ML20038C270
| ML20038C270 | |
| Person / Time | |
|---|---|
| Site: | Prairie Island  |
| Issue date: | 12/02/1981 |
| From: | Ballum J, Adam Wilson, Wrona T FLUOR POWER SERVICE, INC. (SUBS. OF FLUOR CORP.) |
| To: | |
| Shared Package | |
| ML20038C269 | List: |
| References | |
| NUDOCS 8112100343 | |
| Download: ML20038C270 (64) | |
Text
{{#Wiki_filter:__ __-. _ ( Attschm:nt I Director of NRR December 2, 1981 . tr CONTAINMENT l ISOLATION / PURGE VALVE ANALYSIS FOR 18" 2FII BUTTERFLY VALVE WITH 744A-lSR BETTIS-OPERATOR AND 746A-2SR BETTIS-OPERATOR Project Site Prairie Island Nuclear Power Plant Customer Northern States Power Company Engineer Fluor Power Services, Inc. Original Specification TS-M-635A Original Purchase Order HIA-195 Change #2 & HIA-1195 Change #2 Original Pratt Job No. N-6903-l&2, N-6904-l&2 i Valve Tag Nos. CV-31310 thru 31317 l CV-31621 CV-31627 CV-31622 CV-31628 General Arrangement Drawing E-1683 Rev. 4 Prepared by: M )- y h p etsssnurn Date: /l7 - / - f/ , .'..$.0, ,,, Reviewed by: [hde; '
, f f REGIS E ED E i PROFESSIONAL i E Date: /s - / - 8/ 5 1 ENGINEER I E Certified by:
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i CONTENTS - Page I. Introduction 1 II. Considerations 2 III. Method of Analysis 4 A. Torque Calculation 6 B. Valve Stress Analysis 8 C. Operator Evaluation 9 IV. Conclusion , 10 Attachments (1) Input Documents (A) Pressure vs. Time Graph (B) Pratt letter regarding additional-information . (C) Customer / engineer response to - request for information (2) Valve Assembly Stress Report (3) General Arrangement Drawing
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I. -Introduction I This investigation has been made in response to a request by the customer / engineer for evaluation of containment isolation / purge
- valves during a faulted condition arising from a loss of coolant
; accident (LOCA).
The analysis of the structural and operational adequacy of the i valve assembly under such conditions is based. principally upon l I
< containment pressure vs. time data, system response (delay) time, piping geometry upstream of the valve, back pressure due to ventilation l components downstream of the valve, valve orientation and direction of valve closure.
1 The above data as furnished by the customer / engineer forms the basis for the analysis. Worst case conditions have been applied in the absence of definitive input. O g h r i I
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[m (~ II. Considerations The NRC guidelines for demonstration of operability of purge and vent valves, dated 9/27/79, have been incorporated in this evaluation as follows: A.l. Valve closure time during a LOCA will be less than or equal to the no-flow time demonstrated during shop tests, since fluid dynamic effects tend to close a butterfly valve. Valve closure rate vs. time is based on a sinusoidal function.
- 2. Flow direction through valve contributing to highest torque; namely, flow toward the hub side of disc if asymmetric, is used in this analysis. Pressure on upstream side of. valve as furnished by customer / engineer is utilized in calculations.
Downstream pressure vs. LOCA time is assumed to be worst case. I
- 3. Worst case is determined as a single valve closure of the inside containment valve, with the outside containment valve '
fixed at the fully open position. *
- 4. Containment back pressure will have no effect on cylinder operation since the same back pressure will also be present at the inlet side of the cylinder and differential pressure _
i will be the same during operation.
- 5. Purge valves supplied by Henry Pratt Company do not normally include accumulators. Accumulators, when used, are for i opening the valve rather than closing.
- 6. Torque limiting devices apply only to electric motor operators which were not furnished with purge valves evaluated in this
- D report.
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) 7&8. Drawings or written description of valve orientation with N.] respect to piping immediately upstream, as well as direction of valve closure, are furnished by customer / engineer. In lieu of input, worst case conditions have been applied to the analysis; namely, 900 elbow (upstream) oriented 900 out-of-plane with respect to valve shaft, and leading edge of disc closing toward outer wall of elbow. Effects of downstream piping on system back pressure have been covered in parag'raph A.2. (above).
B. This analysis consists of a static analysis of the valve components indicating if the stress levels under combined seismic and LOCA l 1 conditions are less than 90% of yield strength of the materials used. 1 A valve operator evaluation is presented based on the operators , N- ability to resist the reaction of LOCA-induced fluid dynamic torques. . C. Sealing integrity can be evaluated as follows: Decontamination chemicals have very little effect on EPT and stainless steel seats. Molded EPT seats are generically known to have a cumulative radiation resistance of 1 x 108 reds at a maximum incidence temperature of 350 F. C It is recommended that seats be visually inspected every 18 months and be replaced periodically as required. Valves at outside ambient temperatures below 0 F, if not properly adjusted, may have leakage due to thermal contraction of the elastomer, however, during a LOCA, the valve internal temperature would be expected to be higher than ambient which tends to increase sealing capability after valve closure. The presence of debris or damage to the seats would obviously impair sealing. ... \ m)
s III. Method'of Analysis
\ms/ Determination of the structural and operational adequacy of the valve assembly is based on the calculation of LOCA-induced torque, valve stress analysis and operator evaluation.
A. Torque calculation The torque of any open butterfly valve is the summation of i fluid dynamic torque and bearing friction torque at any given disc angle. , Bearing friction torque is calculated from the following equation: TB=PxAxUxd7 . where P = pressure differential, psia A = projected disc area normal to flow,'in U = bearing coefficient of friction . d = shaft diameter, in. Fluid dynamic torque is calculated from the following equations: For subsonic flow P R CR b P l> 1.07 (approx.)
~
2 3 l T =D xC Tl xP x K xF RE D 2 l 1.4 For sonic flow 11 CR _2 _ T =D xF D xCT2
- 2* f,4 RE (F RE x
Where T = fluid dynamic torque, in-lbs. D
3 F = Reynold number factor a R = critical pressure ratio, (f (d) ) CR Py = upstream static pressure at flow condition, psia P = d wnstream static pressure at flow condition, psia 2 D = disc diameter, in. 4 CTl = subsonic torque coefficient CT2 = sonic torque coefficient K = isentropic gas exponent ( d 1. 2 'for air / steam mix) d = disc angle, such that 90 = fully open; O = fully closed are a function of disc angle, an
- Note that CTl "Ud T2 exponential function of pressure ratio, and are adjusted to a 5" test model using a function of Reynolds number.
Torque coefficients and exponential factors are derived from
- analysis of experimental test data and correlated with analytically predicted behavior of airfoils in compressible media.
Empirical and analytical findings confirm that subconic and sonic flow conditions across the valve disc have an unequal and opposite effect on dynamic torque. Specifically, increases in up-stream pressure in the subsonic range result in higher torque values, , j while increasing P y in the sonic range results in lower torques. 4 l Therefore, the point of greatest concern is the condition of initial sonic flow, which occurs at a critical pressure ratio. The effect of valve closure during the transition from subsonic to sonic flow is to greatly amplify the resulting torques. In fact, the maximum dynamic torque occurs when initial sonic flow occurs coincident with a disc angle of 72 (symmetric) or 68 (asymmetric) l from the fully closed position.
.d t l . i _ The following computer output summarizes calculation data and torque results for valve opening angles of 90 to 0 . 4
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D-29253-2 TOROUE TAFLE 3 8 r 31 / 81 i JDB:HDRTH.STiFPAIP.ICL P2-VARI ALLE OIZE ADJU5TED GEYNLLS 110.FNCTti!> 1 SAT. STEAM /AIF t1IXTUPE WITH 1.4 LES STEAM PEP 1-LLO RIP !
