ML18046A854

Seismic Design Evaluation of Palisades Unit 1 Main Components.

ML18046A854
Person / Time
Site:	Palisades
Issue date:	07/31/1981
From:	ABB COMBUSTION ENGINEERING NUCLEAR FUEL (FORMERLY
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ML18046A852	List: ML18046A851 ML18046A853 ML18046A854
References
NUDOCS 8108110536
Download: ML18046A854 (109)

Text

{{#Wiki_filter:* Seismic Design Evaluation Of The Palisades Nucelar Power Plant

• s1os110536 8Io863\
• PDR ADOCK 05000255 P PDR
• Unit 1 Main Components July I 1981 Combustion Engineering, Inc. Windsor, Connecticut
• *** Title 1.0 PURPOSE 2.0 SCOPE 3.0 METHOD OF ANALYSIS 4.0

SUMMARY

OF RESULTS 5.0 APPENDICES Table bf A. REACTOR VESSEL REANALYSIS B. STEAM GENERATOR REANALYSIS C. REACTOR COOLANT PUMP REANALYSIS ' .

• ** rt x . n**oe
• r'tl * ..... .-..... -PURPOSE: This report presents the results of an evaluation of the reactor coolant system main loop components for the effect of higher seismic accelerations than used in the original designs, in accordance with the findings of the Systematic Evaluation Program reported in NUREG/CR/1833.

2.0 SCOPE

• This report provides results 6f analyses of the Palisades Nuclear Power Plant Unit 1 Reactor Vessel, Steam Generator, Reactor Coolant Pump and their integral supports.

3.0 METHOD OF ANALYSIS: The original component stress reports were utilized to determine the areas of maximum stress. These stresses were then recomputed using the new seismic accelerations. The new resultant stresses were than compared to allowable stresses to determine acceptability. For the reactor vessel, analyses were performed at the outlet nozzle, the inlet nozzle and the support lugs. The original stress report did not separately list the input loads for pipe* rupture and seismic; the two were surrmed. To be conservative the sum of the pipe rupture and seismic 1 oads were *increased by the largest ratio of new seismic acceJeration to original seismic acceleration (i.e. in the vertical direction .34g/ .* 312g). For the steam generator, analyses w'ere performed at the primary structure (support skirt) and upper support lugs. For the nozzles and support skirt, new seismic loads were generated by applying the new seismic accelerations ( .64g horizontal and *.49g vertical) to a computer model of the reactor coolant system utilizing the *MEC-21 piping flexibility analysis program. For the upper support lugs, the original seismic loads were increased

• by the ratio of the new seismic accelerations to the old seismic accelerations

{. 346g horizontal and .133g vertical). Resultant seismic stresses were combined with the pipe rupture stresses at the inlet and outlet nozzles. Seismic stresses were considered alone for the primary structure and the uppe.r support lugs. *All resultant stresses were then compared to the original. stress allowables

• For the reactor coolant pump, the pump volute, inlet and outlet nozzles and support lugs were investigated.

The original seismic stresses were increased by the ratio of the new seismie accelerations (l.27g horizontal and .34g vertical) to the original seismic

• accelerations

(.55g vertical and horizontal) the maximum stress intensities were then conservatively calculated by adding the new seismic stresses to the original pressure and thermal stresses. The combined stresses were compared to the ASME Code S:ection III Par. F-1323.1 allowables. 4.0

SUMMARY

OF RESULTS: At all locations the new stresses resulting

• L____

from the new seismic accelerations were less than allowable stresses. The existing designs are therefore capable of withstanding the new seismic accelerations . .... . ..__ =iJ POV./ER SYSTEMS

• C0 1.IBUSTION ENGINEERING.

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• lt-4 Page Number = 39, '?7 /CS I < /, .S-Sn-i :: K5 I

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FRoH /HE S1G/'.J1F1C'.L1Nr (sec. s:o90 . c) 771c /l#JX//Yt/"'f NE11'1B/?ANc T BEND/IVG STR*:55 /N/cNS/IY JS //\) /#*' Ycs.SEL H/9LL T'D /dt.*T /YOZZt.£ #0 OF 22 (iCCA710/\J BL) !=Ro/If SllcE/ A-230 (f:jA-18)

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• Co11e1tJC.JJ STR£S:S INravs1TY(fM -rPa)-=-.. 89 Ks/ </.!Sy"= ¢5.50-51
• ----*---.

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• 11/iA:: (PIPE' Be£"11<+ :5:5* 5£JS111c). . ,312

SYSTEMS COMBUSTION ENGINEERING. INC * /J-/0 . Page Nurriber OU/Lt=/ J/ozzL.E (PART I[ coNrb) V7 (CE5;c;.v PREs:s) = -Z. S-.KS I ,-( . "" .34 -V;t.r; /VIA PJPE LDr7Dy = -0, 7 :3JZ = 0. 7h KS/* vx +re I IVX.-'V@'\ z. ;?_ _ 2 . +'\f \: . z / +-.::r -..38 . .,t'G Ks I r..eo11 SNc:e-775 A-30/ f. A-302 .* /1;..27. ¢ lt-28) . Srass FOR CbHB1NED r' 8*tJD1A)q ONLY /17c; /'11-/A LOADS Nill. 8*' l/11C.*c-15GD. Ji; (Dr=.51c;iJ PRcssoee) = _T:?. 7 . / "\ /.. ,,\ l7X \/1H>i P1P1E == r...-5.5 r--1( .312 = -/.5..3*"K5/ D°X (TOr/1L) = 7, 7-/.53 =. 6,/7 KS/ . .. VB. (05SIGN . PRC.SSURE)

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=. 59.0b \.:._ '-' . '< Veht.e()UJ TED

SYSTEMS COMBUSTION ENGINEERING. INC ...... * :.. -A-/'2. Page Number VESSEl

• SuPPORIS FR0!-1 lflE" :5JGNIF/CA///

RE"SUL./S A-29) I 1"1/'9XJHVH C!.0!113/f'/ED PR!HARY Sl'R*S.S (BEND!Nq' + COHPRE'SS;oN) . + Q$ = Z4,5 KS/ ,./ .34 .31Z </.SSh? -::: f't> KS/ ff !1rtx111u11 ?R11-1ARY S1R.:-.ss Co11017/0A/, +vs = 5a o KS/ . I Al'cN sr.ec-ss = ,3 12 x 5tJKSJ z (Sr +Sv) :::. 60,7 KS/ .llT /11'9X/t1UJ1 SHclJR STR*SS DVRJNCj ACCIDENT CtJ!lorr;oNs ST,e£:ss = x. 14.8K.51 = Jb.J3 < ,\ ,312 '-',,} : 30,C> 1---------------------

