ML20116G841
| ML20116G841 | |
| Person / Time | |
|---|---|
| Site: | Catawba  |
| Issue date: | 07/31/1996 |
| From: | Mccollum W DUKE POWER CO. |
| To: | NRC OFFICE OF INFORMATION RESOURCES MANAGEMENT (IRM) |
| References | |
| GL-95-07, GL-95-7, TAC-M93446, TAC-M93447, NUDOCS 9608090072 | |
| Download: ML20116G841 (55) | |
Text
il I
s Dukelbuer Company snwwR ARDwu,Jn Catauba Nuclear Generotwnikpartment -
lia hesident 48W)ConcordRoad (NB)R31JM Offce kk. SC%)i45
(&B)$3/&f3 Fax DUKEPOWER July 31,1996 U.S. Nuclear Regulatory Commission Attention: Document Control Desk Washington, D.C. 20555
Subject:
Catawba Nuclear Station, Units 1 and 2 Docket Nos. 50413 and 50-414 Response to Request For Additional Information -Geneiic Letter 95-07,
" Pressure Locking And Thermal Binding Of Safety-Related Power-Operated Gate Valves," Catawba Nuclear Station, Units 1 And 2 (TAC NOS. M93446 AND M93447)
Gentlemen:
On July,1 1996, the NRC issued a Request For Additional Information to Catawba Nuclear Station regarding Duke Power's response to Generic Letter (GL) 95-07. Catawba was asked to provide the Commonwealth Edison analysis used to determine the pullout force -
required to open valves 1(2) Nil 21 A and 1(2) Nil 52B, Safety Injection (SI) Pump Hot Leg Injection, and 1(2) NI009A and 1(2) NIO10B, Chemical and Volume Control Pump Cold Leg Injection Isolation. Additionally, this request specified that the actuator thrust capability calculations be included.
i A description of evaluations and training for plant personnel that have been conducted for
]
cach design or procedural modification completed to address potential pressure locking or thermal binding concerns was also requested. Attachment I contains a description of_the Commonwealth Edison Analysis process as well as an explanation of how training and procedure change concerns are programatically acidressed during the modification process. contains the analyses and calculations for the individual valves referenced above. If you have questions or need additional information, please contact Allen Smith at (803) 831-3952.
j Very truly yours, N
[
W.R. McCollum, Jr.
i
\\ GAS
&g 9608090072 960731 PDR ADOCK 05000413 P
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Document Control Desk Page 2
' July 31,1996 xc:
S.D. Ebneter, Regional Administrator, Region II R.J. Freudenberger, Senior Resident Inspector P.S. Tam, Senior Project Manager, ONRR f
i
.~.
O Response to NRC Request for Additional Information 4
NRC GL 95-07: " Pressure Locking and Thermal Binding of Safety-Related Power-Operated Gate Valves" Request dated July 1,1996
l 4
Duke Power Company Catawba Nuclear Station, Units 1 and 2 July 31,1996 Response to NRC Request for Additional Information NRC GL 95-07: " Pressure Locking and Thermal Binding of
{
3afety-Related Power-Operated Gate Valves" Request dated July 1,1996 A copy of the Commonwealth Edison Model analysis is enclosed for each of the valves referenced in the letter dated July 1,1996. The model gave the total pullout force required to open these valves. The actuators' available thrust wa= determined using data from their 89-10 calculations. Copies of these thrust capability calculations are also enclosed.
I For valves 1(2)N1010B,1(2) nil 21 A, and INil52B,52% uncertainty was added to the static unwedging force to account for VOTES uncertainty (uncalibrated test data) in the open direction. For 2NI009A and 2 nil 52B, the unwedging force was obtained from calibrated test data, so only 10% instrument uncertainty was added. Since no test data were available for INI009A, the unwedging force was obtained based on EPRI's conservative bounding formula, and no additional uncertainty was added.
Calibrated opening stroke tests are currently being performed on these four Unit i valves.
Unit 2 valves 2NI009A,2NIO108, and 2 nil 21 A will have similar tests performed during refueling outage U2EOC8 in February,1997. The actuator on 2 nil 52B was replaced in February of 1996, and a calibrated opening stroke was performed at that time. Valve 2 nil 52B is scheduled to be tested again during U2EOC9 in late 1998. The results from all these stroke tests will be analyzed, and the actuator capabilities will be calculated.
Pressure Locking /I'hermal binding concerns for these valves will then be reevaluated.
