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{{#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$ | ||
In the Matter of: | |||
ASLBP #:07-858-03-LR-BD01 Docket #:05000247 l 05000286 Exhibit # | 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Docket #: 05000247 l 05000286 Exhibit #: RIV00052A-00-BD01 Identified: 10/15/2012 Admitted: 10/15/2012 Withdrawn: | |||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 | ||
* IPEC00069602 | L/j' ANALYTICAL REPORT FOR INDIAN POINT REACTOR VESSEL UNIT NO. 2 COMBUSTION ENGINEERING, INC. .i: Ii, 1:_ Cockrell CHATTANOOGA, TENN. Lowry* | ||
IPEC00069599 | |||
* | |||
'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 | ||
* | * 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.&: | 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 | ||
* | |||
* 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 | * | ||
* IPEC00069607 | * | ||
* * | * IPEC00069606 | ||
* | |||
RIV000052A Submitted: December 22, 2011 | |||
* DISIRIBUTDpN LIST No. Ot COEies | |||
{/!. S. F. P. Hill | : 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 | |||
: 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 ********************* | |||
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 | ||
Zl-22 6.050 Inlet Nozzle and Vessel Support ************* | RIV000052A Submitted: December 22, 2011 | ||
* | |||
* * | * | ||
* IPEC00069612 | |||
23-24 | |||
******************** | |||
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 | ||
* IPEC00069615 | 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 | 2.030 ~ | ||
40 years | ~ 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 | ||
* 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 | |||
* | : 1. Plant heatup at 100°F/Hr. 200 | ||
"?r>o }/t?W'lil/& | : 2. Plant cooldown at 100°F/Hr. 200 | ||
: 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 | : 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 | ||
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 | : 10. Hydro test 2500 pSia 5 | ||
* * | : 11. Steady state fluctuations 5 106 | ||
* | : 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. | ||
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 | ||
* | |||
RIV000052A Submitted: December 22, 2011 | |||
* | * | ||
-1). The value of this range of stress in is 50.4 KSI and compares favorably with the allowable 0 Fatigue Evaluation | * | ||
Location -1 U '" 0.004 Location -2 U '" 0.015 The maximum allowable usage factor is 1.0. | * 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: | |||
-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 | ||
* | |||
* * | RIV000052A Submitted: December 22, 2011 | ||
* | * | ||
* | |||
* 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 | 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 | ||
* | 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 | |||
* 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 | * | ||
* compares favorably with the allowable of 1.0. IPEC00069631 | * IPEC00069628 | ||
* * | |||
* IPEC00069632 | RIV000052A Submitted: December 22, 2011 11 5.040 | ||
* MAIN CLOSUJY; SIJ.!!2S A2~~ag~ Bol~ Stress; j \ | |||
* | \ \ | ||
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. | \ 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 | |||
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 | * ,--, | ||
* | I The bolt 3* | ||
* * | I This stre~s occurred dur | ||
* | , | ||
* | \ I | ||
* | / 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 | \ | ||
* * | \ | ||
* IPEC00069642 | / test. This stress I | ||
\ | |||
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 | 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 | ||
* IPEC00069644 | ** | ||
the heatup cycle of the 2500 psi hydrostatic test | |||
* 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 | * | ||
* | * | ||
* * | * 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. | |||
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 . | 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 | |||
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. | |||
* 6.040 MAIN CLOSURE STUDS | RIV000052A Submitted: December 22, 2011 | ||
The maximum bolt service stress was 95.9 KS! | * | ||
* * | * | ||
* | * IPEC00069632 | ||
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 | * 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 | |||
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 | * 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. | |||
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. | ||
* 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 | * | ||
* | * | ||
* * | * 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 | |||
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. | * 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. | - 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 | |||
* | |||
* | |||
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!. | ||
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 | |||
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. | ||
IPEC00069659 | |||
* * | |||
* | RIV000052A Submitted: December 22, 2011 | ||