• J he :

5.080 INLRT NCZZLE (PART I) I\. Abstract * \ . '* .. Th.l:;; a11alysls presents the structural evaluation 1.">f' the inlet for coridi Stresses* are th1.)se t I 11g fr*l"*m in t.ernal preSl:!UI'e, pipe 1011s, support a11d enrt11quake loadl11g. (s .... t*heet.:J A200 thru 1\222 of I\ J'CII' dt*la.lled B. ---J..,, _ Nozzl:__ _ Cut 3 Cut 2 Cut 1 C. Slg111f1cunt Results The reuctol' vessel ir1let nozzles are simultant!ously acting design loads. determ1r1ed in this analysis are less bles. J Vessel ., A .. A,, I I \ \ l I D \ \ J--+:--:.1:.l 1lt 10,, \ \ I I ... 8L. e,,, a de qua te to withstand the* All stress intensities than the required allowa--

• * ,.i 5. 080 HILE'J, NOZZLE (PART I) c. Sig11.if'icant Reaults (Cont'd) ., ... , __ ., 'l'he most cri t.lcal primary membra11e s t.ress 11°1te11s1 ty in au itrlet nozzle occurs Cut "l". Th18 s L.ress l11te11;:;.l t:.r of' 13. 75 ksi (see 3h. A218) is less than the Sm allowable 01* 17. 4 ksi. The most cri tlcal plus local primary st:res3 intc113l t;-.* in no.zz.les occurs at Cut "3" (see Sh. A220). 'l,hls lntens1 t:r uf 12. 7 ksi is less than the 1. 5 Sm allowable

.._.,f 26.1 ksi. The most critical general plus local primary stress intensity in tne vessel wall occurs at location Bu (outside) of inlet nozzle No. 4 with the friction forces acting radially du r. This stress *intensity of 39.4 ksi (see Sh .* A22a) is less than 1.5 Sm allowable of 40 ksi. D. Discussion of Analjsis This calculation demonstrates the .adequacy of the main coolant nozzles to serve a.s vessel supports in addition to perforining their primary.func:tion. The nozzles with support pads support the dead weight or the vessel and sustain the loads due l.(> pipe reactions and earthquake. The 3upport n_ozzh*s have flat pads .integral wl th the nozzles. The pads :ire assumed 1D be free to move radlallv on the . ' M bear*Jng plates but guided to prevent rotation of the vessel

• I I I I l . . * * .... *-* * ** .* *.* . ' * * .* -. . .. :. . *.

.;....:; ... ;;;:.-.,,,;;w:-o;,.,,, ,. ... ,! .... ,,.,. *. . . : , **.. '\' ut-I ... /et* ,."1!* oui" GENERAL -AL PRIMARY STRESSES sra:s OAD * ::> 1 RESS EQUATIONS Au AL u BL Cu CL D11 DL 'DESIGN PRESSl2.q6BOI p or* 8. 73qqB p 7.42 + 7.42 + 7. 4-2 7.42 I+ 21.85 +21.85 +21.85 +21.85 ;NfFY/Rwi

• t-i</Rmt +0.10 +D.70 -f-0.70 +O. 70 t0.70 +0.70
• DESIGN M.YFt .* 6F.>)ltZ fl. 7q -1. 7'( +I. 7q -1.1q +I. 7'f -/.7q +I. 1q -J.1q ax* PIPE i N1My/R!P*

My/R!.Pt. +0.24-+0.24--0.24--0.24 SLJPPORTMYMy/RmP*6MfRmPt 2--........._ ff-J. 33 -1. 33 -1. 33 t I. 33 LOADS .

.-o. 35 -0.35 +0.35 +0.35 MyM:/Rm/?

• . .,Pf!-4-.

04 +4.04 +4-.04--4.04 TOTAL ox + 5.52 +I0.02 tl4-.30 +2.64 f25.qJ +l'l.67 +-22.17 loESIGN PRESSh3.00l61 p or 2.q6ROI p +32.50 +32.50 32.50 +32.50 +7.42 .f-7.42 + 7. 4-2 + 7. 4-2 1 N'¥Fx/Rm

• FY/Rmt +0.55 +0.55 +0.55 +0.55 t0.55 +0.55 +0.55 +0.55* . . DESIGN M¢i/Fl<
• 2.4-5 -2.4-5 +2.4-5 -2.4-5 +2.45 -2 4-5 +2.4-5 -2.4-5 oe PIPE$

MfR!P.t . +0.13 +0.13 -0.13 -0.13 SUPR?RT MiijM>IRmfl' bM>jRtv1(1f! 2.26 -2.26 -2.26 +2.26 LOADS -1.22 -1.22 + 1.22 t 1.22 Mi/M-;/R .... P

• 6MlfRrnfJt2

-2.61 + 2.61 -2.61 TOTAL 00 . t31.67 +31.'i'I t3q,33 +2'l.21 +12.BI 3_3q +8.03 It 7. 65 or PRESS -P,O 0 -2.5 0 -2.!i 0 -2.5. 0 -2.5 DESIGN PIPE MxJ21rro 2 t +0.24 +0.24. +Q24 +0.24 +Q24 +0.24-+Q24-+0.24 JX9 l SUf.'PORT Fi-/1fro t -0.57 -0.57 +0.57 t0.57 LOJ\DS Fy/1frot -1.06 -1.06 +I.Of> +1.06 , _, ;-TOTAL Txa -o. 33 -0.33 +QBI +0.81 -0.82 -Q82 +1.30 +I. 30 s...,rmn) 09 + W";: + :rz. +31. 68 32.02 +3q.36 *+2q.JB +25.qh +/q, 71 t22.88 +2/."11 . \) = aw +5.52 +q.qa t-14-.ZB +2.66 +12.76 +3.35 +zqz +-7.53 . hl1n 2 lCM2!NED INTENSITY t3/. 68 rt 34-.52 +3q, 3b rl-31.68 +25.q6 +22.21 f+22.88 1+24.4 7

• 5.090 INLET NOZZLE (PART II) A. Abstract *
• T}1.e purpose of this analysis is to investigate the main t.J:* *, lnlet nozzles under maximum hypothetical accident con-di tlons where a safe shut down of the plant is necessary. (See. p, A223 thru A230 of Appendix A for detailed analysis.)

