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Revision as of 23:00, 26 February 2020
| ML20027C963 | |
| Person / Time | |
|---|---|
| Site: | Clinton  |
| Issue date: | 10/22/1982 |
| From: | Wuller G ILLINOIS POWER CO. |
| To: | Thomas C Office of Nuclear Reactor Regulation |
| References | |
| TASK-2.E.4.2, TASK-TM L30-82(10-22)6, NUDOCS 8210280089 | |
| Download: ML20027C963 (369) | |
Text
{{#Wiki_filter:_ _ y r. I. ILL/NO/S POWER COMPANY y f3 (79_;gyg 500 SOUTH 27TH S'REET, DECATUR, ILLINOIS 62525 October 22, 1982 s Mr. Cecil 0. Thomas, Chief Standardization & Special Projects Branch Division of Licensing Office of Nuclear Reactor Regulation U. S. Nuclear Regulatory Commission Washington, D. C. 20555
Dear Mr. Thomas:
Clinton Power Station Unit 1 Docket No. 50-461
Reference:
(1) IP Letter U-1431, from G. E. Wuller to J. R. Miller, dated 3/10/82. (2) IP Letter U-0544, from G. E. Wuller to C. O. Thomas; dated September 16, 1982. In referenced letter #1, Illinois Power Company committed to demonstrate the capability of the Clinton Power Station (CPS) containment vent / purge butterfly isolation valves to function as designed through further operability analyses (as required by TMI Action Plan Item II.E.4.2(6)). Enclosed are copies of the completed analyses required regarding CPS Safety Evaluation Report (CPS-SER) Outstanding Issue #10a. The manufacturer of the Clinton Power Station Unit 1 Containment Vent / Purge isolation valves, Posi-Seal International Inc. , has performed a dynamic analysis to assure subject valve operability with the loads experienced during a combined Loss of Coolant Accident (LOCA) and a Seismic Event. These analyses were performed in accordance with the NRC guidelines provided to Illinois Power Company (IP) (" Vent and Purge Valve Operability Review List") during the November / December SER meetings. The results are summarized below:
- 1. Valve closure times during a combined LOCA/ seismic event 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. Comparisons of calculated no-flow closure times with actual no-flow closure times support the models used.
- 2. The operability analysis compares the torque requirements of the valves, with the containment and drywell pressurized to 9 and 30 psig respectively, to the capability of the 3 00/
u M iTEb MT.
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[ > T. U-0571 L30-82(10-22)6 October 22, 1982 Pagc 2 actuators to close the valves. The media flowing through these valves is steam / air at 100% R.H. and 330 F. The results demonstrate the capability of the valves to close under all postulated accident and operating conditions. The effects of piping bends / tees and valve orientation were considered in the torque calculations by modeling drawings of the piping / valve configurations at Clinton. In addition, sealing integrity has been evaluated. The Posi-Seal butterfly valve sealing mechanism is a combination sealing ring / backing ring. The sealing ring is made of an inert, low-friction, wear-resistant elastomer called TEFZEL. The dynamic sealing mechanism involved results in a tighter seal than that typical of more resilient seals. Details of this sealing mechanism have been provided to you in the Reference
#2 letter.
Posi-Seal recommends two actions be taken to ensure valve operability, and thus the validity of this report. These recommendations are as follows:
- 1) For all 36" valves, it is recommended that the body / bracket bolts be changed to A354 Gr BD material, since in the event of a combined seismic /LOCA loading the present A193 Gr B7 bolts will be overstressed.
- 2) The subject valves will perform properly provided they are installed with the flow resulting from a LOCA going in the preferred direction and oriented as recommended.
IP agrees with the above recommendations and proposes the following actions:
- 1) The body / bracket bolts of all 36" valves will be replaced with bolts made of A354 Gr BD material.
- 2) The orientation of all subject valves will be checked to either verify they match the recommended orientations, or the orientations will be revised in the field. IP is currently checking the installation orientations of these valves. Any discrepancies will be corrected appropriately.
As a result of our meeting with members of NRR on July 20, 1982, we have reviewed potential modifications to the CPS i containment ventilation system which would eliminate the need l for the use of the large vent valves. We have determined that such modifications would cost a minimum of four million dollars and could impact our construction schedule. It is IP's position l
r N U-0571 L30-82(10-22)6 October 22, 1982 Page 3 that the enclosed report supports our intention to utilize the presently-designed containment HVAC system on a continuous basis during normal plant operations. This is consistent with our position on continuous vent / purge as previously discussed with members of the NRC Staff. In summary, we request early staff-review of this report and propose to meet with you, as required, such that this issue can be closed out in the next supplement to the CPS-SER. Sincerely, A * ,e G. E. Wuller Supervisor-Licensing Nuclear Station Engineering TLR/jmm Enclosure cc: Mr. J. H. Williams , NRC Clinton Project Manager Mr. H. H. Livermore, NRC Resident Inspector Mr. L. C. Ruth, NRC Containment Systems Branch Illinois Dept. of Nuclear Safety bec: . CPS /DRC -(0982) L. J. Koch, B-25 w/o encl. J. D. Geier w/o encl. J. S. Spencer w/o encl. E. W. Kant w/o encl. D. L. Holtzscher w/o encl. T. L. Riley w/o encl. C. C. Wheeler w/o encl. L. S. Brodsky, T-31 w/o encl. J. G. Cook, T-31 w/o encl. H. M. Sroka, (S&L), F1. 21 w/o encl. D. P. Hall, B-16, w/o encl. i
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. ! OCT : 1 'A9-- Ir!il v v'.
q My yf c-. : i j POSI-SEAL INTERNATIQNAL,INC., (-) .yL N a4 . ~u . yggg~i-,..g.g .;g DATA TRANSMITTAL FORM To: SARGENT 6 LUNDY ENGINEERS D ATl: 55 EAST MONROE ST. ', , - - , . , , W "/ " CHICAGO, IL 60603 ATTN: H.M. SR0KA/J.i... DCDECK
SUBJECT:
CLINTON POWER STATION UNITS 162 BUTTERFLY VALVES SPEC K2S68 __ PURCHASE ORDER NO. C7902 ANS.BY POSI SEAL REF. NO. 16204 rn Gentlemen: The documents listed below are subrnitted for your accrovat as recuired by the subject purchase order and referenced specifications Robert Please J. Seknowiecce tites receipt of same by signing and returning one copy of this form to the attention of: item Description lRev. j Copies 1 NUCLEAR SEIMIC 5 LOCAL ANALYSIS 16204SL-001
!1 I I I
(. I I f l l. l l NOTE: IN ORDER TO HANDLE YOUR ORDER AS EXPEDITIOUSLY AS POSSIBLE, APPROVAL SHOULD BE RETURNED NOT LATER THAN 11-1-82. CC: .'ACK ORCUTT-EQUIPTR )L MR()IILL HARRINGTON m , PROJECT MGR. iMt[ L. y T.t t i e Date Samt'By y/ NOBEM 5 N TdS^'\ MANAGER-CONTRACT SALES 9/30/82
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TABLE OF CONTSITS Page DiCLOSURES . ..... ............ ....... ... 1
....... . .. . .. . . . . .......... i REFERDTCES .
S'U! GARY . .. ..... ............ ..... .. ... 1 IDCA SCENARIO. . . .. ....._............ ..... 3 INTRODUC, TION . . ...... .. . . .. . . ........... 4 RESULTS. .. ... ....... . . . . . .. ..... ..... 6 CONCLUSIONS. ... .. ..... . . . . . . . ..... .. ... 8 IOCA ANALYSIS. . . ..... .. .. . .. . . .. ..... ... ,9 Modelin6 the Piping System. . . . .. . ...... .. ... 9 m 16 (,,) Determination of Flow Conditions. . . . I . . . . . . . . . Simulation of the Actuator Stroking the Valve Close . . ... Ik Derivation of Torque Equations. . . . ............ 15 Aerodynamic Torque. . . .. . . .. . ............ 15 Pneu=atic Torque. . . . . . . .. .. ............ 17 Spring Torque . ........... ............ 19 Bearing Torque. .................... .. . 19 - Inertia Torque. . .. . . . . . . . . ............ 20 PICTORIAL MODEL OF VALVE ASSE! GLY. . . .. . . . . . . . . . . . 21 22 SEISMIC EQUATIONS. . .... .. .. .. . .. ... .. . . . . . . 22 NATURAL FREQUENCIES . . . . . . . . . . . .......... Lateral - Disc / Stem . .. . . . . . .. ..... .... . 22
. .. .. .. .. .... .. .. ... 26 Longitudinal. . . .
Vertical. . . . . . . .. . . . . . . ...... .. .. . 3h Transverse. . . . . . . . . . . .. .. .. ... .. ... 37 . G
f O Pace VALVE STRESSES . . ....... . . . . . . . . . . . . . . 41 Actuator / Bracket Bolting . .. . . . . . . . . . . . . . . h1 Bracket. . ... .. ................... h3 Bracket / Valve Bolting. .. .. . . . . . . . . . . . . . . 43 Valve Neck . . . . . . . . . . . . . . . . . . . . . . . . kh Valve Ste= . .... ............ . . . . . . . 46 Valve Dise Pin . .. ... .. . . . . . . . . . . . . . . 47 VALVE MID PIPING SECTION MODULUS . . . . . . . . . . . . . . h8 DEFLECTIONS. .. ............. . . . . . . . . . . k8
. VALVE BODY BOLTING . . ... .. . . . . . . . . . . . . . . 48 DETAILED ANALYSIS . . . .. ... .. . . . . . . . . . . . . . . 40 INFLUENCE OF BENDS AND E . .... . . . . . . . . . . . . . . 53 -
APPENDIX A - Sche =atics of the Piping Systeb B - Determination of F3ov Conditicns C - Deter =ination of Closing Times D - Comparison of Actual to Calculated Closing Times E - Seiscic and LOCA Stress Analyses e e e 9 9
^
O
Op . ENCLOSURES (1) Valve Assembly Dvgs. 1620h-28 Rev. C 16204-29 Rev. C 16204-31 Rev. C (2) Posi-Seal Technical Bulletin No. 2, dated June 1982
. (3) Derivai, ion of Eydrodyna=ic Torque Curves (4) Posi-Seal Technical Bulletin No. lA, dated June 1962
~ , s
. (5) Calculations of Various Input Parameters PHbRENCES (a) "For=ulas for Stress and Strain" by R. J. Roark, McGraw Hill, 5th Edition
. (b) "Flov of Fluids through Valves, Fittings and Pipe,"
Technical Paper Nc. h10, Crane (c) " Mechanical Vibrations," Church, John Wiley & Sons (d) " Advance Strength of Materials" by Seely & Smith, John Wiley & Sons ( (c) " Eccentrically Loaded Joints" Machine Design, August 1967 (f) Sargent & Lundy Engineering Change Notice No. 2962 (g) " Steam Tables Keenan & Keyes, Hill and Moore (h) Sargent & Lundy Dvg. M06-1110 - (i) Sargent & Lundy Dvg. M06-1111 4 9 e m 4 u.
O( SUWJLRY Due to the design of Posi-Seal butterfly valves with the disc being asymmetrical, flow in tile preferred direction tends to close the valve. In the nonpreferred direction the disc tends to stay in the open position until it reaches a valve angle of approximately 75 , then tends to close. For scme of the pipin6 syste=s investigated, the aerodynamic torque resulting from a'LOCA is of such a large nagnitude that the torque vill overcome that of the valve actuator and partially close the valve if the flow is in the preferred direction. These torques, with the valves in . the nonpreferred direction, are so large that the actuator cadnot overcome .
,. then, thus the valve re=ains in the open position. Therefore, if the subject containnent isolation valves are to properly perform their function, it is imperative that they be placed in the pr5ferred direction such th'at they vill go to the shut position in the event of a LOCA. The preferred direction is shown below.
FiCure 1 ( - RetaininE Ring - y l -< Flov i 8 d ' / h ' k-- -
\/' Scal u.