!PEC.GR.= .73?255 "MDL.WT.= 21.3872 LAPA(ISEttT.EXP.)= 1.19775 R= 72.1972 I GAS Cutt TAtiT-CALC. .
l SONIC 5 PEED (NOVIriG M1XTP.)= 1353.63 FEET /SEC AT 264 DEG. e CRIT.C ASE IHLET VELDCITY IO 1.42357 tit 1ES HIGHER AS AIR CRIT. CASE IriLET V1-CF 5 ItiCH MODEL
- I 11AX. TOROUE IS AT THE' CRITICAL PFECC.RATID(.5?5-(5 IIDMDDEL DR APPX .655842 l
.< 17.25 IID u!TH OTMIF.)FIPST 3DilIC(? 72 DEG.V. A.) i ABCDL. MAX. TOROUE (F I PS T SDri1C)AT 72-68 DG.VLV.RMG.= 18259 Irl-LLO @ 72 DEG.
t1AMa'DFOUE IffCLULES OIZE EFFECT tEEYhDLDS tid.ETC) AFPX. X 1.16257 FOR 17.25 IdCH EASIC LItiE I.D.
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I ALL PPESEUFES USED: STATIC (TAF)PPEOS.- ADSOLUTE!P2 IriCL.PECOVEPY FPESO. (TDROUE) CALC'S VALIDITY:P1/P2> 1. 07;
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VALVE. TYPE: 18"-2FIIi2.25/4.75 CLASS 150 i DISC SIZE: 17.37 ItiCHES SYMt1ETRICAL DISC i 5 HAFT DIA.: 2.25 IriCHES
. . LEAP.ING TYPE: ERufi2E q SEATIffG FACTOP: 25 ,
.i t INLET SPESS. VAR.MnX.: 50.2 PSIA .
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- DUTLET PP6;s00FE(P6):
119Xt Arib.FLDtJ PATE: 26.85 72023.2 PSIA (72 LEG. ACTUAL PPESS.DifLY(VAR.)) CFlii 117867. SCFMi 6479.49 LE MIti 6
. . CRIT.5DNIC FLOW-90DG: 6942.42 LU/IIIri AT 30.0498 IriLET PCIA
> YALVE IMLET LENSITY: 8.99640E-02 LE/FT^3-M1H. .134812 LE/FT^3-MAX.
" * ' FULL DPEh DELTA P: 9.79071 PSI i l
G , cYSTEM CGtfDITIDMS: FIFE Iff-PIPE-DUT -Arid- AIP/ STEAM t1TXTUFE SEPVICE & -264 DEG.F [#1114IMUf1
- i 0.75 DIAll. PIPE LDWHSTPEAri FFDM CEffT.LIffE SHAFT.
P1 FB?.' PPES$UPE(ADJ.)FDLLDhC TIf1E/PPESO.TF Ari?IEriT CURVE. ;
,,ABSDLUTC r*AX.TDPCUE IS DEPErfLEtiT Off DELAY TIf1E Arid 3.43 TO 2.15-TH PDMEP j
9 DF (P1xo2)IH L'ORST RANGE X LINEAR CuttSTAttT X DYH5TR.PPE55. P6-ASS.(75-60DEG.) Ili SUBSONIC PAfiGE LIMITS-DNLYi!EE FORMULATIDriS.-FER TESTI F.PPATT .: THIS TO.' AT 72 DEG.OYt111. DISC (68=DFF5ET CHAFT)CT=T/D*3 P2(ABS) !* ( .
--S Iri.t1DDEL EQUIV. VALUES------ACTUAL SIZE VALUES----- i AriGLE ,P1 P2 DELP PRESS. FLOW FLOW TD TE+TH T It1E (LOC A) .
; APPPX. PSIA PSIA PSI PATID (SC Ft1) (LB/t1I tD ----INCHLB5---- TD-TB-TH CEC. -!
f3 33.5 23.71 9.79 0.708 117867 6479 0 1058 -1058 2.25 i
< 85 36.1 24.97 11.16 0.691 126251 6940 4937 1095 5842 2.47 i Sd 38.2 25.49 12.70 0.667 12835? 7056 7285 1228 6056 2.68 ;
a 75 40.0 25.16 14.82 0.629 127959 7035 11933 1502 10430 2.35 j
. e r 72 40.9 23.97 16.97 0.585 121436 6675 18302 1877 16425 2.95 ;
. 70,41.5 23.56 17.97 0.567 115910 6371 17814 1848 15965 ?. 05 {
- j. 65'42.8 21.71 21.11 0.507 104?42 5763 10274 1531 11692 3.21 l
/' 60 43.9 19.98 23.87 0.456 90047 4950 13462 1592 11869 3.32 .g 11990 1779- 10211 3. 12 55 44.6 10.30 26.29 0.410 75555 4170 50 45.0 1#.22 27.83 0.382 62025 5409 8669 1952 6717 3.42 l
'c _ 45el5.2,(16<42 20.78- 0.363 61256 3367 7641 2099 5541 3.50 !
I 40 45.3' 15.90 29.39' O.351 42190 2319 5408 2238 3170 3.52 l
, 35 45.6 15.37 3g720 0.337 32155 1767 3879 2374 1504 ?.58 ;
15s06 39.96 f 0.327 25931 1315 1985 2506 -520 3.67 : 30 f546'6 4650 ~ 14.38 31.T2 0.319 16764 921 1181 2676 -1494 ?.79 I
,Juo 47.3 14.78 ?2.52 0.313 10769 592 798 2913 -2115 3.45 l s , 45 48.1 14.72 33.36 0.306 6115 336 ,051 3183 -23 31 4.12 ;
I *10 48.9 14.71 34.16 0.301 2923 160 296 320E -299? 4.2c l l
. 3 5 g/S . 6 14.70 34.o? 0.296 941 51 192 3373 -3181 4.52 i a otre 11 ro :5.50 0. ,- e O fj 106,05 3165 7439 4. N -
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/ j B. Valve Stress Analysis
(' / The Pratt butterfly valve furnished was specifically designed for the requirements of the original order which did not include specific LOCA conditions. The valve stress analysis consists of two major sections: 1) the body analysis, and ,x
)) all other components.
The body is analyzed per rules and equations given in paragraph NB 3545 of Section III of the ASME Boiler and' Pressure Vessel Code.
.The other components are analyzed per a basic strength of materials type of approach. For each component of interest, tensile and shear stress levels are calculated. They are then combined using the formula:
Smax =2 1(T 1 +T2 ) +1 (T1 +T2 ) + 4(S l+S2)
,/- ' s a 2
1
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where S max = maximum combined stress, psi Ty = direct tensile stress, psi T2 = tensile stress due to bending, psi Si = direct shear stress, psi S2 = shcar stress due to torsion, psi The cal.culated maximum valve torque resulting from LOCA conditions is used in the seismic stre'ss analysis, attachment #2, along with "G" loads per design specification. The calculated stress values are compared to code allowables if possible, or LOCA allowables of 90% of the yield strength of the material used. -/ 's b
C. , Operator Analysis . I Model: Bettis 744A-lSR Rating: 152,400 in-lbs at full open and closed positions only 101,600 in-lbs at intermediate positions Model: Bettis 746A-2SR Rating: 143,200 in-lbs at full open and closed positions only 94,500 in-lbs at intermediate positions
. Max. valve torque: 18,302 in-lbs The maximum torque generated during a LOCA induces reactive forces in the load carrying components of the actuator.
, Since the LOCA induced torque derived in this analysis is less than the maximum absorbtion rating of the operator, it is concluded that the Bettis models furnished are structurally suitable to withstand combined LOCA and seismic loads. i N
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i IV. Conclusion - . f It is concluded that the valve structure and the valve actuator are both capable of withstanding combined seismic and LOCA-induced loads based on the calculated torques developed in this analysis. I i 4 A 'I i i
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t e ATTACHMENT 1B 1 PRATT LETTER REGARDING ADDITIONAL INFORMATION O e l l 4 l i
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1 lPRATT, 1-4
. HENRY PR\TT COAL R-\NY
( *l't 'i 11 i \ e ' t *I lif i t it 't
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-(t)! MutTil IIIGlifANI).Wi:Nt*l: . Witt H t.\. llJJN sts s;t ru,7 December 3, 1980
' Northern States Power Co.
