1t3 Op*_ _2::..L9_ _ CHAItGI: NO DAT- /O-Z2-t..5 8y('"",,eReU DUCItIP'TION ~Te~7U.Rdf IlYALY'$!S tJF?;;r a()$VRC CHECK DATI' /tJ-?l-6a> BY,.4U>(,q,(lO~

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                            -7'1. 872tp IPEC00069706

RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. DlGtNURING DEPAIITMKNT. CHATTANOOGA. TKNN. CHARGE NO_ _ _ _ _ __

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC. NUMBER §-(;;tJ-P IA-4D ENGINEERING DEPARTMENT. CHATrANOOGA. TENN. SHEU*_.....:;.2;:..CJ_ _ O I" 2. 9 C H A ~ G E N O ' _____________ It}* 2 2-(,,5 BY~Ck"ReU DATE gUCRIf'TION S*7RVC7WM4 ,4""&tY~/f tJ"" 7#E Ct.tJS?,,e4" CHECK gATE /tJ-]Z-t,5 By.4L.~,("'.t:JGR

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. IiNGINEIiRING DEPARTMENT. CHATTANOOGA. TENN.

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  • IPEC00069709

RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. NUMBER 5-/5&-P I A-42 ENGINEERING DE ..ARTMENT. CHATTANOOGA. TENN. SHEET :2 Z 01"';" 2' CHARGE NO, _ _ _ _ _ __ DATE /t?-22-b~ By("<X~ReU

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Submitted: December 22, 2011

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RIV000052A Submitted: December 22, 2011

                    ~JON ENG~G;                                            INC.

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Submitted: December 22, 2011

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  • RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC.

ENGINEERING DEPARTMENT. CHATTANOOGA. TENN. CHARGKNO_____________ DUCIIIPTION 5"revc rv'R& bAt Y~I.S tJ,..- ZN, 6tJst/~F

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  • IPEC00069715

RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. NUMBER 5'-/5&-,0 I A*48 ENGINEERING DE~ARTMENT. cHATTANOOGA. TENN. .HEU 1.8 01" Z '7 CHARG.NO'______________ DATE 1~"22jf5 BY~~ A,(II2?'1s/.$ tlr Me /t'- ~2~5 BY~R.

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. ENGINEERING DEP'ARTMIENT. CHATrANOOGA. TENN. CHARGI!: NO,_ _ _ _ _ __ ST.I!"v~ rVR191. AMAI. >51$ tJ~ -1Yr 4"',teR

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. NUMBER s"-IS()-,D hA I A-50

               , ENGINEERING DEP... RTMENT. CH...TT...NooG.... TENN.                SHI:ET          I           OF'_L1_ __

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IPEC00069718

RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. IENGINIEI:RING DE..ARTMENT, CHATTANOOGA, TENN. CHAROIENO_____________ DDCRIPTION Ilp~e&a!)( 70 s-/s{)-P

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RIV000052A Submitted: December 22, 2011 I COMBUSTION ENGINEERING. INC. NUMBERS-ISO--/' Ike, .&/ A 52 ENGINEERING DEPARTMENT. CHATTANOOGA. TENN. SHEET 2 OF---'3"'-_ __ CHARGE NO _ _ _ _ _ __ DAT~E_ _2-1_-~2~6:...-.:::6~B_ _ IBY {'OO.'.I?C:U

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  • IPEC00069720

RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. ENOINIEIERINO CE~ARTMIENT. CHATTANOOGA. TENN. CHAROIENO'_____________ Cac:RIPTION /lpeEl/alX' ze 5-/.>tJ-,P

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RIV000052A Submitted: December 22, 2011 INC. NUM

  • CHATTANOOGA. TENN. SHEET 1 OF 2

CHARGE Net DATE 4-2')-68 BY Cockrell DESCRIPTION AE:E:eildix to S-l50-P CHECK DATE BY_ _ _ CLOSURE HEAD PENETRATION SPACING:

  • The general requirements for spacing of openings in spherical shells (such as a closure head) are given in Paragraph N-45l of the ASME Code Section III.