.1-
- . - . . .- ...-. - - -..--....-.-.. .. .- . . . . ~.. . . . . ..... . .- . . . ., .. For all 36" valves, it is recon = ended that the body / bracket bolts be changed to A354 Gr BD, since in the event of a ec=bined LOCA and seismic accident the present A193 Gr 37 bolts vill be over stressed. Recon =endation concerning the orientation of valves IVQOO3 and IVQOO4B are given on Pages 53, 54 and 55 As can be seen in the results on Pages 6 and 7, the aerodyna ic torques do not exceed the maximum allowable design torques of the actuators, nor do the loads imposed by a LOCA and a seis ic evert result in excessive stresses except as noted above. Shown on the following pages is a scena-lo of whct vill happen to each valve in event of a LOCA. C ~ O . O G 4 4 e e n v . O E
. . IDCA SCENARIO CASE 1 & 1A -
24" Valves 1VQ001A & IVQ0013 CASE 3, ?A
& 3B -
24" Valve IVQ002 and 36" Valves IVQOOhA & 1VQO0h3 CASE 5 & SA - 24" Valve IVQOO2 and 36" Valve IVQ003 i CASE 6 & 6A - 36" Valves 1VIOO1A & IVR001B Valve
. Preferred Direction The aerodyna=ic torques are of such large =agnitudes that they vill overco=e the pneumatic torques of the actuators and partially close the valves. Upon .
. cetuation, the valves vill fully shut.
pf . Q\J- Nonpreferred Direction The su==ation of the aerodyna=ic, packing and bearing torques is greater than the spring closing torques of the actuators, thus the valves vill remain in the open position. CASE 2, 2A
& 23 -
'10" Valve IVQ005 and 36" Valves IVQ00hA & IVQOOkB -
l CASE h & hA - 10" Valve IVQOO5 and 36" Valve IVQ003 Preferred and Nonnreferred Directions Flov through the 36" valves is not substantial enough ! to cause significant aerodync=ic torques since flow i through the 10" is choked. As a consequence the valves ( vill re=ain open until the valve is actuated shut, then they vill fully close.
- v/ (
l
Cc INTRODUCTION The objective of this analysis is to show that the subject containment isolation valves can withstand a Loss of Coolant Accident (LOCA) as well as a seis=ic event of g magnitude as given in customer's specification and still maintain operability. The escape of contain=ent atmosphere during a LOCA will result in large aerodynamic torques on a valve assenbly if it is in the open position. This analysis will detemine the effect that aerodynamic , torque has on the valve assembly and its operation.
= -
cf . The seismic aspect of the analysis vill consist of determining the natural frequencies and stresses of the valve assembly in accordance with references noted, assu=ing the basic valve body to be rigid and the actuator to act as a lu= ped mass concentrated at its C.G. and rigidly connected to the valve bracket through the bracket bolting. The purpose of the frequency calculations is to show that all valve assembly natural frequencies are greater than 33 HZ and therefore, static ctress analysis of the valve is applicable. Where resonances occu- below 33 HZ, valve and/or bracket are modified in order to drive the fundamental natural frequency above 33 HZ. c h- . _.-_ ___. .. _~ - , __ __
CC Those critical sections of the valve esseioly such as the bolting, neck, stem and pin are analyzed assuming a g static load (magnitude per custc=er specification) applied at either actuator or dise C.G. , in
- each of the orthogonal directions simultaneously. Seismic stresses are combined with operating stresses as well as the stresses due to the IDCA aerodynamic torque.
S 9ction modulus of the . valve body and deflection of the actuator relative to the valve due to seismic leading are also analyzed. All equations are either straight forward or from reference (a)
- unless otherwise noted.
{, ' 0 e 9 9 6 S 9 ( O' . 5
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.; m.-
! RESULTS
~
Tabulation of Maximum Aerodynamic Torques and Closing k'ines Valve , Matryx Max. Aerodynamic Design Torque Closing Times (Sec.) - Case Size Actuator Model Torque (in.lbs) of Actuator (in.lbs) Normal Preferred Nonpreferred 1 2h" 33082-SR80 47,825 57,955 1.3 07 - i la 2h" 33082-sR80 h6,611 57,955 1.3 07 - 2 36" 45102-sn80 2,769 166,660 3.2 3.6 3.9 2R 10" 26062-sn80 '2,048 - 25,h13 0.6 0.55 0.7 2B 36" 45102-sn80 2,764 166,660 3.2 3.6 3.9 3 36" 45102-SR80 88,675 166,660 3.2 2.h - , 3A 2h" 33082-sR80 48,376 57,955 1.3 0.7 - 3B 36" h5102-sR80 8h,344 . 166,660 3.2 2.h - h 36" 45102-sn80 2,768 166,660 3.2 3.6 3.9 ha lo" 26062-sn80 2,048 25,413 0.6 0 55 07 5 36" h5102-sR80 88,675 166,660 3.2 2.h - SA 24" 33082-Sn80 48,376 57,955 1.3 0.7 - 6 36" h5102-sR80 122,133 166,660 3.2 1.8 - 6A 36" 45102-sn80 122,090 . 16'6,660 3.2 1.8 -
o'^ OA O G SEISMIC AND'IDCA STRESSES (psi)
- y Actuator ,
Bracket Bracket Valve Sten Dise Bolt Bolt Neck Pin Size Actuator Cale. Allow. Calc. Allow. Calc. Allow. Calc. Allow. Cale. Allow. Calc. Allow. 36" h5102-SR80 15013 bl250 h8900 49500* 5685 22605 6120 28875 32013 59730 30391 35838 2h" 33082-SR80 21987 41250 35065 h1250 6181 22605 6625 28875 33030 59730 29836 35838 10" 26062-SR80 18305 41250 332ho 41250 4713 22605 5667 28875 7988 59730 13653 35838 1
-l
- This allowable is' based on a bolt material of A354 Gr BD which is different than bolt material provided with the valve assemblies, A193 Gr BT. The allowable stress of A193 Gr BT is bl250 psi.
NOTE: The al3cvable stresses are based on 1.65 times the allowables given'in Section III of the ASME Boiler and Pressure Vessel Code.
~
-T-
- - . . - - . - - - ~ - - . - . . _ . . - . . ~ - . - . - - - - - -.c CC
_ CONCLUSIONS Based on ,the resulting stresses not exceeding allevable, if the bolt material for the 36" valve body / bracket ' bolt is changed to
'A35h Gr ED Posi-Seal concludes that the subject vr.lves will perform properly during a combined LOCA and seismic evsnt, provided they are installed with the flow resulting from a LCCA goind in the preferred dire'ction, and orientated as recc:::= ended.
It should be noted that the angular velocities of the subject valves shutting are sufficiently slow as to not cause over stressing when the actuator's scotch yoke impacts against its stops. This . conclusion is based on Posi-Seal's experience with bigger valves closing in a shorter period of time (e.g., h2"'vith Matryx Q( k5211-SR80 closing in 0.8 seconis). 4 S S e 1 s e e
-S-L
( . IOCA ANALYSIS The purpose of this analysis is to dete=ine what effects the aero-dynamic torque resulting from a LOCA vill have on a telve assembly. Since aerodynamic torque is dependent upon the flow conditions and the valve angle computer programs are developed which:< ,
- 1. Models the piping system .
- 2. Petermines the flow of various valve angles
- 3 Simulates the actuator as it strokes the valve from fully open to fully close Modeling the Pipirg Systen Forthesubjectordertherearesixpipinksyste=swhicharetobe investigated. They are: ,
Case 1 24" Valves IVQ001A&B Case 2 10" Valve IVQ005 and 36" Valves IVQOOhA&B-Case 3 24" Valve IVQ002 and 36" Valves IVQOOhA&B Case h 10" Valve lVQ005 and 36" Valve IVQ003 Case 5 24" Valve 1VQ002 and 36" Valve IVQ003 Case 6 36" Valve IVR001A&3
. Shown in Appendix A are sche:stics of the piping syste=s with each system broken down into the inditidual. cesponents with its corresponding resistance factor. These facters are inputted into the computer program either as a K value, as a length of pipe, a change in pipe dicmeter, or as a valve C y. The K values are obtained from Ecference ( b ), the C y values from Posi-Seal Technical Eulletin No. 2, Encl. ( 2.).
Q
.3_
~
O( - Thus, with the piping system modeled, and with the upstrea= and downstream conditions known, the flow conditions can be determined. Determination of Flow Conditions Derivation of equations Bernoulli's Equation . Zy+144Py+V1 2=Z2+1 P2*Y2 +h P1 ', 2g p2 2g
~
Since the flow investigated vill either be steam or air the height terms (Zy , Z 2) can be ignored. 144 P y +V y = 1M P2 + Y 2 (,,. Py 2g p 2g . 2 where P = Pressure PSIG
. p = Density lb/ft 3 V = Velocity ft/see g = Gravitational constant = 32.2 ft/sec 2
= Head Ioss Since the piping systems are relatively short the flow is assumed to be adiabatic.
P " per Ref. (b) 2 P1
-1
[ P,' 2\ 1/q .
- g. \
T 2
" Tl f P2 ' \ El-1 b
(Py ') . _ lo - .
O C where Ky = Ratic of specific heats P' = Pressure PSIA T . = Absolute temperature *R Flov equations In pipe ' 69h.3 P VD2 Q = T *
. where- Q = Flov SCFH 2
D = Diameter in In valve t Q = 1360 Cy Py Yg X per Encl. ( 2 ) 1 GTZ- .
~
Oc':, vaere cv = ve1ve coefficie=t X = AP/P , AP = Pressure drop across valve PSI . Y=1- X Kb F = Ratio of specific heat factors K X = Rated 'p ressure drop ratio factor - T
. G = Specific gravity 3 Z = Compressibi11ty factor
, For choke fic'i in valve
- Q y 907 1 C y P' y I
Fg XT Per Encl. (' 2 ) GTZ f AP choked = Fg Py
r Sonic Velocity Equation
~
i V 3
= 4637 Ky P per Ref. (b)
P Determination of the ficv conditions vill be perfomed as follows:
- 1. Calculate density at the end condition
= (P 8 -
. P N+1 N+1 py ,
P'y -
- 2. Calculate initial velocity ba. sed on beginning and end conditions.
. V(1) = P N+1
~
21b288g
\ N+1 P P/
1 1-fD y \ -K . k N+1) - ' (]3, where K = K(1) + K(2) + ... + K(N+1) Using the initial velocity V(1), calculate AP for all the stations 3. as shown belov For I = 1 to N p = p(I)
~
p(I+1) = p V(I+1) = D(I)2 V(I) p(I) D(I+1)2 p(1,y) P(I) = P(I) - 14.7 P(I+1) = p(I+1) P(I) + V(I)2 (1 _ g(1) ,y(7,y)2
~
p(I) 9274 9274 - ! P(I) = P(I) + 14.7 P(I+1) = P(I+1) + 14.7
'p(I+1)=p(I)[P(I+1)\1/Yg ,
( P(I) J If p(I+1) - pl > .0005 then p = p .0005 l end recalculate P(I+1) ' l Note: This is done cince p(I+1) is a function of ('- P(I+1) and vice versa. M T(I+1) = T(I) . {P(I+1) (K1 _1)/g1
- P(l) t t
For determining the AP across the valves, the equation for Q - given on the preceding page is used. Solving for AP from this equation results in a cubic equation with the c=allest root
. being equal to the actual drop across the valve.
. 4. .With the final pressure P(N+1) calculated, this pressure is co= pared to the final presskire Given. For this particular study the final pressure is atmospheric. i If the calculate pressure is less than the given final pressure then the initial velocity is decreased and Step 3 is repeated. The init,ial velocity is increased if the calculated final pressure is greater than the given final pressure.
5 Steps 3 and 4 are repeated until the calculated final pressure - approximately equals the given final pressure. .
- 6. If sonic velocity is encountered at any of-the ' stations the initial velocity is decreased until Step 5 is achieved or until the calculated sonic velocity approximately equals the actual sonic velocity.