B. Geometry I C. Significant Results *The moximum membrane + bending stress intensity was found to be in the vt--ssel wall adjacent to inlet uozzle #6 of Refer-ence 22,, (Loc":a t.ion BL). The nrnximum stress intensi 1..y (Pm + PB) = 42.l ksi was found to be less than 1.1 $y = 5 ksi for SA-302-B material at design tempera 01* 650°F. It is, the conclusion of this report that the let nozzles will the impooed loads under MHA ditions

• PAL?E J}-17 D. Discussion of Analysis Sir1ce two of 'the inlet nozzles function as supports for the reactor ves3el, it is or particular interest to insure that there will be no gross failure under MHA condl tions. Both the nozzle and vessel wall around the nozzle opening are for pr1mar,y load carrying capabil1 ty. The maxi-* mum combination of membrane +bending stress is limited to 110% of minimum yield strength at design temperature.

It is of part.icular interest to riote that the 11ozzle section experience*s comparatively

• low membrane + bendit1g Dtress while local regions in the vessel wall *around the nozzle opening -the highest sires:S<.->::>. . '*

. ,, I I i .I I I i \.* *,. i 5.110 OUTLI*:T NOZZLE (PAR'r I) fl.. Abstract Thi:J analysis prese11ts the structural evaluatiLn1 of.' the 0ut...; let nozzles for desigt1 conditions. Stresses c1.mside.red are those resulting fI'om inte.r1Jal desig11 pressure and desig11 load3 and support reactj.ons. (See Sheets A269 thru A292 of pendix A for de taJ led analysis. ) B. Geometry Nozzle Cut 3 Cut 2 ---Cut_]. J Vessel I I I C. Significant Re3ults '1 1 he reactor vessel outlet nozzles ari= adt:?quate to wi thsta11d the slmul taneously acting design loads. All str*ess interis1-tles determir1ed in this analyuis are less than the required allowables. I ------------* .

• * * .. i PAG* A-5.110 OUTLET NOZZLE (PART I) C. Significant Results The most cr:1 tical general pr11)1ary membrane stress lntensi in an outlet. r1ozzle occurs at Cut 11 1 11* This stress i11tens:t of 14.17 ksi (see Sh. A289) is less than the Sm allowable of 17.4 ksi. The most critical general plus locaJ. stre.ss 1ntens1 t.y ln t11e 11ozzles occurs at Cut "3" (see Sh. A291). This stress tensity of 13.7 ksi is less t.han*the 1.5 Sm allowable or 26.1 ksi. The most crjt1cal general plus local stress intersity in the vessel wall occurs at lo ca ti on BL (inside) of t nozzle No. 2*with the friction forces acting radially in. This stress intensity of 39.8 ksi (see Sh. A292) is less than the 1.5 Sm allowable of 40 ksi. D. Discussic:'ln of Analysis Thls calculation*dernonst.rates the adequacy of the main a11t nozzles to serve as vessel supports in addition to forming their prlmary function.

The nozzles w:ith support . pad.u support the dead weight 01' the vessf:!l and sustaln t..he due to plpe I'ea<:tior1s a11d earthquake. The support nozzles have flat pads integral with the nozzles ac shown on Sh. A270. The support pads are a1:1sumed to be free to move radially 011 the bearing platesJ but guided to prevent rotation of the vessel

• 2.0

---

I *. -... ,,. . ;_ ., **. : .*-. * . . . **.. .,;... ::_ **. "..!;. ....... :

• .* ":-:,;;;

... .:;::.-:""-** .. --... -* .. *---* I 4 OU I LET N . 2 . *_,u R . cu -. o. I '"' GENERAL + -AL PRIMARY STRESSES lAD [STRESS EQUATIONS Au AL . * -= BL Cu CL

• Dv DL
• DES!GNPRES53.0637'1Por'l.ooJBI P +7.66 .f7.{,{, +7.{,6 +7.{,6 f22.50t22.50+22.50 1 t22.5C l IN:IF>i./Rm
• -I. 38 -1.38 -1.38 -I. 38 -1.38 -L38 -1.38 -1.38-DESIGN IM.¥,::-,y
• 6F>f'tZ -2,q.2 +2.q2 -2.q2 +2.q2 -2.q2 +2.q2 -z.q2 +2.'12 o; PIPE i NyMy/R!P'
• My/R°fnPt +o.53 f0.53 -Q53 -0.53 6MJ/R111Pt 2 +2. J t -2. JI -2. I l' +2.11 LOADS

+o.4q +o.4q -o.4-q {;tv(fRmPe +4. 36 -4.36 -4.36 4-. 36 TOTAL ox +8.21 +5.33 -1.,f.q +13.07 +20.84-+22.4-G +15.56 +25.f>2 DESIGN PRESsll3.2634-4-P or +33.)6 +33. 16 +33.16 +33.16 +7.66 +7.66 t7.66 +7.66 iN*.Vr-x/.Rm

• F>VRm t -o.q5 -0.'(5' -o.q5 -O.Cf5 -o.q5 -o.q5 -o.qs -o.q5 DESIGN M¢/F"
• bf!"x/t.2 .12 +4-.12 -4.12 +4.12 -4.12 t4.l2 -4.12 +4.12 oa PIPE $ Nt/My/R!.P*

M)f'R:;Pt +0.28 fQ 28 -0.28 -aze SUPPORT fVl'VMy/RmP' +3.81 -'g.8 I -3.81 +3.81 LOADS

• M;/R!a P'f'-+I. 62 +I. {;2 -1.62 -1.{;2
• 6 M.iRrnP t2 2.57" -2.57 -2.57 +2.57
• TOTAL 08 t32.28 +35.38 +23.q(J +37.28 +6.60 +7.30 -1.50 +14:36 .ar DE"SIGN PRESS -P,O 0 . -2.5 0 -2.5 0 -2.5 *o -2.5 PIPE +Q03 +Q03 f0.03 +0.03 +0.03 +0.03 +0.03 +0.03 Jxe SUPPORT Fi-/1rro t -0.4-2 -0.4-2 +0.42 +0.42 I LOADS FY71frot -0.73 -0.73 +0.73 +0.73 . TOTAL Txa -o.3q -o.3q +0.4-5 +0.4-5 -0.70 -0.70 +0.76 +0 .. 1b llin(mav.)::