Information was requested describing evaluations and training for plant personnel for each design or procedure modification completed to address potential pressure locking or thermal binding concerns. In general, all modifications are reviewed by a former Operations Shift Supervisor to assess the impact of the modification on Operations and their procedures. Additionally, a training contact is notified and the Operator Update program is utilized to communicate pertinent information about the modification prior to the modification's completion. For some of the more complicated modifications, Operators are trained prior to implementation. Additionally, an Senior Reactor Operator (SRO) in the WCC (Work Control Center) signs on all work orders, including modification work orders. This ensures Operations (OPS) personnel are informed of all work. An important step incorporated into the modification process is the evaluation of the effect that a modification will have on plant procedures. Based on this evaluation, l
procedures are changed and training conducted as appropriate.
j l
l Page 1 of 2 i
Catawba Nuclear Station has implemented two (2) modifications in response to pressure j
' lockiiig and thermal binding concerns. Bonnet vents were added to valves 2 nil 84B and 2 nil 85A during refueling outage U2EOC7. Valves INIl84B and INI185A will be i
similarly altered this summer during UIEOC9. Since these modifications are fairly straightforward, no special training was given other than the usual updates. The design basis document (DBD) for the Safety Injection system reflects the changes to the U2 valves, and will be updated again following completion of the U1 modifications.
Additionally, the NI flow diagrams show the new configuration of the valve bonnets and i
their vent valves. The new vent valves have been assigned unique tag numbers. This way, Operators are visually reminded of the bonnet modifications to nil 84B and 185A i
cach time they glance at these drawings.
Only one procedure, OP/2/A/6200/06 " Safety Injection System Procedure," was changed as a result of pressure locking and thermal binding concerns. The new bonnet vent valves were added to the valve checklist enclosure for this procedure. The corresponding Unit I procedure will also be updated. Similar to modifications, all procedure changes are reviewed and Operator Updates are issued accordingly. Cross disciplinary reviews are done where appropriate to ensure all affected groups have a chance to evaluate such changes. Procedure changes written and modifications designed at Catawba receive a thorough 10CFR50.59 evaluation, which is reviewed and signed by a qualified reviewer (exceptions are editorial minor modifications). The 10CFR50.59 evaluation for the NI bonnet vent installation looked at the increased weight of the vent valves and associated piping and their effect on the NI system. The fact that 2 nil 84B and 2 nil 85A are now uni-directional was also addressed.
l Page 2 of 2
i e
Catawba Nuclear Station Response to NRC Request for Additional Information NRC GL 95-07: " Pressure Locking and Thermal Binding of Safety-Related Power-Operated Gate Valves" Request dated July 1,1996 Commonwealth Edison Model Analysis And Actuator Thrust Capability Calculations
)
C:lculati:n (2) 1N1121 A Valvo Information Actuator information Feet.ca NI PurEp A to NC Loops B & C 10. Isolauan Type EMO
.fanufacturer Borg Wamer Manufacturer ROTORK
!!am Number 09J-219' Model No 30NAX1 56 Dr2 wing No CNM i205 00.00G7 RPM 3600 mens class 1500 PLTB System Calc Inputs Gear Ratio Size 4 00 (A) Rghest System Temp dunng c!mmg 110 Torque Ratmg Disc Type Flea (B) Lowest System Temp smce siasms 40 Umt Emc Nican Seat Diam 3 75 (C) Rohest Press on either side smce closwe 2235 Undervoltage Duc Diam 45 (D) Lowest Press in gerung on same side as dub Diam 2 24 (C) above o
System information Hub Length 04 (E) Lowest Press For opemng on opposite GL 89-10 Yes Disk hckness 1 38 side as (C) shove on either side smce closure o
Flow Diagram CN-1562-12 Nsdge Angis 5
(F) Lowest System Temp when closed 40 Coordmates J. 5 Lam Dem I375 cG) RsFest Systeem Temp when opened i10 Normal Position close Bonnet Vent No Safety Posiuon Open boa Matenal SA 182 F316 Req'd To Open Y
Nedge Matenal SA351 Gr CF8M Dp To close 1520 BB or PS Presswe Seal Dp To Open 1520 Dwnsmn Press 0
Design Temp 650 Thermal Binding Review in initiil screenmg using the data sheet. is this valve susceptable to thermal bindmg concerns?
YES The temperature differential is
/ The system design temp is 70 650 is the wedge design flex and the system design temperature 200 F. or less?
No 1s wedge design flex and temp differential 100 F or less / or solid and temp differential 50 F or less ?
Yes 1 N1121 A has been detemuned to be susceptable to thermal bindmg? Yes / No No flydrtulically Induced Pressure Locking In uutal screening using the data sheet, is this valve susceptable to rapid depressuruation concerns?
YES Was this valve confirmed to be leakmg durmg the time this valve was last tested?
N 'A lias a bonnet vent been added or has the seat or bndge wall been tapped to reheve pressure?