If the latter is the case then the given final pressure is assumed and the pressures at the stations between the outlet and the station at which sonic flow occurs are determined by using the equation given in Step 3 in reverse order and using the flow, Q, .
. based on the sonic veloci.ty.
7 If choke flow is encountered in any of the valves then the same approach is taken as given in Step 6.
- 8. To de'termine the flow conditions for the various valve angles, the C yof the valve closing is determined for the angle of interest and Steps 1 thru 7 are repeated.
The above is formulated into the cc:nputer progrn= "FLOWGAS." h . L
m U Simulation of the Actuator Strokine the Valve Close C . In order to simulate the closing of the valve, an equation which describes the torques acting on the valve stem has to be defined. This , equation is given below: TI'O = Tfygy + Tair + Tspring + Tpacking and seal + inertia + T be ri'ns Where Tg = The net terque tending to open the valve (equals zero when the valve starts to close). T fyny = The torque due to aerodynamic ficv caused by the LOCA.
. T = The torque exert by the actur. tor as a result of air the air acting on the actuator piston tending to open the valve. .
.. Tspring = The torque exerted by the actuator spring tending m
to close the valve. Tpacking & seal = Torque of the packing and the seal resisting the closing motion of the valve. The seal torque does not take affect until the disc begins 'to seal which occurs at approximately 3 frem fully closed. The running torque of the packing is approximately .6 times the break away torque. T = Torque due to the inertia of the disc assembly. inertia Tbearing = Torque due to the AP acting across the valve which forces the stem / disc assembly into the bearings.
'O
- 114-
Derivation of Torque Ecuations Q( - Aerodynamic Torque (Tfgy) Since Posi-Seal has only determined hydrodynanic torques for water based on testing, see Encl. ( 3 ), a way to determining aerodynamic torques for air and steam from those for water has to be derived.
- The resultant drag and lift forces acting on the disc are as follows:
F D
= Cp pV 2A Resultant Drag Force 2
2 pV A F = C Resultant Lift Force L 3 2 The resultant torque is 'the resultant force times the length from p of _ s, tem to the location of the resultant force.
,?, TD=Cp Lp pV A ,
Resultant Drag Torque T =C 3 gL pV A Resultant Lift Torque L , 2 D ,L " D,L b ,L P ^ 2 Where V = Velocity A = Surface Area p = Density of Fluid C,C D 3
= Drag and Lift Coefficients (Dependent upon shape and orientation of disc)
] L'L D L
= Length g stem to resultant lift and drag forces D',L = Combined Subscript v
~
15 .
O s NOTE: Cp and g nr.e the scme for the same size and class valve, asstuning the sa:e angular position, regardless of fluid, flow, media or temperature. T fluid p fluid V fluid
"" '# y 2
, p water V vater 2
Thu YF T = pp , 37 2 62.4 Vy Where W = Water .
. F= Fluid
- p water = 62.4 lbs/ft 3 V
F
= Calculated in the deter =ination of the flov ,
.. conditions n,- .
Vy =
.00223 3 = .00223 Cy %(J A g
7 . Tgy = Disc Hydrodynamic Torque per PSI AP (function of valve angle) T = Disc Aerodynamic Torque per PSI AP 4F
. The total aerodynemic torque equals Ty = T gy AP Values for Cyand Tgy can te found in Enclosures ( 2 ) and ( h )
respectively for various valve angles.
* ~ ' ' ' , --,e .-e- - - - .,, 4 _
Pneur.atic Torque (Tair) ( Tair = A C2 R P1 Where A = Area of piston
=T running . Trunning " 6 #E"'
R actuator P = Working Pressure of Actuator
. .R = Radius of ' Scotch yoke (See Figuid'3)
P1 = Pressure of the air in the piston cylinder ,
= P1 ( V- AV) P1 m Previous pressure
.. V = Specific Volume AV = Change.in Volu=e . ,
= dt
- Q dt = Change in Tine 3600 c.
Q = Flow thru solenoid valve or quick exhaust
= 963 Cy , 733 P1 1.25 (F 3)2 ,
GT
.. C,=C y y of scienoid valve or quick exhaust F33 = Rated liquid pressure recovery factor of a solenoid valve or quick exhaust = .9 G = Specific Gravity of Air = 1
' T = Tenperature
- Rankine = Assune equals 530
\ l Q = 33.62 Cy P1 C2 = Equation describing the adycntage of the Scotch yoke
. as a function of angle.
4 0 8 . _ . . . _ _ _ _ _ -
. s Y
E' f "1V' 8t** f Spring V / B t t L ! Air Supply . : , N. .
& E::haust e 9 s [ > l <
Fiston Scotch Yoke Figure 2 Forces acting on Sco'tch Yoke Fin IV - [IB o H , r
~ O -- .
..- Fg Figure 3 de Su=ning forces in the horizontal direction FH - cos 6 FR- [ sin 9FR=0 FR=FH (cos9+psin0) FR = Resultant Force Fg = Horizontal Force I Tg=Fy E =F g B = Bes t ant To nue cos & T T
.- 3= '
cos 6 (cos & t g sin 9) M ' C2 = cos 0 (cos e + p sin 6) %) q Spring Torque (Tsering) spring = Figure k 1.klk R 0 e 0 = 45* R bX = 2B
*FE {
B ,.
. e AX ,-
K = Springrate
=g AF = Tstrine beginning - Tstrine encing ..
, 1.414 (1.414)R AX T =T breakavref. - Tspring ending spring beginning K = "*bre @ avav -2T string ending ,
E kR
,. X2 = Xy + R (1 + tan 0) b "istring endine C2 @ 0 = 45 Ka I l= .571 Tsprine ending KR ,
I X2 = .571 Tsprine ending + R (1 + tan 0) F3 . e _ Bearing Toreue (oben-ine) 2 - bearing = F # P D d where /' = Coefficient of friction O = .059 fer trenze bearings l h'- D = Disc gage dianeter d = Sten dianeter l _ . _ _ _ .
4 O Inertia Torque = I< ( - C2 I = Inertia of Disc A= Angular acceleration
=
W dt , W= Angular velocity 1 ,
= _AB dt 60 = Change in angle old ~ new 0 -1 y .
"" = tan ,
B , AX X = Xold q . i AX = 2R AV .68V
-'{
.68 = Percent of total colune over which the actuator vill stroke.
The torque equations are for=ulated into the conputer program
" FLOW-CL". As p' art of this progra=, the closing times and the angular velocities of the disc assembly are calculated.
e o e D i 20 -
, 5
. f ;,X 9, y .
- ~
O _ . m -
- g
" z
~
- p Y Y .
2 X _
- =
- h g j '-
l z Y gK L
.. E D
S S
- A
.h E r V o L 5 t A a V e u
bT: F r t c O u g A L i E F D O M c L _ ~ s i s . wo A R
. n D c ,
O i T P - C I e P t s i s x - lo D B y d o B 1 _ X p Y -
~ .
; Y
.//-
L f,
.' /
f/ .
/
\
O' r o m e . t t ass i ut tl co _. AD x I
?
SEISMIC E00ATIONS d. A. NATURAL FRE0VENCIES:
, LATERAL - Disc / Stem (By Rayleigh's Method) Ref. (c)
The natural frequency is calculated for the worse case, that being the valve open where the disc is not supported by the seat. (- , 3 1 1 f' D D
- + 0 v ,
x 707 D t 1 f , I
" t 2 W ' ----d 4 k N
C= 3.125 1 3: NATURAL FREQUENCY Per Ref. (b)' : 1 Y , 8 kI. W iY
.Y *
/
$ ~
y 5
~ ,
- ~ - - " -
3 2 3 2 W 4 D M D W 4 D W 4 L) ,L2 D - 2 2 2 3 y ,
, , __ _ Deflection of D
3 EI D EI 4 6 EI D D. D 2 '. W4 D 2 M D W 4 D W 4 L) ,L2 D 2 2 2 3 Slope at end gD, _ , of Disc 2 EI D
- EI 16 EI D
. D D
-3 -
+
-3 '
W 4 L)- ,L2 N 4 1 '2 g 2 3 , 3 Deflection of Stem
'b 3 EI S 6 E1 3
O( .
~
~
3 - 2 2 3 W4 [D - y +hD y+ gD L y+ g L L 2 2 l+
.=
+
2
+ +2 +3 E 48 I 16 I D 16 I D 4I D 6I g D
[]t 3" W4 D 3 gy+h D 2 g+g 2 D p+2 L
+ + +
y, , E 48 % 8% . 45 SI s _ I S= N'4 1 Mcnent of Inertia of Sten ( in 4)
- 5-
. 64 .
2 4 2 _ 2 707 DE -
.707 DE ~E Y' TT E ff E Y _? ., 2 + 2 2 - + 1 + 1 _2 _ Mrent of 'D 12 ,_ 2 _ 64 4 Inertia of Dit 4
(In) 2 2 3535 DE 2 + .7854 E1y 2
- , Distanct to Neutral Axis (in) .-
. 2
.707 DE 2
+ .7854 E 1 - -
;. . . ~
1FERE: W = DISC WEIG?T (LBS.) 4 D ' j 1 = STEM DIA. (IN.) D = DISC GAGE DIA. (IN.) Ly = mwnVE BRG. LENGIH (D7.) See Page h6' for egaation L TdRUST IGSEER TdICKSESS (IN.) . 2 E = WIIrni SmLL DIA. FICT OF DISC (IN.) E2= WIDI I I .RGE DIA. OF DISC (7N.) Y2 = DIST. ( STDi T FPJ7T EACE OF DISC (Hi.) e' O CL
VAINE NECK AND FLANGE DIENSIONS m
. .) g 1 .
M 1 7 "N -
~ ~- ..
~
@. . ^7
' s _1) e e r- -1 u- -
e su ,r ..
^8 i T x 3'
\ /
%, 2 6 6
.e @ r e
P i - h { ~
.l l . .l(. ,.. LB5 d' N, 5i i -
X'5 x5 R
', R-6-
+ Do - r! .
D , i.T - r8 a ,-- I. N 's / - N
\
\
) \ l , .
J e
\
\\
\ , /
/ x '
m Q J
/ Yi;;= c f>.
. Lk
9 O' . ACTUATOR MOUNTING BRACKET DIMENSIONS e S O _ T ' 5 O di 4 T0 v : X 4 ise
._a 1'
+ +T 9
4
/ T2 1 >
f O I , 1 l Figure 7 ' i I i O
-- ,- , - --,--e--, -. - -, -. -, - , * - - - -----------.,,,,,,-7,e -- - - - - - - . - - - , . , - c- ,--- ., .-,--- -- - - - , - - -
(*'
,,, ) LONGITUDINAL (Z)' NATURAL FREQUENCY c, .
DETERMINAh10N OF LONGITUDINAL SPRINGRATE Springrate of the Neck Springrate of the neck due to the shear in the Z ' direction
.. F.,~
~ Fz a Y ,
+l , Y =
1 ,l h_ Y 1
, e j %
F.;
,r x
~
ww m'
/ wm wm '.. F3 -
gg
= 2 Yp=F 3 1" Y3=M1 2 cl 3 F,I .
x , X i 2 pM,gy GF=F z 1 2 El.. s.
" #x
- 2 '
Y=Yp+Yg Y=F 1'+M1 _ 2 r,2 3 c.,A x x
,~., .
'ef
\,
O " Gy+ 0 ,h G=F12+M1 =0 2 EI px x M=-F a 1 2
- - ~ - ~ - - - - - - - -
m- m. .-
, ,. 26 - _ _ _ _ _
ns LONGITUDINAL SPRINGRATE OF NECK V
- Y=F 3 p 3 y,p 3 3 1 _ z 1 z 1 T2 EI x
, 3 EI x 4 EI x -
K=Fz 12,EI x . Y ,3
, Circular Cross Section Rectangular Cross Section
.I x =
. .y_ (D o -
- 5) I x
= T 3 Ta 3
_ y" 35
- 64 la With Gussets o
'I x =Ix + (L - D O)T" ,,
12
- c - .