+V,iU-t-"'.4.Jl+

r2. +32.28 +35.38 +23.'IO 4-20.97

+15.'Jq . , i) _ crv -r CTA_\jf-.,, -u,.f +Ji! +5.32 -I. 50 + 13.06 '+6. 65 +7.27 -1.53 +14. 31 . l-1:.!!>:1n -z z. . CCMPINED STRfSS INTENSITY +32.28 l37.8B +25.4-J +3q.1q +20.87 +24._lf q +17.12 +28.17 n o J: > Pl -i. 0 . ,.. z c i::: m Pl :u I * .I . I

• ; . *i DETAILED ANALYSIS ! t SYSTEM GEOMETRY f -* i ' 1 r* . i i ;. f I f. ; I i ! I t f. The fol1owiYiB is of the outlet nozzle: l .

v I 11 2tooo I , ** :24.000 34.28125 25".3125 L .* *. . . I . I 1* I --. I j Rv= If I. 625" I . I . . I ---* r--J I . L--, . I . , 36.2812Su* SYSTEM. LOADING . -. . . In th; s analysis; the. *outlet nozzle . be.* under design load co11ditions. Tne loads are: I. Design P,ressure .. = 2500 Pasi Desigri_ iewiperature =.650 F 2. Desi9n loads avid suppp.rt loads : * . .. Support reactioVl.5 due .. to aead : of R. v. Support reacTions due to control rod" scram . DeaCJ

• weight pi pi;igL_ reactions.

on

• nozzles .. *
• Cold springing reaiTions
• of PiipiY.>q on nozzles Frictional effect of pipinq ar?d -RV. .

COMBUSTiON ENGlNE:ERING, INC. ENGINl!:ERINQ CEPARTM£NT, CHATTANOOOA, TENN* CHARGP.: N0_2q __ NUMDltH e1 c*

• w_a._..:.*
• ... , , ; I :sHcrr 5 ry,._2._ G ..

a..n4-18-67 SNGINEO C!:SCRIPTION ST R!)GIVRAL AtiALVSJS._Q.._F __ OUTLET NOZZLE CHECK M-67 ovHus1!e1W ' PAG £ A -2 3 if" CUGRIPTION_ ANALYSIS SYSTEM LOADING Support growth reacfioris . Pipirig reactions at 1003 power Design seiswiic l'"lozzle and support reacti'otls . . l SYSTEM

• ALLOWABLES I -I I The followiv.g allpwable.

stresses are taken from f/,e ASME

• Nuclear Code J Section J[; ref. 1 ; and are the for _tJ.ii s analysis. . .. ... . .. . ..... . .. . . . . ! .
• l. The primary stress intens11j across a I . solrd section wrust not exceed S,..,., at design I
• temperature and design pressure.

l . . . . . I *2. Joe.al priwiar.Y.. stress alone or I .. . with 1 above noi exceed 1.5 Sm at desigVl tempe raf1Are arid pressure. . ** i I I I! . . * *3. Thet' ding ?tress alone.dor combined . wi n

• I 2 above WJusT excee
• 1.5
  • design
• ey,,perat£Are desigri pres sure. . -** .... . I I; ! * ., I [ I I le I . . .

..... . , ___ _ -, , ""!. DETAI'

• Il'lTF ANAi. The divfc 1, assi: re du} Slqn '

I .. E\em: I Elewle-EJewr Elem. H-, JM, are r fot-t V}OZZ defe;-. analy .5.120 OUTLET NOZZLE (PART II) A. Abstract **

• The purpose of this analysis is to investigate the main a11t outlet nozzles under maximum hypothetical accident con-dl tions a safe ahut down of the plnnt is necensary. (See sheets A293 thru A302 uf J\ppelldlx A for detaJ lNt B. Geometry ..........._

_______ _ I C. Significant Results '1 1 he maximum combined membrane + bendi11g stress intensity was found to be 56. 3 ksi in the vessel shell at the top of the t10ZL':lf.? opening (location AL). Based on lim1 t desig11 theory, t;he ollo 1*mble membrane + bendirig stress intensity was found to be 60 ksl for the critical stress pondition. (See Sheets A 301 t.hru A302) * .I. l the conclusion of th ls report. that the let nozzles will resist the imposed lo.ads under MHA conditions w1 thout rai lure .

• *
• D. Dlscusslon of Analysis Ont: of the outlet nozzles (#*2 of Reference

22) functions as a support for the reactor vessel. It is, therefore, the princ.tple concern of this calcula tior1 to insure that no gross failure of the nozzle or vessel wall will ucc.ur under MHA conditions.

While the nozzle cross-section was found to experience a t1vely low membrane + bend1ng several locationu around the nozzle opening in the vessel sh1!ll were f'ound tu * + bending stress abuVE:.' 1.1 s.v* By ducting an E*valuaUon of Collapse Streugt.h ul' the Sl1tdJ undc:r comb11!ec1 membra11e

md b1:::11ding loads, u::ij11g lillllt slgr1 theory_. the fact that !'aJ.lure w.ill 1 tot 1.'C<..:ur ui;de l' .MHi'\ loads 13 suf"ficle11lly suhsta11tjated

• 1 ! .: .. I I u .. ; . ........ .. ' ..-* *' . ., .......

,,,,, ... ... ....... ,,.._-.. 4--Yes5t:L SHEL.._::.;

.. ***;* *.*. 61::-;,/i:Jc!AL-

• -'4L -r I /JA/LJ :S 'N're,../..51nc-c:.

I . -I SU' .LOAD ST1r.c:n eOt.JAnw I],, A,_ Bo B,_ eu CL [1 DL.. I F'RtSl P t}.(;t)1K1p t-J.7 I-7,7 .;. '/.J + 7.7 22.s-+ 22.J--1-u.s 22.s-! I . "1Fx /f ...

• F.c/f.>M-f

-S'.:;--s.r -s.s--s.S' -S:r -s:r-1 I /11 J.I A ""*Ir-; * (pF-j f -//17 t-//. 7 -11. 7 +//.J -l/17 -t-11. 7 -11. 1 I r 11. 7 I I PIPC i

• M>'/R" f<t IV( f-/.O -r/.0 -1.0 1-J.tJ I LOAD.S /.-i'x/;i1 1/[:.,,Jl
• t,1-iy/p..,,g/z r-$.'I -3.'/ . -!J.1 i l-gl/

J *Mc//:.,' JI-1-J./ .,. J...J -J.,/ -./../ I If* tt. ,,_ ;t. 3 -gt.:5 ;..gt..3 I Tor-1'-J?.< 1-10.C/ -IB. :S -41*1 +44./ +/IJ.2 1-t'.S:Z l

• 4-. +3/t, i .. I

.;-g3,z -1a3.2 .J..8j.2 + gs.2 r 7.7 ! .J-7.J I + 7.7 + 7.71 N.J/F,./1.."M

• Fr. /t:ll-f t--s.g -5.8 _q,g -3.8 -3.8 -3.g -3,g l-8.JI I . M1-/A '* Mtl/F;._ * &F_y_tt.