R.R. #2 . Welch, MN 55089
- Attention: Mr. A.D. Smith Project Engineer
Subject:
Prairie Island Nuclear Generating Plant 36" and 18" Purge Valve Analysis MQ-05174
Dear Mr. Smith:
Recent findings in the general analysis of purge valves sub-jected to LOCA conditions have necessitated a request for d additional technical data from the customer / engineer. Delay time, system back pressure and valve orientation have a significant impact upon maximum torque and resultant stresses in the valve assembly. To properly ccmplete the purge valve analysis referenced above, the following information is re-quired:
~
- 1. .The combined resistance coefficient for all ventilation system components downstream of the valve (one for each f
valve size) or_ A graph of back pressure vs. LOCA time at a distance 10-12 diameters downstream of the valve. Consider also the capacity vf the piping, filter and duct work to resist increases in back pressure.
- 2. Maximum and minimum delay times from LOCA to initiation of valve rotation.
..g O !".Rt"!!
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! PRATE 1-5 p
Mr. Smith Page 2
\- December 3, 1980 ..
- 3. Drawings or written description of valve orientation with .
respect to elbow immediately upstream of valve (within 6 diameters), as well as direction of valve closure (clock-wise or counterclockwise) as viewed from operator end. In the absence of the above 'information, the following assump-tions will apply to the purge valve analysis: ,
- 1. Back pressure of 19.7 psia throughout valve closing cycle.
Higher back pressure increases maximum dynamic torque and valve stresses.
- 2. Delay time from LOCA to initiation of valve rotation shall be chosen to permit initial sonic flow condition and critical valve disc angle to coincide, resulting in maximum possible dynamic torque. .
- 3. 90 elbow immediately upstream, oriented 90 out-of-plane
(} with respect to valve shaf t, with leading edge of disc ( j closing away from outside radius of elbow. Such orien-tation and closure will increase torque values by 20% or more. Your prompt response within 30 days would be appreciated. Very truly yours, HENRY PRATT COMPANY ~ 4- .60kxx- - T.J. W rona, Manager Contract and Proposal Engineering l l
/sw CC: R.D. Nelson O
s_ , - l . I
... .. ... Am r.t e d l
--- . . _ . _ __ _ . . _ - - _ .__ . - .._. - -.- - = _ _ . - - - _ . . _ - - - . _ _ . _ _ _ _ . . - - . ..
. v 1
- 16 i
i 2 i t i . ! r i l i - i i l, t i t
- t J ,
i t
! i i l l
,' ATTACilMENT 1C L i I i CUSTOMER / ENGINEER RESPOUSE l TO REQUEST FOR INFORMATION f e i l i ii
. r e
e g 4
- k.
1-7 NORTHERN STATES POWER COMPANY D PRAIRIE ISLAND NUCLEAll GENERATING PLANT RR #2 Welch, MN 55089 December 26, 1980 Henry Pratt Company 401 South Highway Ave. Aurora, ILL 60507 Attention: Mr. T.J. Wrona
Subject:
Your letter of December 3, 1980 requesting additional technical data for Purge Valve Analysis MQ-05174.
Dear Mr. Wrona:
- 1. Neit$er the combined resistance coefficient nor a graph of back pressure vs LOCA time at a distance 10-12 diameters downstream of the valve is available. Also, we do not consider a back pressure of 19.7 PSIA a conservative assumption.
- 2. Since delay times from LOCA to initiation of valve rotation is an un-known we accept your sonic flow condition assumption.
{
\ 3. Table 1 attached is a summary of valve orientation.
If we can be of further assistance, please call. Very truly yours, F.P. Tierney, Jr. Plant Manager By
'Gdry 411er FPT/GM/jac Attachments cc: subj. file - ventilation
]
d
-- ~ -_ . . . . . _ -
V 1-8 TABLE 1 Butterfly VLV Closure Upstream Valve . Tag No. Direction Elbow Orientation l t CV-31310 Clockwise Note 2 ; i CV-31311 Clockwise Note 1 CV-31312 ,
. Note 2 l CV-31313 Note 1 l CV-31314 Note 2 CV-31315 ,
Note 1 7
. CV-31316 Note 2 CV-31317 Note 1
'#-31569 Note 2 ,
+ .I CV-31570 Note 3 ! CV-31574 Note 2 l CV-31575 Note 3 ! CV-31633 Note 2 CV-31634 Note 1 CV-31635 Note 2 CV-31636 Note 1 Notes .
- 1. Inlet of butterfly valve opens directly into containment with no ductwork including elbows upstream of valve.
- ~ ~
!. There are two Pratt Butterfly valves in series separated by a 21-30 inch straight length of pipe. This is the second valve.
- 3. There is a tee directly upstream of this valve. See Sketch I for valve
! Orientation with respect to the tee. W w r* s ,19 e m m e wmve -- -* W-e t -n---t--+-m-n4-=h-w+w-' ear w'M .w -NM - s *CPN-W r e +* V f w w*trr e' P", rey,= m,, w w,% ,,w.w,ymm.% ,ma q- g www .-, y www ,,, , .,y m , m w ,., -y-g+
1-9
~
O FIGURE 1 BUTTERFLY VALVE , j, TEE I/fj/ / ' o
'y ;
z >.+ e ( DIRECTION OF CLOSURE i O
l-, , 1-10 l I FLUOR POWER SERVICES,1NC. 200 WEST MCf4 ROE STREET '
\ CHICAGO. illNOIS 60606
( TELEPHONC (312) 368-3500 April 29,1981 Mr. T. J. Wrona, ManagerV Contract and Proposal Engineering FX - 110 Henry Pratt Company 401 S. Highland Avenue File: 000 268.1 Aurora, Illinois 60507 1.2 Ref: None
Subject:
Prairie Island Nuclear Generating Plant 217450-268 . 36" and 18" Purge Valve Analysis
Dear Mr. Wrona:
The enclosed table contains the calculated post LOCA pressures at several points in the containment purge supply and exhaust ducts. Please call me if you have any questions. V uly your , 0, . . a) . D. F. Wheeler Principal Mechanical Engineer DFW/dm encls. cc: Mr. A. D. Smith, Northern States Power Company l l l l
,g-e---,,,y.. . , . - _ _ , , . , - -.,,.-..m.e.~,.---,-.,,._
. , - ,._ - -.-- ,..-,,.-mr,--, ._,,--.,4 , . - - . . -
. .m,_,, ,,w-- - . - .-,
I j 1-11 i SUPPLY SYSTEMS 4 UNIT 1 UNIT 2 PRESSURE, PSIG PRESSURE, PSIG ; LOCATION 3 SECONDS PEAK 3 SECONDS PEAK , Containment 27.8 42.6 27.8 42.6 Damper 25.4 38.6 25.2 38.3 i l 10-12 Diameters
- 22.3 33.4 21.5 32.5 !
Supply Fan 17.5 25.8 , 19.8 29.4 ! EXHAUST SYSTEMS I Uni t 1 Unit 2 PRESSURE, PSIG PRESSURE, PSIG OLOCATION 3 SECONDS PEAK 3 SECONDS PEAK 27.8 42.6 Containment 27.8 42.6 Damper 21.2 31.5 21.2 31.5 10-12 Diameters
- 18.0 26.1 18.6 27.2 Stack Inlet 2.1 3.0 2.2 2.8 l
l l l l l ,
- 10-12 Diameters downstream of isolation, valves.
l l. l l I _._ ___ _ ____ _ _ ..._ , ---_ _ __ _ ___ __ __ . _ _ . _ _ . , _ _ _ _ _ . _ , _ _ . - . _ . _ _ _ . - - . _ _ _ _ _ _
r . - - o Of
. 2-1 h
Yk . . O9 ,,
- ATTACFVENT 2 l
#k Nuclear
<> = i i _
Purge Valve Ir Ik Stress , O" Anaaysis . . ik Ab d 4 o o kk o Ik
<k h
kk
$f s
e -r,- w ,-r---tww ww- m+ge -*=u .--w-evrw --w-----v-- ,---w-. .%,-,w-,.--, --w-- m----- - ------ ---- - - - * -,---w--- --- w.--- --
- - ~ ,
l . . 2-2 . i i
. s i
. .FORElf 0RD -
. . . c. . .