(' For the Neck 1=X ' 5 ENF, = 12 EI x
~
3 5 Springrate of the neck due to the moment about the x - axis
,- F -Y T ~~
^
/. ~,.
c
\r . 6 X
., ,3 8s -
i xy Y g' 6) ,f X 3 s ;;
/ x 5
Q /'? -,- 4
/
mw~>- /
LONGITUDINAL SPRINGRATE OF NECK m V ( YT"XS+OS(3+X) 4 Y3=Yp+Y3 G3=Op+GM Yp=F X ' X M=MX 2 gm p** 5
. 3 3 E1 x c ~ IX3+X) 4 2 El x
Eg=F (X3 + Xa) X5 2 EI
, x Gp =,, F 3 X 5 O F (X3+X4 ) = F 3 (X3+X)X5 4
,, 2 E1 x 2 EI, G
=MX5=Fg (X3 + Xy) X5 ,
EI x EI x , G (X M 3+X)"F 4 z CX3+X) 4 5
'~ ( EI x
~
X 3 7 YT=F3 5+3(X3+X)X5 4 + 3(X3 + Xa )2 5 3 EI x K=F 3 v . T K 3 EI-gg* = X 5 T 3CX3 + X4)X5 + 3CX3+X) 4 5 . K N *X K NM X
-NF Z K
NF "b XNM x . 4 M
. 28 _
LONGITUDINAL SPRINGRATE OF BRACET Springrate of Bracket - ( . Sprin5 rate due to twisting of the bottom plates of bracket per Seely and Smith, Page 271, Ref. (d).
'~ ~
1 g, 1 T where B = .333 = 3 for b >> h . U B b Y13, G = Shear. Modulus
~
Looking at one side of bracket .
- Assume the width of the bracket that resists the twist of the plat'5 is the average of the j valve neck width and distance X between bolts 3 4
Q '
~
/,b = T4 + Xg h y 4
2
---- N
'"(
'i N .
G = 12X10 6 h=T y T=4=F %-Ty + Xp , 2 f= 3 3 F., (X4-T1+X) 3 - F., (X4-T1 + X,) 3 ( 4+Xg) T1 6 6 _ 2 (12 X 10 ) _ (T4 + Xg) 4 X 10 0=fd where d is assumed'to be = T5 - 2Tg - (T3+X) . .. 7 2 D 2 - k' 8 X 10 6 7 3 (T4 + Xg) 1
.e.w+,. . ,e --go -...e.. w. - w = e.w e - * .e-
. e e. . . e .-m, -
LONGITUDINAL SPRINGRATE OF BRACKET Y = 0 (X4-Ty+X) . 3 Tan G = G for small angles Y=F (X4-Ty+X) C 5 - 2Tg - (T3+X7 3 3 2 (T4 + x8) 8 X 10 6 Ty 3 - , 8 X 10 6' E 3
=
(T4 + Xg)' , T y BBM* 2 (x4-T1+XI 3 (T5 - 2Tg.- (T3+XM 7
. 2 7 The total springrate for the bottom of the bracket is K
BBM = (T4 + Xg) T1 3 16 X 10 6 . X (X4-T1+X) 3 (T5 - 2Tg - (T3+X7 , ((
~
for a valve with a fla'nged neck b = B +'Xg 2 - g , ('lB + x8) T1 3' 32 X 106
. BBM x ~
(X4-Ty + X3 )2 (Tg - 2Tg-( +X 7 Springrate due to the twisting of the top plate of the bracket b=X 6 DBC of Actuator 6 K BTM ". X6 To 32 X 10 , X X 3 ( 5 - 2Tg-X) 6 n k,.(
'30 -
O LONGITUDINAL SPRINGRATE OF BRACKET O, . t E BM "E BBM E BTM x x 7 E BBM +E BTM x x Springrate of the bracket due to the, shear in the Z direction
. Per Fage 27 - KShear = 12 EIx 33 K -
Ix .= (2) Tg Tp3 x
- BF* = 12 EI X4-Ty-TO '
T2 3 KBF,, = 12 E Tg 6 (Xq -Ty -TO) ~ n(- g ; .
= 60 X 10 6 T g K T2 '
/
BF - z (Xq-Ty-T) O I Springrate of the bracket due to the bending of the side plates YT"YS+OS (X3+T) g Y3=Yp+Yg G s *OF+OM Yp=F z (Xa - TO - T1)3 3 EI x , Y 3-gs. l
~
O E3+To Yg = M '(Xa - TO - 71 )2 g , _, 2 EI X <
~Z x
- n M = F,.- (X., + T O
4 0-Il L( 3 w I 31 -
LONGITUDINAL SPRINGRATE OF BRACKET
-0
( Yg=F z (X3 + OT') (Xa - To-T) 2 EI x 1 Op=F 3 (X4-TO - T 1)2
- 2 EI -
Op (X 3 + TO) =.F 3 (X+T) 3 O (E4-To-T) 1 2 EI x ,
,OM = M(Xa-T O-T)=F y z (X3+T) O (Xa - TO-Tf y El EI x Og (X 3+T)=F O 3 (X 3 + Tg )2 (E4-To-T) 1 El , , YT=F z (Xa -TO -Ty )3 + (Xy-T o-T 1)2 (x +T 3 g) + (Xa-T o-T 1)(X 3+Tg )
3 EI x .EI x EI x - 3.{
. K 0U x ggy* = y F, = (X -T -T )3 + 3(X a-T o-T )2(x 1
+T O) + 3(Xa-T o-T 1)(X 3+To )'
, 4 o 1 3 I
x = (2)T g Tp 3=T g T23 12 6 K BS g "E BF E BSM x EBF ,+ KBSMy , K " E B 3 BM, E BS EBMx + EBS g K., = KB z E
~
N: B+EN; 1 l _ 32 - 1
LONGITUDINAL (Z) NATURAL FREQUENCY O - M=W1+W2 , 366 Where W = Weight of Actuator W = Weight of Bracket 2 ,
~
fn. '
=' 1 I
K, Hz 2T [ . e e 9
/'*
e 6 1 6 i -
. 6 4
0 e O G e ep 33 .
.-.---,,mr. .- _ - , _ _ . - , - - ,.--,-,ee..,m,, . - . , . . . - - , _ . . - . - . - , , . - , , -
, - - - . - - - - - - - , - , , y ,. ,-.. -- -.. - . - , - ~ . -
VERTICAL (Y) NATURAL FREQUENCY DETERMINATION OF VERTICAL SPRINGRATE- . Springrate of Neck Stretch of Valve ' Neck . K NFy
=
7 E
. A =T tf (D035) Circular Section 2
K NF = A=T 3 T4 tr B5 Rectangular Sectier. y
., = A + (L - D O) T Springrate of Bracket -
Sprin5 rate of Bottom Plate y,A
-Y = F 1 3 '
for fixed fixed 12EI per PaSe 27 e P For one side
~
l-1=T5 -2Tg - (T3+X) 7 2 . 2 l . .
. % 9 I =T T1 3 ,
z 2
.12 4
3h - 2
VERTICAL SPRINGRATE OF BRACKET O( K BF y = 12 EI z = 12 (30x106 ) T p T13 13 12 (T5 -2 Tg-(T 3+X7h 2 2 K BBF
=T 2 T1 3 2.4 1 108 (T5 - 2Tg - (T3+X))3 2 7 ,
~~For Both Sides For Flanged Neck K =T 2 T y 3 4.8 X 10 8 T2 Ty 3 L8 x d BBF -
(T5 -2 Tg - (T3+X) 7 3 5 - 2Tg-(gtXy3 7 , i 2 .-
?
Sprin5 rate of Top Plate ,
~
.8 X 10 0 i
K BTF =T 2 T O . I y ' l (T5 - 2Tg-X) 6 l .
~
Springrate of Side Plates . A=2T Tg K 3p y
= AE T
1=X4-TO-T1 2 6 KBSF. = Tp T g 60 X iO Y Xq-TO-T1 .
.O C. .
1 1 - . [ .
VERTICAL NATURAL FREQUENCY b( . I KB "E BBF EBTF K BSF y , y y y A A E BBF ABTFy+ ABBFy B S?y + ABTF y BSF y y Ey '- "E NF y EB y ,
~
E NF
+A B
_ y y e fn = 1 K 7 Tii l Hz
, y2 - ~ .k( -
e % e e 9 e m 4 4 4 e O 36 -
TRANSVERSE (X) NATURAL FREQUENCY O . C- DETERMINATION OF TRANSVERSE SPRINGRATE Springrate of Neck Springrate of the neck due to the' shsar in the X direction
.Kyp x
= 12 EI g Ig =T T4 (D0'4 -B5) circular 5 I =T z a T 3 -1T B5M Rectangular 3 g
. 12
+ 2(L - DO)T(L + DO)
- Ig =I 3 + T(L-DO)3 6 4 with Gb5 set
(' ~ s
.~.'(.
Springrate of the neck due to the moment about the Z - Axis K 3 EI g NM* = X ' 5 + 3 (X3+X)X5 + 3 (X3+X) 4 4 *5
.Kp =K NF X NM Z X X A
NF +E NM x I e 4 O
TRANSVERSE SPRINGRAT.E OF BRACKET O . SPRINGRATE OF BRACKET { . Springrate due to the moment about the Z - axis acting on the bottom plate at the bracket Y=O p (X4 -TyfX3 ) F -
.F = M2 = Fx(X4-T y+X3)
- op T -Tg 5 ,
F=F x (X 4-T y+X3) T -T
. 5 9 F . .
M., ,
, f ,
.m p . _
~
[ D'- Op=F12=F lT5 - 2Tg - (T3 + X7 )) /2 2 El 2 EI Z - Op=Fx (X4-T1+X) 3 T5 - 2Tg - (T3+Xh 7 2EI g (T5-T) g Y=Fx (X4-Ty+X) 3 Ii5 - 2T9 - (T3+X3 7 8 EI g (T5-T) g K 8 EI.z (T 5 - T g) y ,7 3 T l z 1 2 BBM* = (X4 ~- Ty+X) 3 I 5.- 2Tg - (T3 + ~X7 g - 12 l l l 4 ss( 1
~
_ 38 _ 1
. - . - ~ . _ .--g- % , .,,,3
TRANSVERSE SPRINGRATE OF BRACKET
'(~ .
20 X 10 6 T T) 2 Ty 3 (T5 3
~
E " BBM g (X4-Ty+X) 3 (T5 - 2Tg - (T3+EU 7 2 For a va'1ve with a flanged neck , 6
'- K = 20 X 10 T T (T 5-BBM z
2 9) 2 (X4 -Ty+X3)2 (T5 -2Tg -(g + X7 ) Springrate due to the moment about the Z - axis acting on the top plate of the bracket . 6 K BTM = 20 X 10 Tp T O (T5-T) g {,( X 3 (T5 -2Tg-X) 6 . E Blig "E BBM g K BTM 3 _
~
K BBM g +EBTM g
'Springrate of the bracket due to the shear in the X - direction 3 T *
, K BF "E BF exespt Ig =T g 2 .
x 2 6 i K = 60 X 10 Tp T g 3 BF X (X4-T1-T) O , 6
TRANSVkRSE SPRINGRATE OF BRACKET O. . Springrate of the bracket due to the bending of the side plates. K BSMz EB$M except Iz E T g 3 T2 + 2Tg T2 (T5 - Tg)2 x . 6 2
'g 3 EI z
. BSM* ,
(X4 -TO -T1)43R a-T o-T )2(7 1 +T 3 )+ O 3(Xa-T o-T 1)(X 3+T g)2 E "E BF E BS BSM g x , KBFx+ EBSM g ' ,,( .l '~ ~ K "E BM E B BS - - x g x , EBMg + EBS x Ky =K B E ' x N, . KB+EN y 7 fn* = WC1 K j Hz o
- 1;o -
- 1. ACTUATOR / BRACKET BOLTING.