-It,. 'i'" +-1&.r I - + ,,,-s-I I I -Jt.-:r111t.S IQG Al; y_l/1:,J. ;ti ¢.!/;J t .s-+ .s --* S" -- .. -*--LoAD5 A1r/>/;i1,,;j!.,, M Yhl-t /J/-2 f 7.0 -7.0 -7. 0 /-J.O i I I /,I ;}jJ. t1 I-' 1-1.J.S 1-15.S" -/!J.S' -/B.S' t 1 1-t/. 4--ti. 4--1-21.4-TOrAt... 77J 47. K 1d!I.O 1-tt.O +53.8 -S":J +15.? I -2(). / +f't.1 I I or Pcc.s.s. 0 ,, -P 0 -t.S 0 -2.S" 0 -l.O 0 I -2.> I I I /V/1/A , Ot:, ,Ott, * {)(JJ ,()(, : o' I .tJto I Xo P1Pc -*'fl I -.n .11 ./--*'11 --....1 Fy/1rrat -2. It. I -i /(., .,. 2./(p TOTAL-ne -.7 -.7 + ,, _,_ .9 -!./ l z.2 +2.Z ! 1. a;j fMAl<) =

• 7.1 +-!!.O -21.')

I + . 7 .f ;2.4-! (N1AJ) = .rx

rz --l'.3D.t -JJ.5 -41.,

-5.3 1-13.-s-I -f'(). . .;.J,11;1. /:o..i181.f.f'::°tJ {t..t1/J11) ,147.'J. S"t:..S 41.'I IS". 7 . t/.O ! 34.'/ i -. -... . I I (P,'\+ _____ S0.2 61J.{) fl'/.' 7S".0 7f.S-74./ ! I 75": 0 i . . . . COMBUSTION ENGINEERING, INC. ENGINtERINQ DEPARTMENT. CHATTANOOGA. TENN. c:HARGlr NO f'fM -A P.:SCRIPTION tJoncr tlozZLc ..... Al llA duA<.y:,11> r .. oJ t *S) t * ... _ ... *o&J.:...

.*. ... .. - i i I I I I I I Cur ,_ S/l.£LI.. tlE/V'cJYJl. . . . I ! -f-/t:JC/ll. ( .5T.(nS..iW'TEH.r1114 LDA.D f!.QcJATIC)N A" A.i.. B" B .. cl) C'-D" De. ' ' q.tW11p t-7.7 ./--1.1 f-7.7 I-?./ ri-22. S" I +-211.S ! Mll/J Nt/Fx//.',.,,

• Fx/P..., 1-

- -s:s--s.s -s.s -s.s--S:S" -S:S" i -,;: P/Pt:-16./;41/i::}i. C?S -I-/,{) I-/.0 "" /.0 "" i.o I I LO/JO.$ //,, R,., 2 ,J*1'1Jtj .fJ, .ii---r4./ .J. 4..1 +4.1 1-4./ >< >< ><' I "/?JTAt.. a;: -1.1 -1*'1 -r 1S;.o 1-/J,I) 1-/6 . .!' I De.*.14.u 1..!. i'. I' .,t.a:J.t

.ag.2 +eit ,t-1.1 l-7,7 -I f.7 /-f.? . I .MllA

• ii/!?"' t -:J.3 ._ !J .a -9.1 -S.8 -fi.8 -!J. f -3.8 -3.H --*-**---*--

-: Jg P1Pi; Ah/Mt/l.'f..J* Mt/{!,2-jjl: >< >< >< >< 1L .5"° .s--.s-LOADj

• Mz/!.?J/it T-f!J. s-

-/!J,S--15.S->< ><* 7lJOJl. Io 41.9* *r.l.!/J rtS:? 1-1s.1 *-r.J.4--r4.4-I I I (">,_-...,'"'" l-\c.-lS. -2.s-1 I -2.s-i " -P" o 0 0 0 0 1

• 1"11111 * /VlJ( I ;a irti t ,Pt .. ,f)t, ,{)/,,. ! ,/), ! * --* -. -. ******-**-****-
• ----*-*-----**--*-

--*---... ..... Xs P1P,:;* FL/ITrof -*11 -.71 * "11 .n 1><F><!>< ->< *-t.I' I t-2.14" .,c.J.ll ! F>' I 1Tt'6 t-' >< >< TOTAL. JlJCQ -.7 -*1 +-.'} I-* 'J -J'.l -2./ I t. l. I t. c! ! 1-;; (#1'111.) tr;-t roJ!t .,_ 1-__T._'- ->-I!. 'J +IS/} I .J. //..' +-lt.4-I W (AA1AJJ"' ("IA tTV)/t . . .,. (.. 3. -1.1 -/. ' +4./ ./-"*' I + ,.01 CoA1-e.11Jco

• 14_f!:1B'!_AAle J!.'J. 5,.(, /.? /t.4." /4.e ! 20.t I 15.4-! /8.1 ' PM/ ,'fl"* .KJ .04-.4/ . I ! I So-=-

° I ,42 ! I * /. I (.. r;.+) (Pio\ t-0 ) /.// /. 55 /.'!!:4- /,t,7 I /.64-/.t.1 *.IS: S'esi (P..,+ P&) s-0.2 6().0 'f.l-,s-74./ 1s: 0 I -*-----------*-**--*--------------------*--- 0-,_ g * "'. .,. _':"' _ ... -0 Vf*::JSEL SUPPORTG Tl1.l::; uri;ilysl:J ih1.! :..;iructu!'al a111..i fat.lt!,uE..* tlcJ11 or 1.he l'CH.lct.nr \. '\. LJ re thu:::c:! re .Jul tj rig 1' I'Om 1KH'J11a1 '-'Pt? ra:i t t 1 d:s, * ..