~
' ' - ~ ~ ~ ~ ~ This report presents applicahic des.ign criteria and a'nalysis
- method for 2FII' and MKII line of. b'b'tterfly valves. The basic
' - ' difficulty in the development of the applicabic criteria is the ,'
compact shape of the' valve body. This body-shape is not easily adaptabic to the " Body-Shape Rule of ASME Section III, Boiler ~and Pressure Vessel Code". - The analysis methods a~nd a-11owabic stress intensitics use'd are in accordance with the requirement of Nuclear Class I Valves. A - Por the Valve Compon'ents no't covered by the Code, analysis method presented are in accordance with the best engineering practice .
~
and judgement.
~
% Wherever applicable, valve components are also analyzed for Sg level of Seismic loadings in three orthogonal' directions. - i t
O
. 4 g .
- ii
~
i I- .. . JJ l, . . *
~ 7, '
i - l , . . ' ' '~ ~ * . . ., e,'. l
.. - 3
* .e, 4 D w
- t. .
i *
. .t l
{ L.. ' t I , l A l . . ( ,
- 1 l
2-3 , l i
. .."., APPL.lCAll!.E CRITERIA T ANAL.YSIS METIIODS Scope: , , ,
The procedures provided in this document are consistant with, the requirement of articic NB-3500, ASME Section III, Boiler and Pressure Vessei Code. ,
-Abstract: . ,
For the purpose of analysis the valve is divided in the following components: - -
- 1. Pressure - Temperature Rating -
' 2. Analysis of Valve Body' and Trunnion.
Analysis.of Disc ,
- 3. .
~
- 4. Analysis of Stem .
. 5. Analysis of Pin
- 6. Analysis of Bearings -
- 7. Analy' sis of Mounting. Bolts' for the operator. -
1
. i Stresses in these componerits are generated for most severc possibic working condition combined with the Seismic loadings.
For each of the above areas, body of the report identifics
-- .. the applicable criteria (artic1c) of ASME Section III and the method of analysis. Actual calculations, results and comments for a particular valve size arq included at the end.
~ - . .
. h b w
~
. e g
e
-~ " '-_ = w -.- -
-n-,,,wes e-e- -n-,--- -----w-r-- ---
4 2-4 p . V ' PRESSURE - TEMPERATlIRE RATING Critoria$ The service temperature and pr.cssure, of the valve will be in accordanc'c with the articic NB-3531, - Method: Tables NB-3531-1 t'o NB-3531-7 provide design temperatures and corresponding service pressure for 150, 300, 400, 600, 900, 1500 and 2500 psi class valves. Tht tabics may be interpclated for
~
design temperatures other than those listed.' O . 9 9 S 4 r e l 4 O e Q S e l L
- m. -
. . 2-5 .
. ANAI.YSIS OF VAINE BODY
- . 'Minimuni Wall Thickness: .*
. Criteria: -
-
- The minim 6m wall thickncas of thc valve body including the neck shall be in accordance with the article NB-3541.
Method: Tabic NB-3542.1,identifics the minimum wall thickness (tm), for inside diameter (dm) o[ the valve b'ody for primary pressure rating (Pr) .
*3 '
Body Shape Rules: - Criteria: , , . s p . Th'e valve body in question has practically no structural discontinuitics. The body is compact and axi-symnetric. Hence
- the body shape rules of NB-3544 are not applicable in their .
~ '
entirety.* .
. The external fillet radius at the junction of trunnion and body shall be in accordance with NB-3544.1.
Method: . The external fillet radius ( Q) at the junction of trunnion r - . and body shall be governed by : q
. 7, o3(b) where tm = minimum required wall thickness.
mm e d l
- i .
l ,
'1 2-6 j -
i h - Body Primary and Secondary Stresses: - Criteri'a: Limits of the primary and seconda.ry stresses will be in accordance with the requirement of N!k-3545. The primary membranc i
- t l
stres_scs will be due to internal pressure. .The secondary stresses . will be calculated for the following }oad conditions:
- 4
- ?
(a) Discontinuity stresses in the crotch area - (b) Secondary stresses duc'to pipe-reactions . (c) Thermal stresses. f j Method: , i
~
The primary-membranc stress (Pm), due to internal design pressurc '(P) will be: -
~
pm =. (?) (d gj
+ zz :
.9. Im -
~
- Primary plus secondary stresses at the crotch' region (Qp), duc
~
to internal pressure will bc I (3L
+ o 5) Ts
.. .ae = ce .
be
. where dm rA = T' I .
Cp = 3 ,
~
i - Ps - Standard calculation pressure from fig,NB-3545.1-1 or 2 . L -
.: t.
\ . l 5 L.- . l
+
l .
2-7 c, [ i
\
sv Secondary stress due to pipe-reactions are calculated as
- follows: . ' ,
g - fIcl . Ga. where Ped = stress due to direct or axial load effect S = 30,000 psi - Gd = Metal area in the valve body at the junction of' body and trunnion Fd = 1/2 the cross-section areagof standard connected pipe.
. or the value from figs NB-3542.2-2 or NB-3545.2-3 Peb = Ch. Fb. S Gb Where Peb = Stress due to bending of connected pipe Fb = Bending Modulus of connected pipe -
or the Value from figs NB-3545.2-4 and NB-3545.2-5 Gb = Section Modulus of the body at the junction of trunnion and body. Cb = stress index from -fig NB-3545.2-6 Pet = 2Fb. S Gt Where Pet = stress due to torsional load of the connecting
~
P i pe Gt = Torsional modulus of the body at cross-section
' t of the tru'nnion
~;3lll>
W: : 2-8 L i * -
- t
[
. e . -
i ,
- For va1ve application at temperature Icss than 5000F, secondary :
*
- i thermal stresses are negligibic.
For number of operating cycles less than 2000, no fatigue analysis is required.
- For the normal duty operation the combined stress intensity *
.- . l } (Sn) in the valve body shall be given by , i -
- Sn = Qp + Pe .
, s ( t 1: . s ,
1 . , Where Pe is the greater of Ped, Peb, or Pet. l! 4 l .
. 8 .,
- e e
~
- i
- e g .
f .
. 1 i
- m b
- . . l
; (, - '
8 ,I -
- m .
^ - - _ _ - - _ . . . _ . - , - --
2-9 r$ ..
. Analysis of Trunnion *
- - - Criteriar'- .
Trunnion shall he considered a,s,a ctitical part of the valve body since it supports the operator,and is. subjected to the normal l operating load and scismic load from the operator.
.The allowabic stress intensity in the trunnion shall be in .
.. accordance with NB-3546.3. ,
Metho'd: . s
. The stresses in the trunnion sh'all be computed at Section A-A due to the most severe mounting conditioni. as s' own in the figure 1.
The load characteristics in the trunnion shall be as follows:
, 1. Tors.ional load due to the operating torque -
~ '
- 2. Bending load due to the weight of the operator
~
- 3. Bending load duc to the combined effec't of horizontal i . and vertical seismic load acting at the C.G. of the operator.
The Sliear Stress (Ss).in the trunnion due to the operating load will be: . Ss = TC .
. T -
3
. . i Where T = operating torque }
C = Distance of the outer most fibre from the N. A. -- [ J = Polar moment of inertia of the trunnion. i The. bending stress (S2 ) at the section A-A due to dead wt
.e -
of the operator sill bc: .
- S1 .) .C ~
I' 1xx .
=
1 a fe ee--r,----,-- --- - -
.n.,,,,--w,~-v,--w----w--,,m,-- v-,-w-n,--, ,,.-w er-aa,,,- m-,-,,---w-,,r-n,-w.
2-10
.Whcrc M3.= B.N. at the Section A-A .
. Ixx = Moment of Inertia of the trunnion around tho' -
, , ggg .