OPERATING STRESSES - S = 1.414T SOX NAX WHERE: T= VALVE TCRQUE (Packing +Bearii16 + Aerodynamic) (in I.35) 1 6 N.= NO. OF ACTUATOR 50LTS 1 ' 2 A1= TENSILE STRESS AREA OF ACTUATOR BOLTS (IN ) S =S soZ sox X=D CF ACTUATOR BOLTS (IN.) 6 BC SEISMIC STRESSES - , G = Transverse Scismic Acceleration A. VERTICAL DIRECTION (Fy) G = Vertical Seismic Acceleratics
. G = Longitudinal Seistic Acceleration 3
Fy= W[
- G2 M "'
Z '1 X 2 l
= A tuator Weight
. 'W Bracket Weight 2
4 MAXII.u! E LT LOAD (LBS.)
- F '= (1 + COS N'fP') "X X 3X N
, , 61 1 ,, Per Ref (e)
F= Z 4 (1 + CoSN * ::) M Z 61 ,,_ F= Fy +F +F (LSS) TOTAL TENSILE LOAD ON BOLT T X Z
. Ny . .
8 Ty"
',[ ' ,( T (PSI) TENSILE STRESS ,
Ay ,
~B . TRANSVERSE DIRECTION (F ) .
" 'U X "1 1 X2 H=FX g 3 Sg 1.414Tv '+ Fx (PSI) SHEAR STRESS NAX yy6 NA ll -
F RZ
= 4 (1 + C E) M MAXIMUM DOLT LOAD (L3S.)
3X N 61 "1 ' t 8 TZ RZ (PSI) TENSILE STRESS A l . C. LONOITUDINAL DIFICTION (F ) - - F= z W
- G F=F1 M Pg X3 1 3 3 1.414Ty + F -
Z
, SSZ = N A X
~ t, 116 NA yy i
l s- F RX
= 4 (1 + C OS N ) M X
MAXIMUM BO!.T ICAD (LDS.) y 3X N 61 _. F TENSILE STFISS S TX .g_
= RX (PSI)
....s~~....
S - SS / (ssox + S ssx}2 + (ssoz +sssz)2 ! g , 2 g 2,g 2 (PSI) TENSILE TS Ty TZ TX D MAXIMUM STP.ESS: MAX . b'at-SS THEORY TS TS g 2 g,2 T ,,, 7. ,, SS
- 2. BRACKET OPERATING STRESSES S=g F=T/T 5- ""
4 5 I=TT, g2 c= T 'X 4 2
, 12 2 h~ I
~
S=6X T > b B 4 . TENSILE (PSI) I -
- T.5 s*s5'2 I
~
~ 1 J.
' S3 =2 .T= T T
^
^ 2 !
. 4 { T 3 < 2 S= T SHEAR (PSI)
T T T I
,. g 2 5 ,. .p a SEISMIC STRESSES - . .( , A. VERTICAL DIRECTION (Py) F Fy= (W + . 5W ) G M" Z
2 2 l X 2 . .
+ X2 TENSILE (PSI)
S = Fy Z5+ 2T T 2J 2J
, 2 3 2 _
.~ ~
3-' 3 J =2 2 92 J=2 3 29 + TTg2 ( 5/2 ~ 9/2 _12 ,12 - B. TRANSVERSE DIRECTION (F ) F= (W + . 5W 2) G 1 Ty=F X 2 M F y_ ( X Z
+X)4
~
S = Ty +F- SIE7a (PSI) SX X 9 2 5 TTg2
+
TZ" 4 Z 5 TENSILE (PSI) TTT2 gg S92 3 C. LONGITUDINAL DIRECTION (F ) F=N-t g .W ) 2 G W=FZ1 X , l 3 gX, ,Z J SZ" ,,
+ F,, SFE7a (PSI) 1 '2'S .T9 T2 S = 6X Ty + MT TX 4 2 2
b .h [? . f3. _ _ ~ h2 _~ _ . _
ROOT SUM SQUARE STRESSED
- 2 S = S + S g3
+S SHEAR (PSI)
SS S S S = S + S TZ 2 L TS Ty +S g + S B MSM (PSI) l MAXIMUM STFISS: MAX. INS THEORY ('
+ +
S, SS l
. 2 ._
- 3. ERACKET/ VALVE BOLTING OPERATING STPISSES -
2X T - SOX " N, ., Xg bsoz " 7 NgX2 g "WHERE" T= VALVE TORQUE (IN-LBS) H= NO. OF BRACKET BOLTS = 4 '
, _ _ , _ X 2 7 A= TENSILE STRESS AREA OF BOLTS (IN.)
2 Os
. 9= X +X #;
7 8 9 ~
- X Xg
=
EQUIVALDIT BOLT DIA. (IN.) SEISMIC STRESSES - p o A. VERTICAL DIFICTION (Fy) V
.. Fy= (My + W2 }
- OI "Z-FyX y M=M x 2 z ,
F TOTALTENSILELbADON ' . k.2' RX "X F = Z F= - F F RZ 2X 2X N BOLT (LES.) - 8 7 2 Ty= T TENSILE (PSI) A
. 2 B. TRANSVERSE DIRECTION (F )
F=y (W +W) 2
*Gy Ty= F X X2 M F Z
(X 3 4 . S r g D+F X SHEAR (PSI) S E "2^2'*h n 22 A P = Z S = RZ TENSILE (PSI) ' RZ 2X A 9 2 C. LONGITUDINAL DIRECTION (F ) ,. F= Z M l +W)4 7 3- &FX g3 glF(X X Z 3 A X)4 c u - 7 + F r-
'5 S Z N.s,A ,Xg2 p n. ,
g, F = X S = EX TENSILE (PSI)
~
2X A 8 2 43 -
l ROOT SUM SQUARE STRESSES: ( (sssy.+sy)2 + S SS (sssz + ssoz) 2 O S,S
/S,2+S 2+STx c T Tz
' MAXIMUM STRESS: MAX.sTEss THEORY
'T * 'SS
- 4. VALVE NECx - .
~
OPERATING STRESSES - S= C SHEAR J 1 J= 8( !)2 ( !) 2 - 8(
! 2 + R6) ( !)
3
!2 + 1. 8 ! 2
- 3 3(R5/2 + R6) +
.. + g(D/2 ) ( !) 2 -
T Di
'3( 2) + 1.8 2 D r iT 4 OR g 4 4 '
X J= 7 (6 3 - Di ) 32 , R5 - R6 - I DIST. TO MAX. FIBER STRESS-
#'(
I*I C= T4 2 - - - -' 4 + Di2 OR P 3 + Di2 HOOP (PSI) ' P T 2 - D12 d 2 - M2 - 3 _4 - .. SEISMIC STRESSES - A. VERTICAL DIRECTION (Fy) . Weight f valve neck (LES) Fy= (Wy + W2 + "3I*U2 "z" Y*1 "X" Y*2 "3= , A= (T3 - 2RS 4 ~ g g +g 7+ 2 TENSILE (PSI) OR A= . W (d32 - 2) (in ) 4 2 (T3 ,_2 R)T4 3 - ;7 31 4OR TV (d,4 - Di ) 12 64 64 3
~ ^ ~ ~
J" ~ 2 2 3 3 12 64 64 12 B. TRANSVERSE DIRECTION (F ) . F = (W + W2 + N3)*G1 Ty FX +X)g M=F Z XM3+X4 SX r. SHEAR (PSI) 2J A S ,
"[3 TENSILE (P.GI) 2J, ,,
C. LOMGkTUDINAL DIRECTION (F ) , F= " + z W1+W 2+3 3 Zl "X -Z 3 '- 4 5' ( S = TyT4 +F SHEAR (PSI) . g fl A S = pat 4 TENSILE (PSI) 2J 2 ROOT SUM SQUARE STRESSES: , S = [Sg 2 +*S gg +S g SN,M 3
- S = S 2+S +
TS TZ TX P t .
, PAXIMUM' STRESS: MAX. STP2SSTHEORY b
.. S= TS + T +S 2 s'
..T 2 2 5S '
l e: , 6
\
Valve with Gussets y -[-
~ s ,
E e
' , ~J=J + 8 (L/2) (T/2) - 8 (d3/2) (T-/2) ,
.v
'( 3 (L/2) +1.8 (T/2) 3(d3/2) + 1.8(T/2)
C= 'd . 3 , 2 ' J 2 J2+ (L ~ d 3 ' 12 Y, - d + 2(L~d) 3 T T, + d J=J3+T 3 3 3 ~
. 2 .J 4 6
A= A+ (L - d )T W= A
- X5 * .283 3 3 S Fy + M: L '+ Mx d ,
A 2J 3 ZJ 2
~
SX 3+Fx ST = M: L
. 2J A 2J 1 3 SZ" 3+ _ ST = Mxd 3 .
1 2J r3 U 45 -
5 VALVE STE4: bh OPERATING STFISSES - (' ' Sg= 16T S D 3 SHEAR (PSI) 1 2 F = ] P, = 1T PD 3 APPLIED IDRCE ON DISC (LES.) A 8 TE EFFECTIVE BEARING LEiGTH IS DERIVED 'AS FOLLOWS: S =F WHERE A = PROJECTED BEARING AREA 7 I =L y D1 = EFFECTIVE BEARDIG LEiGTE TIES THE STE! DIAMETER. . S= F I hDy SINCE TEE LOAD IS ASSUMED TO BE TRIANGULAR, EALF OF TE YIELD . STRDIGTH (OR 15000 psi) IS USED. - F r- s , . 7 _.\ ). - N . N S N . _2 - - ;- --
-s -- -- - ,
N 2 i . n &l aL 1 . I. L1 THEREFORE, L=y F 15000 D1 AS CAN SE SEET IN TEE FIGUFI A30VE, IT IS ASSUMED THE FISULTANT BEARING F2 ACTION OCCURS AT 1L /3. . 2 (=D3 . hPD 1 1+[2 J BENDING DUE TO PRESSURE (PSI) l WHERE L1 + L2 MUALS LDiGTH OF STE! FROM TE _3 END OF DISC TO THE BFJ3ING FIACTION. . f^ \.k ' , , h6 _ _m _ _ _ . _ n. u . .. - - - - ,..-..m.-. . . .. e m,e ,
SEISMIC STRESSES - O*f - ~ .I p~ 2 M= H.L Whg + ( , 2 3 2 6* Yh
- E z
~
Sl= 32M = 16 whc p_ + L2 BENDING (PSI) b TD31 'TrD13 3 Gbs "'0b+O1* b . MAXIMUM STRESS: . MAX. STRESS TEMRY *
~g 2
'Sbs +i Sbs + Ss t* 2 _2, .
.6. VALVE DISC PIN: (No. SEISMIC STRESSES)
~
S3 = 2(%/Ico)T ShE R STRESS (PSI) ' DyAs . ( ' .L . . T = Torque due to seal torque and hydro- - static torque.
, . +1-.
f-T V'-^,/ b: L - r ~ c/ d
,- D, -
. .~
s 0 - 98 1 is ll lI I; j CT U lj V, %/y f,*cf 7, , S o I
- h7 -
I
~
2 As= .7854 cdp SHEAR AREA (IN ) , a= .01745 D yG ARC. LENGTH (m.) e= sm~1(f) - ( 1 2 1= dp(5) - 2 4 C. ,VMNE AND PIPING SECTION MODULUS: 4 3 Ev= g (d y -R 7
- 4) SECTION MODULUS OF VALVE (IN )
32d 1 .
^4 4 3 29= 'W (R g ~R SE C ION MOD M S OF M AC M P1PE G (m )
9 32 Pa *
. Zv > 1.12p WHERE: d = VALVE BODY O.D.
1 (IN.) R = VALVE BODY WATERWAY DIA. (IN.)