• n i.; l '* *l scr*um,_ c:i.:1rih.1ual<e aw.1 pjpe rupture. (Sv1..' ::3lk*t*ts l\3;H3 tlu*t1 A3G2 <:£ Appe1dlx:

A. B. GeumL* lry i I --------. t: ______ -****- A A C. Slgnif lc:rn t Re::;ul*t.s Stresse::; in the reactor vessel supports meet the appropriate allowables as stated in ASME Boiler and PressuI'e Vessel Code, Sectlor1 IIl and special criteria of references 16 and 18. The maximum combined prtmary stresses (bending + compression) for dE:sigr1 conditions Oi}CUI'S on Sectlori A-A of iule t. support #2. '1 1 hlu stress of 24. 5 ksi is less than the Section III allowable of 1-1/2 Sm = 40 ksi (see sheet A351). The bearine stress beneath the supports was found to be 955 pni during normal opera t1un. 'rhis stress ls conslllered to be :3atisfact.ory when compared to the spC'clal allowi1l>h=! beul'-* ;; trc?S3 01' q50 l>i' reference

16. Pft:::Gf A-ZCJ' ;. .:..

.. ; I ' l \ .ff ii H r :1 1* *j I* . 1: :i !'. :1 i' . ii . 1, h .1: it f* : ** !" 1-;q4 C: A--.30 :n C. !3lgn lfi ca11t.. Result::; (CL'llt 'd) From the standpoint. of .rutlgue, w.ill wi n mlnlmum of 25000 cycles oi' hentup a11d cotild\'"" quj red); 6000 cycles of dt::::>lr;11 selsmlc* <_1*1li aao* occurrences of accldent (1 required)° dht!et. A356). The maximum combined primary stresses .for acc:l.dent t, tun* also occurs 011 Sectlott A-A of inlet ::;upport.

1. 2. This st.rt:>SG of 50 ksi is below the nllc)wable of 60. 7 of referetwe 16 (nee sheet A353)

• The* m;ucimum shear stres:J occurs Oil Sectio11 A-/\ of inlet por*t #2 during accldent condi t:J ons. Ss = 14. 8 ksi which is .wc,-11 below the allqwable stress of 30 ksi (see sheet A353). D.

of Analysis The Consumers 1 vessel has three supports. These oupports are inter:ral with three of the main coolant nozzles, ( 01Je outlet nozzlE* ond 2 inlet nozzles located 120° opart). As referred" to ln this report, support #1 is be11eath an let r1ozzle and supports #2 and #3 are beneath inlet nozzles. / For the case of frictional loads ac.ting between the supports and the matching foundation, a frictjon factor of 0.5 is used with normal operating support reactions. Due to the fact th:i f* the supports are keyed, frictional forces uot con-s.! di:-red to result from seismic, control rod scram and pipe rupture loads. 5.150 VESSEL SHELL AND BOTTOM HEAD (PART I) A. Abstract* 'I 1 his ::malysis presents the structural eval ua t1oi1 of the nnd bottom for the design pressure condi t1on. ( SF:t; .:>hf?e t.s A363 thru A374 or Appendix A for detailed sh;.) .,. ..... *-. -t I ! i . I . ' I j I \ I __ ___ .. A.---- . . r;:a,.J"2 POVJER SYSTEMS COMBUSTION ENGINEERING. INC. ** ,,! . B-1 Page Number .APPENDIX B Sc!SNIC Rc/1/1//Jl YSJS OF Co/1/sllHERS ?oN£R 0-reAJvl GENG",e,1-roR

• PRJH/l/2/

sr,eucruR!F SUPPOR. T LUCS. B-C. B-2 E-3 B-8 B-10 B-13 8-/5

---

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• H 11.
• SYSTEMS ' ..

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SYSTEMS COMBUSTION ENGINEERING. INC

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• J-y = .Z.41'3 ..C/?S _ :. .+/-/1'4 KIP.5 /1,x 8Z 7 /N-K'1r>S

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POWER COMBUSTION ENGINEERING. INC B-4 Page Number PR11-i*,')2r CurLET /VcGzZLr * -F-=-+/-./63 l</PS 'JI/ = /Oc /C/J=>S ::: ,1...V-...e/Ps Vz -=-::t. /7 /Yr-= 9927 FE-01--1 SvKe-ss S;:o,<?7: (P1tc;;£ c-sz3 I c-sz--1) .* (fjs 8-2/ f B-22) Z --%=* 3/8.7 h-2 . ,,e:--/ ,I;" < / -.:,,,.J / ....... , N' i = .75 ,<:s/ 17;' = /.8 ,<:;; . -""7 J( - A -A -:. ,32KS/ :: /-fl -<s/ . /(Y'\Z v,:;,,,..::; + (., "' 2, .s-.KS/ _ ii J 117L"_ / -/.l-.,.. /Ze : 2 KS/ .

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POVJER

• t -SY"T-P.45 i.;..,;;J

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.. *l-SYSTCE&-"S

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• I. ' .. ' ** P/-J-6* G-IS-21 ;< 5.3.2 Prir.1.:iry OutlC't Nozzle Ahf.ltrn.'.t TI1c pt*ir:*,.1ry*

outlet nozzle was [or and effects by cilc Seal-Shell 2 pro:;raq. Pipi:! loads were analyzccl by cla:;si.l!al beam theory and nijlaarc.J analysis. It W<!S that the s true tu re mcc ts a 11 rcquircr.:ents for the spccifi*d loading couclitions

• . Safe End Primary due to normal operating

+ seisrJic = 15. 39 !{SI < Sm = 26. 7 -1{$! Primary membrane dt1e to normal -:. design seismic *'*pipe rupture = 39.6 KSI * * < Sy = 41.4 KSI Primary wembrane due to norm.al + 2 (design seismic) +pipe rupture = 44.9 KSI < 1.1 Sy c 45.5 l<SI *Prinary + Secondary stress intensity range = 59.0 KSI < 3 Sm Q 80.1 KSI Nozzle-Hec!ld Junction Prir.1ary membrane=

?4.1 KSI <Sm"" 26.7 KSI Pri-mary local membrane = 33.3 l{SI < 1.5 Sm = 40.0 KSI Primary + Secondary stress intensity

= 68.35KSI < 3 Sm *.80.l l<SI Fatig;.ic -ac;:Jequa::e by comparison with inle:: Ace idcnt -Primary lo ca 1 rnl!mbranc."' dl:e to ucs i:":n pressure, sa fc seizmic, & p i.i")C i*up curl! -allow.:ihlc: is l.l Sv. " -! .. -..-. ...... ....... >CJpaq:A.P'<I",.,..... .. i\'C)f ... .. ..... . . z;c; ________________ _ ' J I J .. * . l . ! I **: :*'

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.. ll1e nozzle was ana for pressure e ff cc i

s with the Scal*Slacll 2 computer program (R.:-f. lt).