> - Bending stress (S2) at the section A-A due to vertical seismic load will be: .
S2 a (M2) . C . Ixx
~
Wherc = M2 = B.M. at section' K-A due to Vert. Seismic Lond. Bending stress (S3 ) at the Section A?A due to horizontal
. . scismic load will be: -
) , S3 = (M 3 ) (tz) ggg {. . i Shere M3 = B.M. at section due to horizontal scisnic load. Cz = Dist. of the outer most fibre from Z axis
.. ~
12z = Moment of inertia of trunnion around Z axis. Resultant Bending Stress'(S B ) in the trunnion at Section A-A will be: , l... g M.
- (s, + sg + 93)3'7 33 . .
i' - t I-l l t. e e_ . .
~
g
~ * - . . 2-11 Maximum principle stress ( 7) in the trunnion 5
at Section A-A will bc . e e r = (%^)+JCO,+(50a
- e M
i O e
- G e
i l i e e
- t-o 4
2-12 (
\
\ /
%/
- ANALYSIS OF DISC CRITERIAi * .
Thediscshallbeconsi,deredasapressureretaining component. The allowabic stress intensity in the disc shall bc in accordance with NB-3546.3. , 4 . ..- METl!OD: The disc shall'be tonsidered as a beam simply supported along the stem axis and ' fixed (cantelever) about the
' stem axis.
- The stresse's in the disc will be calculated for pressure load and inertial scismic loads.
~
p') d'. cmax.bendingstress (( ) along the shaf t (J
~ '
axis
'w .
. due to pressure and scismic load will be:
- , C "'
[at ; - L. M a, P Y do.ts s '
.t.q Where Malp = B.M. along the stem due to pressure Mais = B.M. along the stem due to seismic acceleration Ia1 = Moment of inertia of the disc along the shaft
^ axis. . Cal = Dist of the outer most fibre of the disc from . .~.- the shaft axis. 1 1 ti
,ry. .
v lo -
2-13 1
\
1 The max. bending stress ((b) about the stem axis due to pressure and seismic load will be: . (s
= f1as p- t M ab s
~
' C"'
L c.a
. Wh o're subscript ab indicate corresponding values about the stem axis. .
The max. primary bending stress in the disc shall be: s 1 m (G)g 6 = (C + 0 o O e D p ll
1 . 2-14 i
~
, t .
1 I ,
.I
^
s g: ANALYSIS OF STEM
.> s
. .. v, ,. ;
/ \, '
5 )- '/ . CRITERIA:
.'- 5 j ..
f Stem shall be considere'd' as i critical component
\,
' since it's failure can Icad to gross violation of pressurc ,
f' : t' , , ret,aining parts. The allowabic stresses in the stem shall be 3
- in accordance'with NB-3546.3.
s s e . e METil0D: -
~
3
) /
The strestact in the stem shall be computed for pressure, 1
.t., ,
' '^
i
. , ., seismic and tors'icnal loadings.
The bending stress ( k ) in the stem aldnjy axis J * \.\') s , ,
'r
. , e . f',',Jue to pressure load and seismic acceleration of the, disc will
. . -r be: '
- - 2 m a-s ap . @ h (?) Do ( 2)+ ( $XQ
- i. . . - -- -
Whe're a =- Stem overhang . . , ..n ..
~
Bending stress ( k ) in the stem c.ldn3 z axis due t
,t,o seismic acceleration of the disc will be: ,
k -
\ 31 (A/D (o.
f-
~
*iTcl^
*- g
, ? ,
4 The max. bending st.ress ((s ) in the stem will be: i .) , , s
. i ,
% M
/ l , u.ie
[.-
' k s , , ~; - ( h.
-t [E -
1 % k , n- ( .
) ,
\
/
1 , f , r
, p . ~ . - - - , . . , . ~ .
4, _ _ , _ ,_ _ _
,. ___ m. . _ _ - ._ _-_ _._.___ _ - . . ____. .. - _ . . _ . . . _ _ . _ _ _ _ _ _ . _ _ _ .-~ __
. i .
a , . i t
- .', j 4
( 2-15 , ! f . . !
=
1 e - - 3 r s . . .
. 2+ . . .
j-
. , r.Torsionni stress (
3 ) in the stem due to operating l
. i 4
. Ioad will bc: .
1 t } , lc T- i i , - - - a
*. + . S y g3 ,
i 4 f.. I
- The max. stress intensity ((5 ) i the stem will bc: .
2 . . .
- s '
i , s i
- A
*2,, =
/
g -::. ( 5)+ - ( Y l i . . t t ,
#. s .
*; e , . .. ,
1 . 8 e b O
~ '
l
@- ,\
j
/ . I
- i. . . .
, r i .
4 . l
- l. . ..
[ l r
- u .- , ,
- . -
- 1 4 - '
i
..: i i ' :
I . [ , I - l >
.. .f . _, . .
=A -
3
'1 ( ,
. . ) ,
1 fI ,
, / t j_ << ,
-v I
, l
+ . i 1-i s a r
~ - - .
(t e
* . i e
l l .
~ ~
, e
- N l 's.
. rE s
l ' I
/( ar/, /
lf p r
/
1a ,s c 4 .
, i I I e e%t-d vew m% ew b _w.-_e-wew. _how.w.--.-ee.-----w.-wr.-.------,-.--, .--,--+--r,--m-
.- -. . - - - - - - _ . - .~ . ._. ~ . - . - _ . - _- . _ . .- - .
i ' l I
. i j
. 2-16 l
- i ANALYSIS OF PIN l l , , .... .
CRITERIA: , .! Allowabic stresses is the. pin will be in accordance l
. with NB-3546.2. .
- METil0D
- ,
~
4 l The pin will be in douhlc,shcar due to the operating
; torque and inertial loading due -
to seismic acceleration,of the disc. . The max. shear stress (p b ) in the pin will bc: 2 ,L l G .D'- % I ( ~[* ;r ) + (
. .-- = s. ,
I NM hy 7 . A i . I
- r. *
- j. Where . dp = dia. of pin . -
- i. . . - .
j4 t u 1 - l l .- . l* , . e . ti . l=
- i .
i i
= .
l p l I 1 .-. .-. - _ - . - ._ -
-~ ..- -+-
.-~
2-17 i
- n
.'.- ANAINSIS OF BEAltfNCS_ ;
. . )
- I 9'
CRITERIA:- The bearing analysis antt'the 311'owable stresses the bearing sh'all be in accordance with the standard engineering
~~
practice. . 1 . * + j MET 110D: . Each bearing shall be cons'idered to share one-half The stresses in the bearing will b.e due
- of the total load. .
,=
- to the pressure loading and due to the seismic acceleration of the disc.
~ - ,
The max bearing pressur6 will be: g 2 9 ' l' -Y ' Q , 7 y N,I) < A u 8-(La)d l-k 5 T~- Where .LB = Lengtli of the bearing. , , 7 l. t e I l J
- t. .
i, . . l .
*.
- e
.+
+
o e b.,,.,..-..._._.....__,,e~.,._.,-,,..-, . - . . . . , . , - - , ,n.~..~ . . - _ _ - ~ - . , .M:--_-...---.-n-..-.
l 2-18 . i , ANALYSIS OF BOLTS CRITERIA: - i . . . Bolts are critical co'mponents from the stand-point
- of scismic analysis.
- METIIOD: . . -
Considering the combined cffect of s'eismic and direct loading, the max. Ioad .(P 2 ) carried by a bolt will be: 1
- : a .
. 73 =. M P 'd M d wj ct) o-v)(LQ .
([ y ,, n g , g ; n-- [ W P 4- ( A f y ,
.. , s jj Where N = no. of holts in row 2 Other Nomenclatures are shown in fig. 1.
' - Max.tensilestress(k)intheboltwillbe: .
! ~ O . O t. . ,
. Wh'ere At = Stress area of the bolt. '
Max. bearing stress (bI ] on the threads will be: i
- 1. G . m 12.- +
Lt- .. 5 ~* T h (df- d()N I - Where n = No. of threads per inch , [ h = Length of thread
- engagement t da i dia. of bolt
! ~ d 2 = minor dia. of bolt b L ,
2-19 Max. shearing stress ( ) in the bolt will be:
- i .