. 7 R **
- 8 .
R = I.D. OF WAN PIPEG (m.) 9 , D. DEFLECTIONS: W WHERE: W= WEIGHT,, OF ACTUATOR + 1/2 WEIGHT OF X,Y,2=(9,x,y,: BRACEET (LBS.)
-{'
y g= G' LOAD = [x2 + gy2 + g22
. K= SPRINGRATE (LATERAL OR VERTICAL) LBS/IN E. VALVE BODY BOLTING: .
+ 3 MAXIMUM BOLT LOAD (LBS)
F= 3X N '4 O3 % 3 _ S= F TENSILE STRESS (PSI) A4 ,e WHERE: M = MAXIMUM PIPING MOME!;T (IN-LBS)
. N3 = W. OF BOM BOM ,
X=D .DC OF BODY BOLTS (IN) 0 A .= ROOT AREA OF BODY LOLTS (IN ) . p NOTE: NOT APPLICA3LE IF 2CDY IE WAFER STYLE OR IF SSCTICN MbULUS AND Q ALICWABLE MATERIAL STRENGTH OF VALVE EXCEEDS THAT OF ADJACENT PIPING. PIPING l'.AT'L 7.SSU:GD SAICS GR.B 5 ALLOW = 15,000
. h3 w p.
_gpe e ** , . = = * - em= we e e-+
- ee a=**
==e o e
- eo . we . += _
x . DETAILED ANALYSIS Per Reference ( f ) upon a LOCA the containment and dryvell vill be pressurized to 9 and 30 psi above atmospheric, respectively. The media flowing throu6h these valves is steam / air at 100% R.H. and 330 F. To perform the analyses the media is first assuced to be super
- beated steam with its density obtained from Reference ( 8 ), based on the corresponding pressure and temperature (condition 1). The r.edia .
is then assumed to be air with its density being obtained using the
,. ideal gas law and the corresponding temperature end pressure (condition 2). For conservatism, the analyses are also performed '
. assuming the temperature to be the temperatur5 for saturated steam (condition 3'being steam and condition 14 being air). .
The above translates into the following conditions: S 4 8 e e 4 9 149 -
1 9s D n - o LOCA CONDITIONS Dryvell Containment
~
~
. CASES 1 thru 5 CiSE 6
. Condition Condition 1 2 3 4 1 2 3 h Media Steam Air Steam Air Steam Air Steam Air Upstream Prescure kh.7 hh.7 hh.7 hh.7 23 7 23 7 23.7 23.7 Initial Density .0995 .153 .106 .16h .0509 .0810 .0564 .0918 Initial Temperature 330 330 274 27h 330 330 237 237 Final Pressure 14.7 1h.7 1h.7 14.7 1h.7 1h.7 1h.7 14.7 O e _ a
O( To detemine which condition results in the largest aerodyna=ic torque for those systems connected to the dryvell, the co=puter program
" FLOW-GAS" is run for Case 1 using all four conditions. The same is perfomed for Case 6 to' deter =ine which is the vorst condition for the piping system in containment.
For Case 1, condition 2 was the vorst, 'for Case 6, condition 4, although in both cases the variation was less than 1.05. Using condition 2, the flow and the aerodynamic torque were calculated for Cases M through 5A. For Case 6A, condition 4 was used. The computer input sh'cets and results of these calculations are given in Appendix B. The flow conditions for all cases were then used for input into the . computer program " FLOW-CL" to deter =ine the closing times. This was . performed for both flow in the preferred direction and the nonpreferred m, direction. The computer input sheets and results for these calculations LA ' are given in Appendix C. Shown in Appendix D is a comparison of the calculated closing times under no flow conditions to the actual closing times of the subject valves when tested at Posi-Seal. Posi-Seal believes the relatively good correlation.between the ' closing times demonstrates the accuracy of the computer program "FLO*n~-CL." The largest aered,nc=ic torques for each of the unique valve sises (10", 24" and 36'!) along with their corresponding bearing torques are then inputted into tha corputer program "LOCA-SMC." This program then calculates the combint seismic, operational and LOCA stresses of the critical areas of the valve assembly. These stresses are then showed
'o be less 'than the allowable. If they are not,then a caterial change l
is made to ensure the stresses are less. These calculations can be found in Appendix E. O e
O( As can be seen on Page E-3, tlie stresses for the actuator bolts based on an aerodynamic torque of 122,133 in.lbs exceed the allovable stress for bolt material A193 Gr BT. Consequently, the bolt r.aterial is changed to A354 Gr BD for all 36" valves. e 0 e 4 e e C . e 4 9 e e e e o 9 d 52 -
c-
^
O. ' C . INFLUENCE OF BENDS AND TEES
~
The piping systems vhere bends and tees could have an influence on the aerodyna=ic torque of the valves are:
- 1. Cases 2 and 3 where valve IVQOO4B is downstream of a 24" X 36" reducing tee.
- 2. Cases 4 and 5 where valve IVQ003 is downstream of a 124' bend.
For valve IVQOOhB if it is to be cycled the same time or before the
. other valves in the system, it is reco= ended that the valve be orientated as shown below.
J e . bT, m m m
.t . , ;
0F C# l l 1 {l
. t The reason bein6 that the flov from the tee vill impact evenly on "
either side of the valve stem. 9
T J( as such: For valves IVQOO3A,* Reference (b) shows the valve to be oriented l J
- If this valve has to be cycied the same time as, or before the valve upstream, and has to be placed, on a forty-five degree angle J for space considerations, then it should be oriented as shown below:
This is done such that the flow vill inpact the disc on the side . of the di::c that vill tend to close the valve. m
* **e*
{, If space consideration a11cvs, then valve IVQ003 should be orientated as shown below:
. l l f---
. or n'
1 M l NOTE: ASCO S211 solenoid valves have to be mounted upright to operate properly. Therefore, for the valve asse=blies rotated frc= the vertical, the type of solenoid should be changed or the 8211 solenoid reorientated to be upright.
-- Posi-Seal has perfomed an investigation to detemine what effect a pipe bend upstrea= frc= a valve vill have on aerodyncmic ~
torque. To date this investigation has not revealed a::ything that Posi-Seal can use with confidence. Consequently Posi-Seal has taken - the following approach to analyzing the valve IVQ003 - If the valve were located such that it's ste= layed in the plane of the bend, the flow would impact evenly on each side of the stem
^
with the resultant of the velocity profile acting out board of the valve center line. h . .
C To obtain a feel for what effect this vould have, it is assumed thit thic resultant acts at the halfway point between the disc center line t.nd the end of the disc, and that the density of the flow is doubled. Posi-Seal has determined that the hydrodynemic torque factor, Tgy, is a function of the shape factor (Ey+E) 2
- _ .,l
.}
Ey+ _ p L J 4 D =- Tgy = Ky D
~
(Ey+E)
~
Ky = D 2 K 2
= h.6098 - 5 915 Ky The hydrodynamic torque factor for a 36" valve at 90' equals 89607 in.lbs[ psi. If D equals .707 D (2h.591") baced on the assu=ption above, the hydrodyna=ic. torque factor equals 11,134 in.lbs si.. (Note, this is approximately equal to the hydrodynamic torque factor (12758) for a 24" valve where D = 22.352). Since aerodynamic torque is directly proportional to the density and the hydrodynamic torque per Page 16, the resulting aerodynamic torque for the case assumed above is approximately one, quarter that for flov Eoing d'i rectly through the valve.
If the valve was located such that the ete= is perp'endicular to the bend, a te$n has to be added to the aerodynamic torque that takes into consideration flov impacting the disc outbesrd cf the stem. CL
h The magnitude of this force can be deter =ined by using the ( ~' principles of impulse'and momentum. AM Vy + F At = AM V2 V2=0 LW = F At 1 , where AM = Change in mass - lbm V = Velocity - ft/see F = Force - lbs At = Change in time AM = A PV bt 8 where A = Area - ft - Density - Itm/ft 3 p = g = Gravitational Constant
=ApV ' '
(7, W = Flov - lbs/sec WVy At = F At 6 F = WV y 8 W = .076h Q 3600. , where Q = Flov - SCFH F = .076h Q V = QV 323 (3600) 1 517X10 6 Taking the flows and velocities which resulted in the largest aerodynamic torques for this valve (Case 5) assu ins flow directly through the valve, the forces are determined for the various valve angles. e*% Or\ Deg. 3 ', F 10 1,597,000 69.4 73 20 3,195,000 138.6 291 30 6,480,000 281.6 1203 ko 9,360,000 401.4 2476 50 11,360,000 493.6 3695 60 12,100,000 526.2 4196 70 - 12,100,000 513.6 4095 80 12,100,000 513.6 4095
. 90 12,100,000 513.6 4095 Again, assuming the resultant force acts at the r.idpoint between the center and the end of the discs, and that the vorst angle of attack for the subject valve is ho* (See Figure 8 ), the resulting torques are calculated.
R = D cos (40 - 0) T R
= RF in.lbs .
I
~
- Deg. R, T
._R lo 7,524 549 20 8,164 2,370 30 8,556 10,290 40 8,688 21,510 50 .
8,556 31,610 60 8,164 34,260 70 7,524 30,810 80 6,655 27,250 90 5,584 22,870 If the above torque et 80* is added to the aerodyna=ic torque cale ated for case 5 at 80*, the maximum resulting torque based on the assumptions for this orientation is obtained. This torque is 115900 in.lbs. e c '
O LI) % . 2 4 & L- T O' 1!!
*~o ' us ^
$.W Sb$ f O .
W 2w w (, 2 3 b a W Y$s' x r2 0 d 4 W
=
dU' W, F ?. 23 x p 3 b h' S - LL) f . 0 - 2fu =$ d O*$ 05o O. c2 .JtD <- *I m- ul - **' / ,f
/ i / -
lli .\ s
'V i
0 b$. 2 g l -
/ ,/
9,g o 4 ,1 F* v6
.n@d 'O yo $8 1 s l 0 .
N
. /
y0' ~ N \ \ i,/ 30 ny s -r, 1 o . So j
. . NN / \ , I o / ,
xcx . x i N' .*. I / '..,_' s I U ld W 1 >J c4 q' l O I
'9
?D Fig.ue S
O - 1 ( ' Since the valve lVQOO3 vill be orientated on a 45 angle, halfway between the two orientations described above, Posi-Seal believes that the aerodynasic torque value vill be subject to less than that calculated for flow going straight through the valve. However, for conservatism the combined seisr.ic and LOCA stress analysis for this valve vill be based on an aerodynne.ic torque of 122,000 in.lbs. This torque being the torque that valves IVR001A&B will experience. O G e e 4 e O O. -- e a(. . 6 S e e e S e 9
I b u - APPEIDIX A
- Sche =ntics cf the Piping Systers E.
p %
.-------: - ~- m -~ % . . . ,. 3 .--..----.----y __ . .- . -
O.c
~
CASE 1 DRn' ELL - h I ' 2k" Valves IVQ001A & IVQ0013 Worst. condition f Upstream flange of IVQ001A breaks off Downstrea flange of IVQC01B breaks off The resulting system is as shown below: hp
} te ~
' ~
h /g ,jj per Ref. (h) G. ?
@ hi Station No. Type of Resistance (No.)
1 Entrance (1) K = 5 Dyg = 24" e 2 Valve (7) Cy = 23h12 3 Straight Pipe (h) L = 9.6' 4 . Valve (7) Cy = 23h12: , 5 Exit (8) K = 1 D OUT
= 2V Valve IVQ0013 (h) is cycled close. 1 CASE 1A
, Velve 17Q001 A(2) is cycled close, J
. A-1 mv, -t - -- --- . ,-r- - . - , - - - - - - - .- .
mm
~ - w* ; w.--. a.~
. ...... , . ~ .. , .. ..n- .
. . * *- w a . ,
pn ~ +e, _ - .o,. y yu.. m. o n. 1 m %m. ..s,. ,y.