No 1 NI121 A has been determined to be susceptable to hydrauhcally induced pressure locking? Y/N Yes if this valve is susceptable, see page 2 for sizine equation?
Thermally induced Pressure Locking I
in matcl screenmg ustng the data sheet. is this valve susceptable to liquid entrapment concerns?
YES is vtive bonnet designed such that air will be entrapped?
N/A Was this vahe confirmed to be leakmg durmg the tune this valve was last tested?
N/A l
Has a bonnet vent been added or has the seat or bndge wall been tapped to reheve pressure?
No 1 N1121 A has been determmed to be susceptable to thermally induced pressure locking? Ym No Page 1
Criculition (2) 1N1121 A Calculation Inout and Outout Summary e
Ikmnet Press (P510)
Pb 2235 Londmg Constams (IbO
_Ll!
0.000897242 Upstream Press (P510)
Pu 0
Imdmg Constama (ibO
.Lt ?
0.062865036 Dwnstrm Press (PSIO)
Pd 0
seat coefficient (m) mu 0.520792372 Disk Thickness (m) t 1.38 Average DP DPavr 2235 Mean Seat Diam (m) de 3.75 Disk Constant D
6700307.186 Disk Radius (m) a 1.875 Disk Constant C
10615384 62 Valw Hub Radius (m) b 1.12 Moment Mrb 821.8223093 Flub Length (m)
L 0.4000 Moment Qb 2256.177623 Seat Angle (deg) theta 5
DcDect from press & bndg Ybq
.l.48534E-05 Stem Diam (m)
Dstem 1.375 (Denect due io press )
Kas
-0.116210118 Poisson's Ratio e
0.3 (and shear stress
)
Ysq 6.21516E-05 Modulus of Elasticity E
27600000 (Denect due to )
Preree 1$877.09994 static Unwedgmg ihrust Fpe 14,265 lbs (Hub stretch )
Ystretch 2.91948E 05 i
Valve Factor
\\7 0.50 Total denect due to press (m)
Yq 106E-04 Plate Constants
_C2 0.068870443 o.a.ct aus so s.si f a sh nm/ibcm>
Ysw 7.8914E-08 Plate Constants
_C3 0.008354102 o.s au.m i ra bnanc.ac=>
Ybw 2.53691E 08 Plate constants
_Ce 0.774882489 o.s i eu. ic hub mp, si.er=>
Ye.mpr 2.16629E-08 Plate Constants
_C9 0.267301135 Tow a.n au.ms icmcin.or=>
Yw
.l.25946E 07 S.at samact force to cr
- t. Yabo Fs 9933.927615 Unscaung forces Fpestem 3318.736755 Fver 4302.847441 Fpreslock 8576.05621 Required Total Force Flotal 23,825 lbs Calculation Coefficient Of Friction Between Disk & Seat Rings mu=VF *(COS(thets*PIO/180))/(1-0T' SIN (theta *PIO/lNO)))
me= 0.5207924 AYertge Dp across disks DPavg=Pb-((Pu+Pd)/2)
DPav8= 2235.00 Disk Stiffness Constants D=(E*ta3)/(12*(1 v 2))
D= 6700307.2 a
G=E/(2 *(1+v))
G= 1.lE+07 Geometric Influences C2-0.25 *(14bla)a 2 *(I +2
- LN(a/b)))
C2= 0.0688704 C3= b/(4
- a)*(((b/s)a2+ 1 )* LN(a/b)+(b/s)^2-1)
C3= 0.0083541 C8=0.5 *(I +v+(1 -v)*(b/a)^ 2 )
Ca= 0.7748825 Page 2
Cticulation (2) 1N1121 A C9=(b/s)*(((1 ++ y2 )* LN(a/h)+(((1 -v)/4)*(1 -(Ws)*2)))
09= 0.2673011 L11 =(1/64)*(ll +4 *( Wai" 2)-(5 *(b/a)* 4)-((4 *(Wa)^ 2 )*(2 +(Wa)* 2)* LN(a/b)))
L11= 0.0008972 L17-o.25*(14(1 -vy4 )*(14ble)^ 4 )4(b/s)^ 2 *(1 +((1 +v)* LN(a/h)))))
L17= 0.062865 Moment Mrb=(-DPavgas *2/_Cs)*((_C9/(2 *a
- b))*(a ^2-ba2) _Ll7)
Mrb= -821.82231 Qb=(DPavg/(2
- b))*(a*2-b"2)
Qb= 2256.1776 Deflection due to pressure and bending Ybq=((Mrb*a 2* 02)/D)+((Qb*a*3* C3)/D)-((DPasg*a*4* LilyD)
Ybq=
-1.5E-05 a
Deflection due to pressure and shear stress 1
Kan=(-o.3 *(2
- LN(a/b)-l +(b/s)*2)
Kaa=
-0.1162 l
i Yaq=(Kas* DPas g*n*2)/(t*G)
Yaq=
-6.2 E-05 Deflection due to hub stretch j
P force =PIO*(a^2-b^2)*DPave P force =
15877.1 Yat retch =(Pforce/(PIO
- b a 2 ))* U(2
- E)
Ystretch=
2.92E o5 Deflection due to pressure forces Yq=Ybq+Ysq-Ystretch Yq=
-1.1E-04 Defl ction due to seat contact force and shear stress Ysw=-(1.2 *(ale)* LN(a/b)* ay(t *G)
Ysw=
-7.9E-oS Deflection due to seat contact force and bending Ybw=-(n*3/D)*(LC2/_C8)*((s _(%)H(a/b)* C3))
Ybw=
-2.5E-08 a
Deflection due to hub compression i
Yeom pr=(2
- a
- PI(y(PIO
- b" 2 ))*(L/(2
- E))
Yeompr=
2.17E-o#
Tctri deflection due to seat contact force l
Yw=Ybw+ Ysw-Yeompr Yw=
-1.3 E47 Se:t contact force to create Fs l
I Fe=2*P10*s*Yq/Yw Fs=
sess.es Page 3
=.