S
. 2 ( 13 5 ) .
Where Ps = Shear load A3= Arca of bolt in shear ~ . e e
- e .
.* e e
+
9 w,. * -e g e o O gp
. . 1
;a e
..g*
- 2-20
, e j e H f" N 64 Y t'n A TT t'.O.
\ Aumona. R&L. a g, g , % ,.,,,
e.ss + Pn& PANED DA1E n, C .o . C at . n fr8T.
. _..._ ._ ....._...__..__...w. , g . ., , ; . , , . g g g g l
g i j l l , t : ; ,j { ; ; $
..i___ .
s . I i '. . - : g ( 6 . l i ., Q ._. - e * ...
. - _j i i. .
-.I .
a s, _ . . - _ _. - . - - ...... - _ _ _ . _ . _ ._ e._ _ _ _ . . _ i i ;.- . . . .
- < _. t.. ._
._e__ .
~ I l l I e I
.... _. _._ _ i_,._. ~ .,_ l ~_ .. _..._
i . . _ ' _ _ , _ . . _ . , _ _ . . . .. i
- I I . .
J i !l : .._.._.___.__... __-____-_i._ , r l _i_ i I.__6._'._,._-__..\. . l 3 s . .s,
; .a
__ __.! . . -{. Raw b.
\sAI Y8.G
, -~
~ ~ ~ ~
__i__ _' _.._.l_ I_!!._ !.__l._! 8 ' I i
- ___I- 'I i j i
_l_! i !i ,
-i : i i i h.,f _ _ _
_ _ ' F3e ({
, *l.!.-l i i I l .
,h i
~
Q _ O _ . . .. I i: .i t :-.;i r .
~ . . . _ . _: .
I _. ..__ - _' _.1. . p. . . .._ i. V. g .. . t _-_i,I _ I _ _i _i _I~
.a e _ __ u_ . _ _. .W_.. . _ !,__.i 8
O. .-l l
. , ./,t. . . ?
, . . + . '
! l l
_3_!_ 8
\ -
t l
- I 1
- I :y j-
- . l.' .
_e' e l 8
; r . ; i.
A. ,' . _ . ' _ -! i l 3
,._. . _r _ . : _ ?___.
.- I .
__. . _ . i- -._ .
.- _ - t_._1_ _ .
!__ ;__...__h._._.._._!.__. t
~
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__.l ) _ ii_;, 3 I l ; _I_ !_.l _!. _!_! . i i i I l _.i. l l l i l ( 8_ *
- i i
l e ' . i i. i._._ ; _ _._._ . n.
. i
. _ .. _. - _ -4 , '
t i t t t !~ . t : .._.!~ L i. * ' t
,C
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~ 'il~t 1 --___ _ _ [i . _ _ _.a._.._ T I l_ _._j f_,_- i ,
l
., . . . i l o . l l ! .
.o__,' . , . . . .. . . _ _ _ . _ .
l l I i i *
- y. -
._ T. 1 x __ _
~
_ s .. . .. . g t .._.- f _ . .i _ .... _.,_.I.-_!._.______ I ...._-.,/... . . . . . . . _ . _ \ . o o * :
. ,. . . .f . i
._I
; 1 6
.;._. _ ,_ . 1_. ..... .
l L
.____._..c.____.. -
. s .
. _ . -.. - - ! _i _ . .. .t..
,- . , . _ . _ _i _' _. s s
.4 c
t;. _
+
t __. - g - -y .
, , g-.
, t . . .
l _!_'_ __,_;_ _ _....'_i a i !
- 1. 6. .! _ .i _ i 4
i i. i . i t 8. I 1
.Y 0 5 E. . 6 C. CM LO w . .. .d .. .. . - _ .
g 1. . _ . . . 1
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- i
....t..
i .
.i . . . . . - .t - . . . . . t . *. _ . I I ;- - .1 ' _ : g_.
- l. .' __?y, .
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. , . . O . . . .
..,.._L._...., . . . . i. . . . .
i
' i I. 'l ! .... . . . . 1 ... + ._ . .i._. . .
a e
._ _. **=.. -
l. g s e I
.?._ l_.e._ ....b* ... - . . .: ' _ . - '._.-.-[.-.,-.
s . . (.. ..I
. t . l 0 $ 8 l
6 ,I t . t * * . , a a. e I I . i . e l
2 . I d 2-21 I f . .. s - i i i .. 4 4 i, . . 4 i i 4 g ANALYTICAL CALCULATIONS . FOR .f VALVE SIZIf: /E 'ved . TYPE: 881 - i iG rb-r- S bb E*"* 2,E*17- Co Prepared.For: Eocut Savu Customer Order No. : HIB-)95 h, A. ing s ,[ N - 6?o 3 -l' Henry Pratt Order No.: o.wcl 1
- - W - 696.lt-E o f 3- ,
a O g
**
- 6 =4 ,
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- 9
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6
- l
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. 7 2-22 1 .
- SUFDIARY OF RESUI.TS ,
1
* . *b-BODY ANAI.YSIS 1
SECTION Ill 'INAL SIS STRESS AI.I.OWAB LE STRESS I.EVEL STRESS CLASSIFICATION SYFIBOL REF. PAGE
~
i i ~ Primary,F!cmb rane Pm 6 ' l t'lo *O J g, 3 a ' e strcs.s 1ntcns1ty
- 3 G 2137 04 2.~1 4.fo
- Pr. + secondary ,,
Qp > . stress due to - internal press , Secondary stresses Ped d 7 7g.o 2 7, 4 fo
- due to Pipe reaction Pcb .
, j7,y,fr.3 >7, k f Pet I
i 17o).*43 . p.7, Wo
,. Combined stress i
- intensity 3y,9,p g4,9o, 1 . ,
.~
r - .
~
l.
+
l - -
. e i
t' . i . . i i 6
2-23 ('
SUMMARY
OF RESilLTS
*[i.
VALVE C0i!PONENTS ANALYSIS STRESS ALL0tfABLE COMPONENT LOAD STRESSES
- CONI)lTION IlEF. PhGli LEVIIL il /2/6 %I, 780 Body-Trunnion Operating load Seismic load 10,179 53 S Lt , 0 0 0'
. Disc Op. Load + 13' Scismic load Stem Op. Load + . IS' /deff2 2 4, oo o Scismic load his c load
/#b 7 7N ##
Bearings Op. load. + gg fgg7, f 5' gooo Scismic Icad Bolts , - Op. load + j9 jg.j 3i t
- S i C/,6 o o Scismic load
, O -
-V . . .
e e 8 6 6 9 ( I i
' ++
i ' s . 2-24 4 l 4 . . i
. .. . PRIISSilRE-TEMPERATilRE RATINGS I -
. CALCUI.ATIONS:
. 4
. . . . f .
1 Valve Size. .. II inches End Connections (Flanged / Weld) F/ame el
.. Press.ure Class
/5 o psi Service, Temp (from customer's spec.) . - /00 0F A11owabic Service Press. . .
~. .
. (from tabics NB-35.31-1 to 7) 87[ psi Max. line press (from customers spec.) 46 psi ,
- ~ -
- - Comments: .
.e 8 .
,. .S .M .
g , e
\. c
=
s , 1 t f. 4 . ', . , e e + o - . f , e [ , .
- e e ,
l *
. . i i-t,
- I
- s. ..
' - r I ,
l l
- l. .
1 l 2-25 1 VELVEdoDY l
. j
., . h... . ,
Calculations: . Minimum 11all Thickness: . ,- I Ins'ide dia, of valve bo'd'y (dm) = - 18',/2 5" inches I e Primary Pressuic Rating (Pr) =
/ d'o psi . '* Miniinum ifall thickness (tm) =
- 4 ff __ inches
-(from table NB-354 2-1) ,,
Actual ifall thickness (Tm) = 3 4 3 76' inches # 4 -
- t. .
=
t
~~ .