* | |||
* | |||
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 | |||
* * | 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'~ | |||
* | 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 | 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 | * 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 | |||
* | |||
: 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 | ||
* 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 | ||
.' 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£ 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 | |||
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: | |||
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DATE/:z{.-~ 7 BY~ | |||
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. | |||
£NGINIElERING DEPARTMENT. CHATTANOOGA. TENN. | |||
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC. NUM8ER~~~-~/o~~~~~-~_____LI~A~-_~~b~ | |||
aNOINEERINO DEPARTMENT. CHATTANOOGA. TENN. SHEET*_ _.L IQ L-._OF*_--,Z=:.L 1__ | |||
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* IPEC00069684 | |||
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. | |||
ENGINEERING DEPARTMENT. CHATTANOOGA, TENN. | |||
CHARGE NO _ _ _ _ _ __ | |||
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~"'IJ6f (IE'/TE.eltJAJ 5-C -.3 Submitted: December 22, 2011 | |||
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____ | |||
CHARGE NO,____________ DAT*~F____~/~*2~4~-b~7~___ BY~~i DIESCRIPTION LOA-/TRP'- | |||
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. | |||
ENGINEERING DEPARTMENT. CHATTANOOGA. TENN. 8H"'&1~_ _ -='--__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_____ | |||
CHARGB NO DATE /- 2(. -&,1 By~L DESCRIPTION 5-8- | |||
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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 | |||
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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'_ _ | |||
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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. | |||
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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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COMBUSTION ENGINEERING, INC. | |||
ENGINEERING DJ:~ARTMENT. | |||
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CHATTANOOGA. TENN. | |||
NUMBER 5'-/50...,0 SHEET i 0 IA-:30 0f'_-"2""'9'--__ | |||
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IPEC00069698 | |||
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 | |||
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~ION ENGINEERING, INC. | |||
lIN. . . . . . . . DEPARTMENT. CHAtTANOOGA. TIENN. | |||
_ _ NO_ _ _ _ _ __ | |||
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IPEC00069701 | |||
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'_ _ _ _- - - | |||
DESCRIPTION S ZKlk!TV.e#", 4vm. 'iSIS tJF &#" t!.wS ORe:" | |||
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CHECK DATE ,/0-21.-'5 By)LEJ(~.fR | |||
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£J;; ,. 0 IPEC00069702 | |||
RIV000052A Submitted: December 22, 2011 | |||
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COMBUSTION ENGINEERING. INC. | |||
lENGU... 'c~~Na D.~AIITMDIT. CHATrANOOGIA. T.NN. | |||
CHAIIa& NO_ _ _ _ _ __ | |||
DUCRIPTION S7RP<!;P~!.u. A",IU,Y..fIS & mE 4&1s~,e" | |||
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RIV000052A Submitted: December 22, 2011 | |||
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COMBUSTION ENGINEERING, INC. | |||
ENGINEERING ElE~AIITMENT. CHATrANCOGA. TIENN. 8HElETc_"-lI/.;..!..-_ _ _OF 71 CHAIIGKNOI_____________ DATE /1?-22~~ Byc1qckcFLt_ | |||
DIESCRIPTION 57..evc! TVA!'Q4 "'<<'.IlL "'SIS (?,-'?yo¥" 6".5.:-'126" CHECK gATE 1()-zz-65 ByAax/ljlIl)fi~ | |||
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RIV000052A Submitted: December 22, 2011 COMlIUST'ON ENGINEERING, INC. | |||
DlGlN....ING Da-ARTMIENT. CHAlTANOOGA,'TENN. | |||
1 | CHAIICNE NO _ _ _ _ _ __ | ||
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IPEC00069705 | |||
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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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 | |||
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:"¢<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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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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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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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. INC. | |||
ENGINEERING DEP'ARTMIENT. CHATrANOOGA. TENN. | |||
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= /2.30 1 <. ;Z~tfKSI '1.10 0 1 < /6,~2.t:'JI IPEC00069717 | |||
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_ __ | |||
C:HARGIENO D ...TE J-/jJ-~&. BY~.c,- | |||
DESCIIIPl'ION k?w84'4.'£ <<5/4=# 57-'{':SS t4wc CHECK DAT'Ij;E:_ _ _ _ _ BY_ _ | |||
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('L~D Oe'p&$/,T ~-~E iJEre>eMI,v1!'1!) B y C:E. WELO/P& | |||