. , e .
,o , ' r. ,- ,.
s
* <.e
?., 4 C " %, .
.*Ef.
'[7.4 %, W,#
4
.m
- t $r. e, g%. ,,s, . * '*s ' a ,- s. , g . >4 o. ,m. .a.
.i is
.: s m M. :. .Q V n.
054 .m...
. ..+ .' ' ' /n .
y - ._t: 7. ,' a,f f. , U3- %. ^, ' ,. .u ..4-
& . . . - au .c w N, s , 6 : u -. i.Cn.m --h1 7 n x; " , . .. e n J
, xA,s.y. gy, ..
n,M .=; , .;,
] v%m. . tit.4W.s.J, . ', te h7.. <e n c y.A. ., .
p.nr s..b+. e ~w m v. c w.~ .0;/ %c. n- -
.a , \ ,y*sr u. eme a . r , .c
> > , ~
.r,e o rm -n s:. . c,
. , .~ -. .
,y; a.wp .ppfg;w .. ;!r e ,n w yaL 31.,m ; m'.>;;,g.ypc w
..-u- . , 3;4. .; v .., <.. .
w r
- g- pw .h.;
- .+.. ty:'y? , ,h>
y 4- u w >. l
- i. ~
p?d';%q 4 f :- y t w 4..y. Qs f, - .< . .;fs?., . . . &-
. ' n d. %m % K, w..e,, Q'W }y o gy i:a4s].: '.y#.f.M*, f R. '.. :Q-;,M: . L.m~R, ' :.JgW. f. .'.yo ny.1n - . ;. rs;
%'. ' ay~.'nl.y Q.y v; , ,,. y;g. t>'a
% e 2 b g ,m4Dy 9 ,, : .
pG l
. .% .y.w w n r, p .
.-. W .
~ .
C JCASE 2 $..~ 'iN.xx.*%' ? D ; c. -
. .~ .
; p&y% dd"%,, <kYh5N$.h. 'JJ(i'.W.N. :U$ .W T &,YYY ,' W y& G5 d,.$'% .. h l W ? h. Y,,:?@$ &
[ N', , .'bf. . t M, I. bMkNQsg $ Q ' E ' h b . h h h N b $ M *' Nhh[$hbI.hNMN,M.%,'~hM[f.N.c 5 v kMdNM,Nhh@M.M.c$h..W.M w yqf.why&?hi
~.
l$Yh Y* n :; .VW: DRYWELL 70?. +$.,e[: V
$$v,' ?N -Q' 'n=ntim:dimr*OEM &O M-&S $%W %.
&A' Mh;W 3% & p& M):
7A @10" Valve f; 51V V1;V W j @ Q q,1 TW Q p y J $ %MW'M a m W ;; . ? @p &'F,WN hn n n % W,MM 1% .Iv.Q005 7 e and't-:
+ m 2. M. C vjp.W@v.5 , 7' f .c gy,g n
% ;. h. , @UW(p ';WW.M. .: .W i
a- ,. n ~ :
$s :,0;%'9lW@d l h;y %s, ,g, q~I'1VQ0Uhh UiN. o.. [x!,.N,;h)
& c NNb
- g. ~, i 4,31 $ 36" .Va ve ,. 'o ya m e,,<a< %' Ay.+1- DN6,hdk?(Yhfi w %w34 8
mn 94 9. ~ n,.g.. ,u i+.... . + I ' yw; . '[ .h;. a,. A.
., n p d.a e
1 J 6
- ...pw . g .. p[ m., ,~h,u ~s w. r g~rs. i s; ,. gi yv . .m ~4 p a sr .~ w.; ,
h N 8k Condition g g p o w,Dg %--:ny,m,,.a. p.ytm ,j./ Q p:$.m,u;yiQ .. yp..,~.y{. fy) h, Q.,.w,s. ~ s.. [ L , .,, ? , % CfWh4 w;?! A W4),y te.W:AkW ;cl3 w Ayc; gs, A c1. Q ; . ".% .p M:$@
~
44l AUpst/eamY 8flange ihsrMd h N @ , of c. MIVQOO5' break NMS[$ h off M$ h M 545hA
$ .c g Q % ~
[g(hkN[h jy Downstream flan ;g *. O,@C. 7 h h N 6 M 6. M [ 5 M'ge;of.1VQ00hA 4
, s;-! . w[ % ,.: . ta ga , - .ro r ; . - . +~%; ..W g/a.
h lM~ F. ,6'WvW[UlN %n cer% - f M t y
? MM%kt vd,%y,e.e M7,$:@s t; 4' Ot A~w : m M%.h w
'WN' -
dv Vp. T c rT.F %:p : N W N -L C r A M
. gg @%
MWMy;nt c#P A;GW wpe.exw'he W ~ resulting system . . is . as n shown belowM u, M'l C ..'A M,',NG s) 4... eLp gwyQ.ef. ..?- g: j a;1:y&> 3 A nc.w . +ww. @4 9n 1 . . . . e , w m :4 ., ,
- m. . A,
;; A q.nux
,M%,- m.g w . '
x .i ; Lm w,+.:p..x- . .m-m s; r;mp;m - , t y: .y m.. w. +.
+
r?N : / W Q b 3:$ 0 M;. 3 .oW .
$we$g.,$&p$..e u- c. 3~~
2 d' W;.y. 'NE Fry$6 ?QY f m.,1 . .~~... m ,e nww.. . s. .m : un. cn . . r n . .. w-. aw.
-3
, mmn.)>~.,: . , ,~: w< ,n . u.wyv
) w u ~.~ n -\Ta%w;~.. i,w+. a w15,v ~.m;.c . m ng x~ae v. .m: . pa.g w*vm :.. a.c. . as v. e&,1 :. ,-
~
- 4. %m eyc . . .c-: m ,; u .~' ~ , nL. w~ ^~. > .:. ~n.
m.u.qy, w . C. y ' -
- f. . j>a,'.;~q,n per .s , . . Bef.~ . s a _ y m.(h)h a.g %,.Q mM '
N. y3 or.% n. [ m.s , wl g l '(5 '6. dl ) .M,, m . Mb. . k.,;m-r.h. w~V,, b.h0.M, t.
. $.h, , m <, s. -M Q N N ,; $... c [ m .
h . ,y .s... . y. ,. , , ' . . ,o . 6 :r -
.m.. n c.o [8 s. gw
.e, e .13 .e .sw
- y .- w ; : n, m. v.Lw a.>. 4 , .~.w ,x m e e o, c
~ f9
. , ;J +.
-(wc v e w.a? mn.. ta . - nf u ' Q;(wg.u : r,: m .
Q.ueA p. + y. r. .. ~'
, :d . k s ro v ,
YhMhdh b.WbI.ShhnNhY ,, 5 11 "' My %$hkfkd7M. . ,*.. V c,h M .M e 10' 0hikNhhh:,M.N@yhhhkhNk
.M..mQ T. Q ,. M_... M. [ ffiI.ij:f$,q x J.e,w.y.mcm. n . , , N..h .- q . %3e.W, w u_ yo.o. , .c6 m
.n 4, 4 a %c .c ~.m .
.o *m q, pf s ,p. 1,4_
. s..* , ..A..,.x#y .
s ,a c y*q ..~m,, a, + 1
- a. v: 2 ..
_ .c., v sw
' 4 ] . %,m, , = , a. ;': %, - %'- - , *, . . . 4. .a
% ^
'q , . ...Ft.-
I e4 &y ,' 3 ' ..
; .
- y" ~
Q ,. ; l'm,$,,.Q .,i M
- y' ' f.'X j 'z&r M ' % . F P iW il5 %p j Q.%~ WVf; D,4&l.[ ^: l $O 't; V;- f ' ,, ^
. ?," M v . -
h b$7 %* ww.,;h+NN h p .m - 9 : ., . r b , I W n .. - Nk h,,.h.: b.hMih@J.:hih.,hhl
%. :. ./- ,
.L h ~r' 1
- nw w ? .. ,f'
. , c~ e+ ' - ,y 1
- 4 ,Tq,re %. . WJ.b ,* ~+-%,u :_l s,+
, . , , ,.'3'
. s q} a v ,,* .<r ,4 ~
. c.
n .;*
- c - . ;, :.
o n i m.' 'l , a
; N,. m+.r:-
8 . w .4 a- a; +,.;e;;;: . .s.r :> ;. .. w.<.p ry .,g m.. .,..s ,.,A
,. _ ... a i..
< 1, .
g ,- 3..t.
.. 1s i n.
6 ,
,7; . s . ;
.%-SV',.'*H., .
c.L,,., *:. .. h ;9
- 4 ,-
. : 3, x"y 4
4;A .- 9; , Station No. Type of Resistance (No.) - , h- d%yhkA .f M;M
. . . . . w - m. .
,< , 3. ;
~
m a *.
.1 Entrance (1) K = .5 D zy = 10 p,- " ^
g +. p' p ,,., ,
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CASE 2B - - ~ ' ~
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( ' COI.~u1 TION l
,J:UCLEAR LOCA A7:ALYSIS o.
VALVE SIZE: 2. 4 VALVE CLASS: _ 150 // yo ACTUATOR: /b d-v v ' ~330t'2-51570
/
UPSTREAM PRESSURE V Q PSIA INITIAL DENSITY , O'J 9 .)~ LES /TT3 INITIAL TEGERATURE '330 F FII!AL PRESSURE J Y '/ PSIA SHUT OFF PRESSURE 4 Y,7 PSIA MEDIA G <, ,, IlATIO OF SP. HEAT /,S2$ SPECIFIC GRAVITY L '2.
, -- COIERESSIEILITY I HYDRODYNAVIC FACTOR . )( t '
6 90 DEG / L ~) f f II;. LES ' PSI STEM DIA. 2- IN. GAGE DIA. 2.*2, 3 y1 In PACKING TORQUE 1110 m IN.LES. SEAL TORQUE V3/4 II. 11.0 DIRECTION [eud,-- INPUT STATIO!: I:3.. K FACTOF.S. ETC. s. (See Apper. dix A) i t +" v , r
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h.$gn^ ,* >STATION . 1 yy, NO. ENiiMEE . 24.0 VALVE 'W. i-' s
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- 3.h. .
1 ,. 44.7 ,0.0V95 330.0 640.1 ., , 39.1 'k0.0900 703.7 .p'; ;G' 't r
- y 723 319.3 J':1 1
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7,1: E 35.5 ,4 33.4 i C..+3['. & 0.0799 , 307.1 C.'f .. 796.1 < ,F > . ,\ , o o."II ' L. 9 i ! "E 'e ' 14.7 0.0430 ' 250.5 ' 1479.0 ' NOTE: THLRE IS CHOME FLOW AT STAT 10as 5 *,1 i f ' w'.f.', . * s c4 4 > G : h, *. ..e- ' .a- V -+, ?'< 9 ', s ,' - ., . . .C' TW,, , lI > ~ , . ' l. 'Y - - * , we ANGLE FLOW ,DP ACROSS VALVE Taero Tdp . - . . - - ," O.,g ,,70 , V 13,1e3,s76 _ 'A 9.72 ,3J- -32,01t i s73 ,. ayY , . y U N% < {#,t . f ,t PRES 3URE .OLHSITY TEM 6LRA1URE VELOCliY O yh- 7 .. ,1 , 44.7 '0.0995 330.0 502.6 / ', i.',Jc ' b .,_, 'M, g) $ i
- 2 '40.3 od921 9 32L.7 4.24 7 ' '
g'Qi.- M' P" . 4 *3 ,30.0 '37.5 -'O.0073
- 0. 00 t31 a
- v. .316.1 317.0 655.2 659.0 4
' 'l ' .4 1;[ ' N": I y"Ul' 5 '27.8 Ot 0A96 d' ?*3. 5 ' 025.6 ' f' . '*6 14.7 0.0432 .- 250.0 1316.9 Iy..,- --.cQ M. '< r: ,, ,, e ..vpg 2 a; a, p.' -5 , ..