Body Shape Rule: , t
~
N/A inches Actual external fillet radius (R2 ) - Required Fillet radiuss s
- y> a .3(%)
l-
.- n/a .
Comments:
- e o * * ,
O - . , O 8 l l - I.- T - i . l b . c-d. i i . 3 w.~ ,s,e---,- -mn ,-vm-p-v-,,,w,_-,-,,,.,, ,,,,,w-wwww-,_,an_ _n---.=
- - - - - , , - _ , , . , _ _ ,-.v-.---,--..n-- - - - - - . - - - - - , , - -
2-26
~'
Primar
- Mcmbranc Stress: 0 Design Pressure (p) = , / Q psi *
- p. . #+ 0 Primary Membranc Stress (pm) = P. Im . _
(16*o)(,lf81.C) 15e
~ 3.L3 L**S;17)
+ 2. -
= IP70 psi
- Allowabic Primary Membrane stress ('Sm) for the valve body ,
# A STM ~ /) 6/4 , CT E 'If material (from Appendix I, Tabics 1-1.1,2,3)' . is O /F,3#8 p s i '-
J Comment: ,. e 4 .. ,
* *e e v .
e
. O 9
G e-0 0 e t-
, e e *
- 9 e .
.o e
a .
. - _- . o, - . _
4 * - 2-27
~~ .
T
. Primary + Secondary stress due to Internal Pressure:
- 9, o (2S~ inches M L
.= dm
]
=
T . . 22 . Ps -(from fig. NB-3545.1-1 or 2) = psi QP
- 3 & *5 fS . .
T~w
- f. o C 2-S' 5M zz5 '. -
=
3 ['~ - + - . 3 les 7.5- a
~
~
t .
= 3 fl ~7- ol l - psi
., 3a
' ~
- Secondary Stresses ,. . ~.
Outside dia. of Valve body (d o) = % 6' inches
*-r 1 1 _
gM Gd = . ",TT = 0 q , 4 i- - . i z- '.
, (2.6)s
[/+ - (16'* l3 0 _r . ,
=
- . 3-96' 4 Y Sq. In.
Fd..(from figs NB-3545. - 2 or 3) = 7'/ - l -
.. i Fb (From figs.NB-3545.2-4 or 5) =
C3 .
~&
ly . %- 9
.3 te. .= --
~ , -
- O hC M ,
e s 4(3,te37s]
. ( o-5~ + 1ff*I d .)
t- - 3 8 S' W i-6, e . e l .
{.' 2-28 . from fig N!!-3545.2-6) = /0 Cb (F6r t c.value of
- q T ,4 ~
- Gt = T So -- cLw , . .
lG- a . do. - .
'(.*>S.)N (.I% 11 S T( - .
=. g ' -
%b,
~
- 2.2 2 o . ~5 5 , :
X .
~
Ped = Fd. (30000) : g. . . Gd.
... ~
. 7 l (3 0 ~) .
-. wu w. . .
~7./ r It s
~h ,
.Peb = Cb... Fb . (30000) *
- 'l Gb .
., , (/) ( (3) (3 #DD)
. itt 0." l T ~
l702 - !+3 vst
. s Pct = 3..Fb. (30600) '
Gt (9J hb /-
>f -
pzo sc . 0170 1- t-3' / psi
. g.3 e e i se /no M 9b
- = -
v,_ .. 9 ,e w,----,,--,-_ .v,,-a-~ ~ _, ----~,n_, ,w,,-n ,, w___-,-,,,_w-w,,ne-,-,-- m ,.,,,,--n.-,.-,,.-,--e,--wn-,ey-.,,,n,ne ,-.-------e-. ,-,-% ~.
{. .i
' - 2-29 F s' .
.- . s i
f
. Max. Secondary Stress (Pc) due to Pipe reaction will bc -
j- greater of Ped, Pcb or Pct L l Pe = 1 7 0 2 e lf 'A psi i i i
- Max. str[ss intensity (Sn) in. valve body: l 1, .
l Sn = Qp + Pe . 4
. . ' 3 ll 7, o 4 + l7o 9 - ll 3 Sir l ? >t l 7 psi ;
i
. .~ s .
Allowable stress intensity (3Sm) = s
~
$/f f o-o/ P s,1
' Comments: ,
i , . 1 . .. . s . . .
- t. . . .
i . . . 1 . . r . 3
, ~
. . , e g .
e* e , S
* . e
- t, -
e , .- - r l, .
~
o
2-30 i . . , BODY TRUNNION 4.. . .
~. .
. CALCULATIONS: ..
Max. Oper,ating Torque (T) =
.,. . /f.76 2 in. Ibs.
Wt. of the operator (if) = ~774 lbs. Dist. of C.G. of the operator
- fros Section A- A (L) = 8'b inches .
~
. Width of the tpnnion (B) = ,
. if inclies Dcpth of the trunnion (D) = ,
f e .2 8 inches Dia. of the Stem (d) =
- S*:2. 6* inches -
m
. Dist. of the outer most fibre I" 42 5' inches from x-axis (C) = ,.
~ -
. Dist. of the outcr-most fibre .
4* ' d o inches from z-axis ,(Cz) = .
~
Seismic' accelerations gx,gy,gz'=
~
f .
*f ?*h s
- n. , e 3
j
. T
.. . , t.
9 S O
^
~~~-ve--nn~---------,--,_------,-n.- , - - - - , - - - - - -
2-31 a- ., ., , . i .
') .
IFx = 1/12 BD 3
,~
'lT d4 d... 6Ts9u.zrf.4. < 2 24 13- 4 76J./ in.4 3 ~lf d4 Izz = 1/12 DB .
64 , (s zs-) crf- 'u 1 ( * *")q
.1 s> .
~
- a. 2 2. 7_5 t>
, q .
. J . IXX + IZZ '
t ,
' '. 95*2l + .2.2.2 9C -
. 3l7, 7 6 _in.g
~~ .
- ~
M.., 1 .W , (.776_) ( G ' 5) - Foli,00 in. 1bs. tf
~
M2 O')-C823 CLI .' ~~
. (774) ((j (6 5) '
'3 o, J- 64 e o in.lbs.
- ~
t M3 - OY) (EX) (b)
.(.726){s-(is~)' ) .
35,110 t- i n . lb.,s . sy . (Mi) C ! 7 Ixx l b
,. (56 It ,ogg
, 815' Al i
( e 4** I o
- j
. 2-32 L .
.S'2 = (M7 ) C .
, l x.x . .
, . Sa:1643(2 62O .- ,,
9 5^ s t
. S 3b 3M psi S3 = (M3)(C,) -
Izz *
..(16ti67,5)Dt'o)
* * *' 7 F 'Cis 33
_ psi
- - Ss = ,
. . (teagz) (2 !15) - -
~ 317, 14 , fgj p,1 i
. ,- tiL SB" -
.. (S 1 S 3 2 2 + (s 3) 2 ~
.r.,;st .- .
l,
~? ,
* [ t 39 o b + %'3 4
- 40)"-t , (6 9f' 3 h.)13 '/n _ :
' il 95- 3-7 psi l,> ". -
["h+, .- f by .+ (Ss)2'
. Iq - .
- 5I
&y (II9'9}"4'(/5/)*'~
/2/6 psi 1
l Allowabic stress intensity for class I and II scismic operation
- 01,76o psi (1.,2 Sm) = '
Allowabic Stress Intensity for Class IIIScismic operation - f . 2-7,45'O psi [ ~~. (1.5 Sm) = , Comments: .
" (, .
l.; _ . g .
,e.., - - - , . . . ,,.-.%. . , . . , - , . , - , . + . -
2-33 . 3 c. DISC - s ,.
,, ,, .{ CAI.CDIATIONS : ,
.G . g I7'37 1- Dia.'of the Disc (DD) = ,
s . inches
. , .,. i . 3 . .:. - . W t . of tlic Disc (ifp) = I46 lbs. .
Cal = 1 343 inches
~
~
Cab'= l64-3 inches Iai = i s. d 'k in.4 3 6' lo
.in.4
~~
. Ialy %
C.G. of the half' disc (Xc) =
. , 7- 3 in. .