5'PR. HIJ - 38CT(I) rlMtJ S/fA -38 (c) , I#E £esV£TS ~r 7#~ | |||
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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 | |||
/.v /#/5 ;'7PP.!F',vCl/X / 7,¥E S#E'14,;e AM,:) ~"'EA/T AT C~.r-/ | |||
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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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* 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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()r: 7#£ /lveISEC'" ,)/icET 26 tfJF S -/.J"eJ-r>>, | |||
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 $-/5/-;:;> *t43~ | |||
ENGINEERING DEPARTMENT. CHATTANOOGA. TENN. 8HEET'__~5~____'OF SI CHARGK,NO'_______________ DATK~__~5~-~/Z~-'~~~_____ BY~'4 | |||
* DIESCRIPrION Fi?TKcVE Ea:y.V9??ftr<.! & PFA'.o F4f&E, CHECK DATE 5'-Il. -G';' BY~ | |||
V£S5C4 h!9A/ff ,4,11/0 &~"'<< S7VOS 5_ DE/A/LEO 41/IflLYSI$: | |||
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* IPEC00069724 | |||
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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//-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'_ _ _ _ _ __ | |||
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DATW~ ___9~~~-~/1~*~~~~__ BY~~ | |||
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1- ,4,11[1£ YTf£'(U. )4,U'1. | |||
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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.)$'!~,o :<''- IA'O | |||
_GINEERING DEPARTMENT, CHATTANOOGA. TCNH. ' .HUT """9 0.. 5/ | |||
~GKNO' ____________ | |||
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I IPEC00069728 | |||
RIV000052A Submitted: December 22, 2011 COMBUSTION f;NGU1i~J:RING, INC. | |||
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IPEC00069729 | |||
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING. lINe. NUM.E"-'-S..... | |||
-/ 5._I--'-P | |||
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I!NGINEERING DEPARTMaNT. CHATTANOOGA. TENN. SHIEItT II 01"_--:;;.5...;..' _ _ | |||
CHARGa NO DAft .5"-/2 -be. | |||
vkzzl?Ai | |||
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* i IPEC00069730 | |||
RIV000052A Submitted: December 22, 2011 COMBUSTIQN ~ INC.. | |||
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Revision as of 19:11, 11 November 2019
ML12335A575 | |
Person / Time | |
---|---|
Site: | Indian Point |
Issue date: | 12/22/2011 |
From: | Combustion Engineering |
To: | Atomic Safety and Licensing Board Panel |
SECY RAS | |
References | |
RAS 21634, 50-247-LR, 50-286-LR, ASLBP 07-858-03-LR-BD01 | |
Download: ML12335A575 (134) | |
Text
{{#Wiki_filter:United States Nuclear Regulatory Commission Official Hearing Exhibit 5,9$ 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:
,- / ~ L CX/JT/eAi MJ9URI'1L: FLFJAH;': SA-I":? TYPE30¢ S>I'1//JU$; S-~'i.
7t.18 c : 5/3-167 /A/CO,v£L IPEC00069670
RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC. IINOINEIERINO DE,.ARTMENT. CHATTANOOGA. TENN. CHARG.NO,____~--__- - - DUCRlflTlON &,(/7@'= ROD /hv.fij.I{r '>7.e~S5 A0""Y,5/5cHECK
'. be rr971MIE EJ//i/..vl9w1"l 5_ LJU&L.g.q, AU(k A,'
- b. 5Y57g,v; LtMQS,'
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2- t)PE.RA71A/trP~ess//R;O.-: Z:25~5'1 Ar t'l,PE,e,.t;T//f/q- 1£ 3-?iii /IiEIt'/-tAi- AM/) Ptf"ESSV!}F 7:eAJ(}51E'A.I~ 45 cTl N.e. 4tG cO"v7.eOi Roo ~V.,5I'<//Sc To CJ..OSVRE .4-19.0 THE rou-PWlAoIfr Au"WA9t.E S'TRE.S"SES ;#tf?E .8rJ,SE.D L# iVVClE,q,.c;' COPE Secr/lhtJ JZT.; RErE'E,vC'E' I /lA/£) FbR I#IS A,v-'U"YSI,S ..
- 1- /#£ AYEKnc;£ 5,t/l}u Mr PIt'Essp,ee ExeE£D 2.5,kil, 2_ THE laAI.. Ptf?I"""';~Y P,e/,H4,RY Sn?/?'s5
~ AT UESNTAI /A.lTEAlS/TY AC:KOSS S-ZRG'SS has 7#£ ,4l/o6",("-"'CrF .50,10 5ECT/OA,/ ~h".P, (650~) Avo . . ..,,"'81',...
Y :;;rR~.ss 5,t//Qt.L /L0T EYCEEO /.5 ~ 47 ~5'O"r:
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RIV000052A Submitted: December 22, 2011 COMBUSTION ENGINEERING, INC. ENGINEERING DEPARTMENT. CHATTANOOGA. TENN. SHEET___~______ I~~--~----- CHARGE NO'______________ DESCRIPTION 5'"7-e(/<7(/~m_ AA/r1LY515 CJF 7(Je- &asvee CHECK DATE---f.~!::..!:...~~-BY I/I'/O Ilvo JlES5EL.. A.5SrH(f2 y 5_ OC'rPILD AA/4L Y5'I.5: c_ SYS?£M dLL"WFJ{fLE$: 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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RIV000052A Submitted: December 22, 2011
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RIV000052A Submitted: December 22, 2011
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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
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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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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
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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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RIV000052A Submitted: December 22, 2011
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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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