Additional requirements are given in Article 1-6 of Section III as referenced in N-45l(e). The spacing of the closure head penetrations meet the requirements of Paragraph N-45l with the exception of 1-6l3(b) of Article 1-6. Paragraph 1-6l3(b) states that tiThe arc-distance measured between the center lines of adjacent nozzles along the inside surface of the shell is not less than three times the sum of  :>~r~\

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their inside radii for openings in a head **** ". This requirement would restrict the ligament efficiency to a minimum of 66.7%. The actual ligament efficiency of the closure head is 66.6%. Since the actual ligament

  • efficiency deviates slightly from the required minimum ligament efficiency, Paragraph 1-620 of Article 1-6 must be met. Paragraph 1-622 of Article 1-6 states that 'lIn accordance with 1-1012, re-evaluation is not required for configurations for which there are available detailed experimental results that are consistent with the requirements of Article 1-10."

The purpose here is to use the results of Westinghouse Research Report 100FF996-R4 to show that the closure head penetration spacing is satisfactory for the closure head. The ligament efficienty of the penetration spac-ing in this experiment was 38% which should more than suffice to show that the closure head's ligament efficiency of 66.6% is adequate. The results from the above report show that the membrane portion of the stress due to internal pressure can be accurately calculated by dividing the primary membrane stress in the unperforated region by the ligament efficiency. See the discussion and results given on pages 23 and 24 of the above report. It is shown there

  • IPEC00069722

RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. ENGINEERING DEPARTMENT. CHATTANOOGA. TENN. CHARGE NO'_______ DESc:RI""IONI--!A=pJ::p.:::e.!.!n:.:::d~ix=-...!:t:.::o:.....:S=---=1::.,5::..:0::...--=P=-______ CHECK ..A.T...._ _-+__ .n CLOSURE HEAD PENETRATION SPACING: that the calculated value of the average primary membrane stress deviates from the experimental va by only 2%. The higher value being the calculate value; hence, the method of dividing the required thickness in the unperforated region by the lia~m~nr efficiency is valid and reasonable. This method used to obtain the thickness of the closure head. The stress indices to be applied to the computed membrane stress intensities for a fatigue analys as determined from the results of the experiment 1.05 and 1.44 for the inside and outside surfaces respectively. These values are well below the required index of 2 for both the inside and outs surfaces from Article 1-6 of Section III. It is, therefore, concluded that the slight deviation the spacing requirement in I-613(b) is insigni

  • both from the standpoint of establishing the requ head thickness and for fatigue considerations .
  • IPEC00069723

RIV000052A Submitted: December 22, 2011

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERI",G. INC. ENGINEERING DEPARTMENT. CHATTANOOGA. TENN. CHARGIENO'______________ DEllCIlIPTION h T/&V<"" AMtfl£ Y4b c2E &/'10 n/'lMc.-.rr

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENCINEERING, INC. IA 58 ENGINEERING D~AltTMaNT. CHATTANOOGA. TENN. .HKET*____~7_____ op,___~51____ CHARGE NO'_ _ _ _ _ __

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IPEC00069726

RIV000052A Submitted: December 22, 2011

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                   & (1//             ;t IPEC00069727

RIV000052A Submitted: December 22, 2011 i COMBUSTION ENGiNEERING. INC. ';NUM**,{t.)$'!~,o :<- IA'O _GINEERING DEPARTMENT, CHATTANOOGA. TCNH. ' .HUT """9 0.. 5/

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I IPEC00069728

RIV000052A Submitted: December 22, 2011 COMBUSTION f;NGU1i~J:RING, INC. m9'H~'HG OP"RTMIN'T. c::HA.1Tt.H~. TPN* CH/l1'I9.!I' ~------

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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. lINe. NUM.E"-'-S.....

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