Malp = .113 P(DD ),
~
- =
e il 3 (.f ro) (17 37]3 ,
=
. isnr3 7 4 in. 18s.
6.
. Mais =gD ) (gz) op .
,. 1
' ~ -
. =. ( 1D-)(
- y. 0 (17 31) .
. . '5 7 7 7 , 9 7 i n..1ss. -
t . .......:- - (4)
.Mabs = 11g T gz _g
.' >) .
a
= (r Pu s--) ( s) (~l 3)
'bl75 ' S, in. Ibs.
..s-' . . . .
. . ? .
~.Mabp'=. 0833 P (DD )3 -
=
- 0Y33 (I.To.) {ll 37)3
; (6, 4-T4 o I in. Ibs.
ti . s .- e e 4 m - , . O ,. IT
l 2-34
/,m') r- .
\, / -~ --T - .
__~ -
. 2 . . , .
~
ct L = Malp + Mals , Cal .
.' lal /
~
= { WV319ll.e3777-7{.l'3/r3 . g, y
- 9T55 L t psi k =
Mabp + Mabs
, Cab Iab 9 f
- { C 5'Irtik o off .{- 3 1 7 5 5.. .l* 3 I .3 3 g, ,
s
."2. C 3.~U o 6 psi
{ (%
=
+ (OQ f '
= [(9 r 55 9 + ( zaq Jf~ '"
10,111 53 psi Allowabic primary ncmbranc stress (Sm) for the disc material: -
*/15 '/ /9 - /2 3 f / OfR C.F5 (from Appendix I, Tables I-1.1,2,3) is 40;o00 psi
'The max.' allowable primary bendin'g stress intensity (1.5 Sm) = S o , 07) o psi A11owabic stress intensity for Clas's I and II Scismic
~
anperation (1. 2 Sm) = . 14, e o psi
., Allowabic stress intensity for Class III seismic operation (1. 5 Sm) = 30, N o psi
~
, Commen ts : ,
. g. .
L..
/
/7 \
r y\m,;
y 2-35
. . STl!M CALCllLATIdNS : .
Din. of the stem (d) = ,+ 2* W inches Stem over. hang (a) = *- e Oe[ ' inches vi-e[(00)f(0+(yN.*6A 32_ ' I." (17 37.)'('y) t('?-l') (.() - (o d
-r(p..>cf *
=
2 J 7.3 ' 8 3 1.1 psi -
~ ._7 ~
~
.,. os
.. Jb 34)(b) 09
-. 1r
. _-32=
p zd d' 145j 3
> (g)-(a.9) .
311 1714 psi 65 -
,$ (. G ). +- ( 6.) b g,
, ( l'29 7 3, d3[-t- ( 3 31' ISf6) 34 psi
. . - 12377 IG I l
i
-} . _
Td . .
,
- IC (,/93023 -
. -s p. w.).3 ,
// fd psi t, .
. # a 9
. r 1, .
l
-,m _. _ _ _ _ _ - -
a 2-36
.. ~
O. - 6 .
~
o m-q. 2
/ S-2 -Iz
,/
{ ~r~s ~.2- /3 Y I (./
.h... 1 e
A -# ( gg $,1/'
. ~
.(12.,977 3g /12 9 771C + -
.l .( -
+ l -
-g. .. -
' ~
/f 9/A psi The max, allowabic stress intensity (Sm) for the stem material , ,
/f$ TM - A h77, 73p. 3 / I, frotr.tAppendix I, Tabic I-1.1,2,3) = 70 f N psi Allowabic stress intensity for Class I and TI ,
-Seismic operation (1.2 Sm) = . .0 N N psi
. Allowable Sitress intensity for Class III Seismic ,
. Operation (1.5 Sm) = *
- 300-00 psi g
.* , 6 Comments: - -
*.
- e
. g
- J . ,
* ' * ' ee-4 , ,
g, A O
' 2-37 i
3 t l . PIN -
.*t -
CALCUI.ATIONS: .. . Average dia. of the pin (c[p) :' I ; . 0
- T T74nches dO gy A F
4_ -r 7P 2 g J.f - b %f + k N )2.- - _ , i /> l+.
*~
(145j (s') (/./].502. )> t 3 ' '-' *
;z irlo.tr7S).
i-
/0967 p .s. t X.
The allokabic shear stress intensity for the m. pin material - A S*TPI - A 477, Tw. 3% V y *. - is (.6)(.fSy ) = s
. /62 00_9si a ,
Commen.t:
- ~ -
- ~..-
\ ..
s b
- 1 e
4 g . . .
- O
- e. y
. 9 -
e 1 - - e
.* . p
** e
.. . "a p
~
.- I . . *e 3 i
. t i .
- e, i .-
- ee
- l. -
- , g,
) r s... !.
- e. .
t I e
.h, - - , - - - - - - - - - - - - - , - - - - - - - , - , -
2-38 BEAllING
..m . .
CALCUl.ATIONS: , Length of the bearing (Ln) = *-
- 4'32+37f inches P
D + D ^ 1(L-6)d I J [ 5 (,I7'3 l) (IS*o) +-
., tr (li f) {&
t 1(9 5 co$7Q (2* 2-5)
, , 1967e / 5" psi i
g g ; .
.The allowabic bearing pressure for bearing material I ' V 10 'h
-is 9-00o psi Commenf: :
I ;
- e 1 -
1 . l e - f l
. .-. .- .-_-.__.___-_-_~.-
- a. _. .-_, -_-
- 2-39
. .. . \ c -
. : 1 BOI.TS l
. - CALCULATIONS: . .,
a Type of bolt 5,
/9 -
[ 3 /Y C Bolt Material * . S A 6 - Gr 4 2. No. of threads per inch (n) = /3 Length of thread engagement (h) =
- < F/ d inches Dia. of bolt (dl ) = .
o - 5~ inches Minor' dia. of bolt (d2 ) = " O'l-/ inches
~ ~
Tensile Arca (At) = , O '/4/ f - Sq. In.
*.. ~
Shear Area (As) = . 0 ' / % 5' 7 - Sq. In. t ' i . . 1: rom the fig. 1 Ly = 4 ( 2 5' inches dyy = - #'IV
- ~-
,,.~ d12 "
s
' b'
. s y 4
- .. . .A
.r e e
- a
. . O
... e . .
' s
(- - r . #
- e
^
. 2-40 1.1=~ . _ : .. - ,
P2 = (N)(f.y)(d12) (N)'(n ; [1) # + (d52) 2_ N {GfiDg)+ , (1.y) (d12M (d 1 Z)_]_N g,<) ' {*574 ) m( D UY 'r j 2._
- (7 7c.) (,6.cw)Lu -t 4 cu .or i ~
- [ (,.o rj % (0 5 7r.f.3 2- C(.*650 '21 ~7 *). *90 lbs.
c "JI 72*] , Maic. Tensile Stress ( N ) = , bt '/4 / 7 ,
- = ,.
/5~,' 311 Y 7 p.si
, . ~
a ,
~=
) =_4. P7
* Max. Bearing stress on , threads (
' T.h(,0?~~Lk,f 2 (uy(>.729)
. :* ~* - -
~
s _(,6411-T){-iY 17 ~ U " $3 l'0
/ o . 3 I psi a
* <>.9 L .r. ,
= ,
f Max. Shear load (P 3) ,= W + N(gx) . , ' i . t
. 17s t- 7 re(s) 4.c, s- e ~ vis.
. i Ps.
Max.. Shear Stress ( h ) = Xs uts-L -
. - ,1257
= "b '[ c 4 o '
- 5 7 Psi _
SI, 3" Psi
..Allowabic Stress Intensity _
_v Comment: i
~
l -
f
~
D 3-1 1 i i r ATTACHMENT 3 I r General Arrangement Drawings ' I : i (PROVIDED ONLY IN NRR PROJECT MANAGER COPY) t 4 i l l , 1 I e
- l 1
i
- . . . - - - - -}}