• condition use<l was design pressure (250;) PSI) wich isothcrQal TI1e thermal stresses were ignored in this analysis sir.cc they have no eff cct on. the primary s Si.nee it: coulu be se<.*n from the primary inl(!t no:!zlc.:

Lhet t the* primary + secondary stresses arc \*h.> 11 b'"' allowable wi.th tlwrmal stresses included, it: will be.* ass1.1mcc.I that the holds for the primary 01ttlet: l'ipc load stresses for both outlet 11ozzlcs were cal..:-ula.tcd at the junction by a !H.j laarc.1 analysis. At the sure end, the stresses ior N.:>zzle 'n were calculated usine classical beam theory and Nozzle **;, ' by the plastic hinge method * . Primary membrane stresses were obtained by combining mfdsurface design condition stresses and maximum pipe load stresses. The stresses obtained were fc1und to be than Section III allowables. Local membrane were obtained by combining . mcxi.mum midsurface design conditio11 stresses and maximum load at the nozzle-head junction. The s obtained were found to be less than Section III allowal>les

• Pri.mary and s.econdary stresses were calculated at the safe end and at the nozzle-head junction.

n,e strc>sses were well below the 3 Sm range, so the method of combining peak stresses with maximum pipe load stresses was used. Ft'om the primary inlet nozzle analysis it u.as seen that fatigue will not be a problem in the primary outlet nozzle. 'nlat fatigue analysis took into account the largest stress from either the inlet or outlet nozzles and thus .applies to both.

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• _l 1 .. :-cimum n III ::ie sses pipe :utlet .les i i *-29 P/-JGG"' 8-17 n1c decay of nozzle stresses in the head was found by. ploL:tini; strc.:ss (from vs. dlsL.:mc1:

for f>!"L'G:>urc, and by using BijlanrJ <l.:i::a fol.* the pi.pi..' loads. The :;cc t *Lon III al lowc'.lb les are used e.;<t:upt for: 1) No::mnl operating + design Sf..'isrnic + pipe ru*.a.urc loads -allm;able is yield

2) Nor111c'.ll operating

+ 2 (Design seis1;1ic!) + p*I.pc* loads -allowable is 1.1 ( 1 1 , I *', I . . ' COMBUSTION ENGINEERING, INC. DEPARTMICNT. CHATTANOO<IA. r'.NN

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...... ... .. . : . . . Pr!G* 8-29 --1 I 24 ! \...,5.3.l Prim.:iry Inlet No?.zlc nH:! pr imnry inlet 110Z7. lc WC\S llna lyzcd for and thcr111a 1 e ffccts by the Sea 1-She 11 2 cor.ipu ter Pipe loads \J<<:>re analyzed by cl.:issical bca.r.1 theory and Bij lc1ard an.:i lys is. It was found that the s true tu re mce ts a 11 rcquir0mcnts for the specified loadinB conditions. Sie!1ificant ncsults Safe End Primary membrane due to normal operating + design seismic= 16.l KSI <Sm= 26.7 KSI Primary membrane due to normal operating + design +pipe rupture = 20.7 KS!< Sy = 41.4 KSI Primary membrane clue to normal operating + 2 (design seismic) + pipe rupture = 25.3 KSI < 1.1 Sy = 45.5 KSI Primary + Secondary stress intensity range = 52*. 2 KSI < 3 Sm -80 .1 KSI "Nozzle-Head Junction Primary 24.9 KS! < 26.7 KSI Primary local membrane = 35.0 KSI 1.5 Sm -= 40 KSI Primary + Secondary stress intensity range a . 6 8

• 9
• KS I ( 3 Sm 80 KS I Fatigue -(PL + Pb + + F) a .283 ,1.0 allowable Accident -Primary local membrane due to design pressure, safe shut-down seismic and pipe rupture -allowable is 1.1 Sy. Smax
• 44.4 KSI <: 1.1 Sy 45. 5 KSI '*

er 1 mnc.I the -2 < . I . -.. ;n

• U.i.sctt!:is ion '.L"hc otJ* ..

wa:; analyzed for the.rmal and pressure cffc<.:C:!:i the Seal-Shell 2 Cot:1putcr Pt*o.:;r.:im 111e followinz used: 1. I::n*J of from 7u°F to 532°.r*, P = 21.JJ P::iI 2. I.::nd of coo 1-down from 532°F co 70°F, P = J PSI '* condition -isotherrital, P = 2500 PSI were at the safe-end by cJ.assical bear.1 theory and at the nozzle-head junction by a Bijlnard analysis. Pri111ary stresses were obtained by combining mi<lsllr face design condition stresses and maximu111 pipe load stre:*sscs. The stresses obtained were found to ue than Section III allowables. The local membrane stresses were obtained by cor.1bining .maximum midsurface design condition stresses and pipe load at the junccion. The stresses obtained -were found to be less than Section III allowables. l1rii'.lary and secondary stresses calculated at the safc-e:nd and at the nozzle-head junction. es obtained -were well below the 3 Sm range, so the conservative method of combining peak pressure es with maximum pipe load stresses was used

• The fatigue ar1alysis was to justify the primary outlet nozzles as well as the inlet nozzles. forc, maxi.mum peak s ti*ess conditions from either *were u.:;cd. n1ermal skin stresses were calculated for reactor trip, 10'7. step, loss of flow, and dead weight conditions and added to the *above mentioned peak stresses.