- u. W n9l3 ., ,, t ;.;5 '
a ,. . . , , e 'd, .v, j . q~ c <- , ,-u ivr- - +> .. e. , o np -M,,' t.s f pi a : wn. , af g., FLOW CDP ACROSS VALVE ;41 Taero ,s Tdp i * ,3 a .O M;; ANGLE ,, 60 y10,560,121 13,417 , ; 7 Q U[;q;W j _10.04 ' r ' 1,111 -(g ' , .1 ? 7 e.,, ", '.j'. / .gj
- d. , FRESSURE OLN311Y -TEMPLkAiukE VELOCITT s
" ,, ' 3 > ,- O 9 ", '1 44.7 0.0995
- 2 '42 3 0. QH S
-330.0 325,6 , 466.6 493.6 . ']; " , %* * , 3
- f. i' ',' 3 40,9 , 0.0932 323.0 495.6 ' ', g '
' ( * ,e 4 40.8 .0.0929 3 2.6 495.6 - .? ' ~ S "'1 9 0. QYp 273. 7 79A.3
- 6 14.7 0.0430 250.5 1077.5 , ,
O NOTE: THERE IS CHOME FLOW AT STATION 4 '
- O ANCLE , FLOW DP ACROSS VALVE ,
Tacro Tdp ,' 50 7.P93.926 24.52 4.215 1.445 ' O' PRESSURE DEN 3ITY TEMPERATURE VELOCITf * ~' 1 44.7 0.0995 33M 340d 2 43.6 0.0'/75 327.9 353.7 O. 3 42.0 0.0V63 326.5 350.1 . 4 42.7 0.0942 - 326.3 3%A.1 & 18.2 0.0506 264.2 684.1 C 6 14.7 0.0430 250.5 804.4 * .(H 1 a . NOTE: THERE ls CHOKE FLOW At STAT 10e 4 i .fi- .- 8 jd' Y J' " f ,Iy4- 1 ,g ',' T . ~ s , . f . . p , + t v . l 6_3 f .o . e ,. I \ s l ~ yy . > w p.,,m - . + - ; ! .M = s ,..'> .
- N t, /.1 * * ,,, ,.-
,i t ' .- > t .. ) S ky s:# ',. 41, U J*' 4 + .N:. . s /- 4& %x.S)w;{th 2 i ?f M i,;9 2 .j Q- - . d. ,,e. +,i. e s' 's - > ~ s -+- * ' t ~ ' '
- 1
< d .e t** $; - - .0; ' ,? *te ,4 yV.y f *AQ. 4 8, h V ._ , e . $ 8. 6 en , , % . g }; .;. ' 4. l ,- , =. ., , .c. ,i. 3 ,.t 1 M D k, W l4 M N [ y[ F k-Y M,r. 4 - .M * ' ' M ' ' ' , '* ~** ~ ' ~ ' ' fb b . . ['4d '
- l g e
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u- * ,7.*% e ,_r ,1 :w,i 2+,'s, gtl, 3,~r n . .$ ; , . s ,c . ,. > . Ahi ( M *~ d;;% i' , ,t. O Ai W ' *Y *k,1 Ln,y *4.;t <u d. d A.'~ A' y:D.< 'A + . ;- : s 4
- q1 l j 5 ' 3 *,
~ s.3 i '4.,_.... , L*; ',VnY' . '. . i . 2 .:. ~. . . . - . . . . . . ., J.. . . L .:. 4 o .~ i. : , * ' * ' 6. 't # 't "n s J < .} - .. . .. . . . . .'.d .2' ' ' B
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. +p; ; Q <-% f :L u* it !L; ;b e., R A - ;t- .o ,- .L- '.': e,* v. .' , *s' - yM *- rANC.LE- . " Ff,04 DP ACPOSS VALVE : :1,e " , ,W h' ~ Taero Top - 'f f% % g-,40 5,350,315 . .27.70 , _1,327 1,633 , 1( ..e 4 . .- - l ., M -..' . . f.I QMM:i;;s 7 ' f-PRESSURE i' is ' - - , tv , $. 3.w 3' ' 4 ' ' . %n.? JJi tt b i Jy N DFNSITY d' N _., TEFERATURE VFLOCfTV 4 ' ' % C. .1 . ; 4 4. 7 0.0Y95 . 330.0 - > 236.4 , -- #I kMhI. t2,' .- - A .j , Oi , %a " af '3 Q44.2 43.9 i ,0.0907 0.0902 , '. 329.1 320.5 7 237.6 238.9 9 ~ r r , '~t . '?f'hr[N,Y " i go.0981 ,e >300.5 238.9 .. ~ ..,QA % p dg e,4.;. y 43.0 . b, .i . .. x . '*b56 %%f'16.1 , 0.0463 x k.256.6
- 507.8 J- '
s *94 ,*' * < . 2 4 >' p, .'[Ij .ea 3 * - 14.7 'O.0430 '250.5 545.9 q.-- ' j 4 % m N0iEt THERE IS [HOME FLOW Ai STATION 4 . .
- y. .f -
,1 ./ t - k hh,b
- c. \il i[ *
~ ' b - ' 4 ~ < ANGLE ~ FLOW .OP ACROSS VALVE 1 Taero < Top ',.- i %p;m op _ ! ) I'"J. .' 282 .7 . 1,721 O M , g w .w,3,0 ,:,14.53,306,721 syL 5,.., e 29.20 ... J ?a .e - [ * - p< r 4 Ws y,*> .PhESSURE DENStiY. TEM ER ATURE . VELOCITY
- 7,.
J q;PNq. 4..1 ; g U- R Li44. 7 ~4, ?0.0995 - i330.0 ' t" 146.1 ' ' ', yc s .iE'L,'ijag z 3 . 229.7 146_3) ' ' ' " '6 ' ' ' g y4 44.4 . 0.0991 > .329.5 146.4 - , .a , .. , w .. m.~ ,W , .,, [ M Ni, ' s 'O.0990 T329.5 6 ,(~7[;p; EQ' 15.
- m%, 34 p"y y 44.4 7 ?') '
i .146.4 , / ' - O . 0 4 4 ~' ' M2J rn_3 't ' Ta (
- 6.vdg O i,90T,E:.THERE .' .6 -14.7 IS CHOME FLOW AT STATION 4 0.0430 250.5 "IO 337.4
-h ^ > 't ' - + -; b; ' '+ ' g m. - - i-, q, . I e
- 4 ~ . 1 *. < % 6.
- Q') -
f ., f , e C FLOW' a rA ' ,' 4' , l(Q']],'V'NGLE .OP ACROSS VALVE Taero Tdp ' ' 20 + ,, ; f' ?
- f, i
,t f' n' * .. . 1.659.262 29.00 45 1,J.,57 i ' h'h%fPRESSURE . DENSITY oTEPPERATURE EVELOCITY ~ , r -- j h * # , h;g\ ' 'n ' i h W. g 1 44.7 0.099% ??0.0 73.2 ' ^ f tsc 2 1 44.6 0.0994 .329.9 .73.2 m . . , . 49 .c 13 c.44.6 ,0.0994 329.0 ' ;73.3 P ; r '. . ! # 4 ' i, < 7-Tz' JP- ' ' 4 4._6 'O.0993 329.0 71.3 gg"a 5 14.0 0.0433 ;251.1 160.0 , , m 6 0.0430 ( .t ._ ' O . 14.7 250.5 ) , 169.2 i. 7* i ,s 'i =m ' NOTE: THERE IS CHOPE FLOM AT STATIC'8 4 ' " ' " (l f?ANCLE , )- 0 . '? 'b b't i .i ' FL OW ~ i > DP ACRCSS VALVE -d l (({; < ' ' Taero $a p
- l [f^ v. r. - 'f['D{$f".l?*{{-& 4 yh -b {
Tda - I
- - 14 , s , , s 035,650 29.95
- 4 , 1,765 u
- j. ...3 ,,.s ,~4-O e
w, , W', . - 3 r-PRESSURE OFNSITY w > TE8'PER A TURE VELOCTTY . o o 1,, ' - -: a , . ; n V .'
- e 48'te '
~ cr- ' m, y ,,a 44.7 0.0995 330.0 36.9 Q . 7, . . 0.0994 +
- x. . y
. v ' ' N h' .e' 3 2 w! 44.6 ' O.0994 ;329.9 n g ).36.9 v ,. A 't " s , ; ,0'y- 4' * . W ft' pf 44.6 329.9 . 36.9 ' ' - < 4 44.*6 0.0994 329.9 36.9 I y .
- 6*
- 14.7 0.0431 250.7 85.1 .
Q .>.-} ' 4 6 14.7 0.0430 250.5 85.2 ' ~ , ' NOTENOS'~CftDTTKOH AT STATI6N 4 () ' O ' ' . n-1 1 s I () a. t (.. . ' ,s , a d 8 + y gj .ap >M . 1 e t'. * , .I . . , t .4 .P g + , . e f . . E. s.A > hl ' * * ' 3 . f , t l p.> w . . E ' l 4 % h .s
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Zf4$4.iuf N M l;f D ' s;f k l,'Q G % j, d.y t,$d.iwM.m('R.I yW @ ' 4 M, F M ..r ,,b.M,L/ .UUCLEAR [3 LOCA ANI. LYSIS + '. f, N t Mn . M N,1n.( . 4.1ks.iQ W 2 . ._.. . .. .o m. g n s. en : mwgw . e g w~ h y y: m , @,7./ ;w. w:.g;m yp m v, w p,:;x,, +v. ....w- ..,...w. , .,,, . ,x. . y a ,.,w.g:p ;n.x n1. .g. ..,Wv.. u.x . . <h.mn> . .g# sp,mna, , , ,e . .. n ; ' ' , 7', ., ; , j m. v., :....+( u e^ %g - . a a.3, - . .: # y o"u #' ' " ,.'E*' " ' '~ ' 2 '[ f " s W hWt~X:.m VALVE p . ' mSIZE: e. a a u+w , / W/Tb **. , W.. .'. . ,yM,$n.h$! ~ D.V.,ALVE CL.ASSI -N - Mi ,* U SQh. . f 7 Y. j[ uN. ~.~. , , . r ~ , ~, , . . '- ./ )k Y,-v v 3 3 8 02. -5/ Y O ^ * ~ ..w:d;MA. n .,CTUATOR$ , w .- .x .- . + ,m 4 . 'm;.: A , w . n ..,v' m a,. t. :,L,n ::w.w. k ,A,j'p,bg . y. 41 .;,::L.n: (i :,3- % m !: i w.v: K R '- .a v ..nc ' .<.ce ~. /.', -1 , a w , , Q p.. ,h....n M U,)' W. . 't " , , : ' ;. e ? , y. 4 .y c ., ;7;% ; <r : 1 > , j:, . ...hm;, Tr .a _ q . . t: \ , . ,,', . . . c , , , . . m. r * ~ #q : m ,,3 . , a e. ~L,s..rwr u ;,umm, : . s. ', . . :~t < c - "LBS/FT3"g...- jJe d UPSTREN4 PRESSURE . ,7 ; .W / TSIA . . - ~. r.+. O INITIAL DENSITY , 17') 4 mcu a: .5! N ; ,.INITIAL a TE!PERATURE 330 'F T }]n,W5 , ',' FINAL PRESSURE - /1-e~) -
- d. PSIA' ' ' ',,1ep m
.m. m .n.k . . ! ,. , D$gMSHbTOFFPRESSURE 4*i ? PSIA ,, IMEDIA -AAr 8: cM 'w w : r ~. - .c ' n RATIO OF SP. HEAT ' 'A Y ~ v- . , " A '/ ~ n' D d,: M.'M 7 $ wW< %, ~> .. SPECIFIC GRAVITY f
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.' s/ /.,/.b. a wJO
- 7) eJ..N'jf, , - . ,' @ 90 DEG f'2.75T
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- 2. ' * ~ .
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