The usage factor obtained is small cind assures that both the Primary I11iet an<l Outlet: nozzles satisfy the fatigue requirements. l'he decay of nozzle stresses in the head was found by stre::;s (from Seal-Shell) vs. distance for prNH>u1*c.:, and by li$ing Bij l.:iard <lata for Lht? pip"' loac.Js. #

• The ::.iuctL:m III allowa'bl<.?s are 1.1seci for:* l) operating seismic + pipe rupture toads -all1)\*'ablci i.s :,*1.clu 2) scrcss. Hor1aal opurat:int;

  • 2 set$i.1ic)

+

• pip.: rupture loads -allo\,*nhlc i:> l.l
• ,. . J._

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• j :. COMBUSTION ENGINEERING, INC. NUM1n:,...__

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• j ! I l } I I i I . J . ' .1 I I .; , . i 'I '*t
• I ... G.3.10 _ . ) C,J.10.{, _/'-/.:->::::!._

3 ?'rr S -r C.-4s-': 1 p,,,: 3.S.3 'I-

-( s" :.

k... ---//, 0;? ,P0 ::-;;. 9 z "' '), ..>-..1 :- 5 s :-.f)6 :z ,t1' P,,.. .: [?ft S3 r-1 _______ .;.__,fc.. ,,.-; c:::> .'=:: . fl :I Y. 7 ; * .i. :2 I. ! 2 = .22,08 :: I 10. !..---70 ;>... 28. 99,: N, ;; ) :

• P,; )qJ.{i'-'

= f (;a. 9G){.sp'l')o)

J 12 * ..'2. / ---*

• • .---

.. -*' Wdtol ------f',., =-3. s 3 _,,..---......----------' 0----f(...-- '°'1 :-s.:> = 9.2 r /.S-. '18 = 2..S-.. "lo -?b -I 13 .1)(0 : /&/. $'1-: ... .: ...... - 44 * -; KSI 1 * .3 KSI , .. mize flow e t 119l* I :-e ! The ':eS eam *=imes ector. a :ial I I I . -:-imary ; . ne). , I ! -45 PAG£ B-4'3 5.5.3 Support Lugs . 4 -'llle upper support lugs were analyzed for the specified loading by using classical machine design P.q\!ations and a Bijlaard analysis (Ref.20). 'l'hc str<?sses satisfy the requirements of III*. Results (all material is SA-302-B or equi.v.) The larcest stresses in the lugs are .: .. '. T =-10 KS I <

• 6 Sm
• 16
• 02 KS I (shl*ar tear out at: all *pin joints) = 25 KSI < 1.5 Sm* 40.l KSI Bettring stress on double shock lug .. All other stresses in the lugs are than 607. of their *al lowables Pm+ Pb = 39.5 < 1.5 Sm* 40.l Key Lug, outside surface of shell . ' *. . .* . ... ... , .. ; .. : . ; . ... '* -. . *;it-.*-' >"" ::. . . .; . I .. :; .. CJ---2] !e-1 FIG
• 17 .....

ti. A. Stone, Che . lluelear Co;;i,pooen":. Dept. 8UIUlCT COUSUM.ER-' S FO>.fER STEAM Gfl:::RA'I'Ot1S . COUTrlACT 2%5 **-** -* .* v. JC.

• ---h tt. ** . J\,me 2, . *cc: P. P. Bill, Ca onc:ioga . (EV ; . . .._-J. D. Cravtord p -* : * -'-* .. *. * . P..S_ E-34 ; ... 4*..r
• . . * ** * .At a uetine

?t!!y 18, 1966 to d1seuss the steam senerators CEUD 1 **** -*

• ae;rced to turn1sh support loads. These loads are rorvarded here.in. The enclosed
• akctchs sbov _the: c;encral location or the various PJ1ota. . . . . . **.Vertical support 1s provided by Z. "Lubrite" bearing FJd.s over vbic:h the stee:i . v.ill slide vhen r.31n coolant pipe l".eats. up. A. key 1a FOvidcd under base to * . 1'orce the cencrator to slide 1.n a st:-aight l.1i:e: A stop 1s :provided at the er..re?:e* .
• end ot t.ra'\"cl during heat up t.o prevent p.ny turther i:otion it' a I!:31n coolant :pi;co. :-Upturcs.

]?old c!o\ra finee:s *&re also j?rpVided to limit up°*"'al"d

OWI:.ent Ot' the generator to this

• .* . . .. * * * . . , . . . Svay1%18 or the due to se1sl:ic loading, eccident*cood1tions or v1brat1cn is ::.

..... : l.ilidted by a system or *keys and shock absorbers on t'h.e cylilldrical part tl:e eenerator.

• keys si.-ayfog in tbe d1rect.icn cul.ar (. : * ) to the JLC. l:ot leg vhile ".st.eek absorbers" lll:it. tl:.e 51."a)Pllg in direction parallel (X) to t.be bot. leg. or these devices allov the &ene:-ator to J:OVe
• slc-.rly in tbe . :.._ .41rect1on ot tbenr.al g:rovth Vith virt.uall;r z:o rest.raint. . .*: * * -Sketch l sbovs tu OVel".all.

vhile i 3 sbov in zcare C!etall *-tl:= at tb: uz:er qlinder s:r:d . ... . . . . . -. . . . . . . . .. . . . . . . * . . . A ot tl:e load*b:g b gben 'belc"J. m-e w :.* *( ':". *:

• CCC'Jr St t1-..e SB::e ti::l!. T"""O Sets ot VSl\:.?S ere givai i.e. lia1.s::1c loedil:.i . -* ** *. * =4 'tlllder the ac:.c:1cent condition ot a :::ain ccol.D.nt p!i:a
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• ..

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" ** ** * ---------ATIACHMENT 3 Reactor Internals Seismic Review As noted in the Reference, an update of' the original seismic analysis of the Reactor Vessel Internals has been perfonned using the same methodology utilized in the original analysis. This methodology-consisted of load development by the. equivalent -static method using a lumped mass and beam model. The input acceleration used is the acceleration of the reactor supports based on a peak horizontal ground acceleration of .2 g per the NUREG input noted in the ence. Vertical and horizontal accelerations were applied simultaneously. The design criteria used were those specified in Table 4-3 of the NUREG input noted in the Reference for the load combination of dead loads plus SSE load. All stresses were found to be less than the specified allowable values. The following su11111ary lists the stress margins calculated for the components of the reactor internals in the analysis reported in the Reference.

• . The margin is defined as: (l _ Calculated Stress ) X lOO% . Allowable Stress The listed stress margins.are the minimum margins occuring in the reactor internals.

Components not listed have a margin equal to or greater than those reported for their component assembly

• COMPONENT LOCATION MARGIN % CSB (Core Support Barrel ) Upper Cylinder 95 CSB Guide Pin 72 CSB Snubber 67 LSS (Lower Support Structure)

Beams 83 LSS Core Support Plate 92 Peripheral Bolts LSS Column Bolts 81 LSS*. Columns 86 UGS(Upper Guide Structure) Flange 74 UGS Control Rod Shroud 96 UGS Lug Bolts* 88 . UGS Grid Beam 91}}