Y d
Criculation (2) 1N1121 A Uzscating forces 4
Fpiston-(PIO/4)*(Datem^2*Pb)
Friston-3318.74 1
i Fusrt=(PIO*e 2)*stN(theta *PI(ysso)*(2*Pb-Pu-Pd)
Fvert=
4ao2.as a
i l
Fpreslock=2
- Fa*(mu
- COS(theta
- PI(yl s0)-SIN (theta
- PI(y180))
Fpreslock-8576.1 1
4 Required Total Force i
FlotakFpiston+ Frert+ Fpreslock+ Fpo Flotal=
23825.2 l
The actuator is capable of producing 26,403 the of force.
4 The force required to overcome pressure locking is 23,s25 b.
l 4
1 Actuator Margin is Margin = (Fmax - Fmin)/ Fmin
=
10.8 %
i l
The limiting component is the Actuator.
25,000 lbs s
1 j
The following provides the corrective actions for this valve to alleviate the concerns of:
Perfom calibrated test in the open direction to obtain actual unwedging force and a more accurate PL pullout force required i
J1
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1 4
1
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1 AVAILABLE ACTUATOR THRUST FOR THE OPEN DIRECTION FOR PL/TB 1N1121A ACTUATkMODEL/ SIZE / SERIAL NO.:
ROTORK 30NAX186 B3404/B2 OPEN STALLTOROUE AVAILABLE (FT-LBS):
500 (SEE TEST CERTIFICATE)
STEM FACTOR:
0.015 ASSUMING 0.15 COEFFECIENT OF FRICTION OPEN VOLTAGE AVMLABLE (%):
89 OPEN VOLTAGE FACTOR:
0.89 OPEN HIGH TEMPERATURE FACTOR 1
(NO HIGH TEMP EFFECT)
OPEN TOROUE AVAILABLE = (STALL TOROUE)(VOLTAGE FACTOR ^2)/(HIGH TEMP EFFECTS FACTOR)
OPEN TOROUE AVAILABLE =
500 X
0.89 X
0.89 1
OPEN TOROUE AVAILABLE (FT-LBS) =
396 OPEN THRUST AVAllABLE (LBS)=
26403 i
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Calculati n (2)
- 2N1121 A Valva information Actuator Information i
Funcuoa NT Pu'mp A to NC Loops B & C10 Isolation Type EMO Manufxtwar Borg Wamer Manufacturer ROTORK ltem Nurnber 091-219' Model No 30NAXI 86 Ocwmg No CNM 1205 000087 RPM 3600
- wss Ci a 1500 PLTB System Calc Inputs Gear Rauo size 4 00 (A) Rghest $vstem Temp dunns closmtr I10 Torque Raung Disc Type Fles (B) Lowest System Temp smce closms 40 Unit Effie Wear. Seat Diarn 3 75 (C) Eghest Press on er.her side smce closure 2235 Undervoltage Duc Diam 45 (D) Lowest Press for openmg on same s.de as sub Diam 2 24 (C) above o
System Information l
dub Length 04 (E) Lowest Press For openmg on opposite OL 39-10 Yes i
Disk Tluckness i 38 side as (C) above on either side smce closure 0
Flow Diagram CN 2562-1.2 Aedge Angle 5
(FI Lowest System Temp when closed 40 Cowdtna'as 3-5 stem Diam 1375 (G) Eghest Systeem Temp when opened I10 Normal Posinon close Bonnet Vent No Safety Posiuon C4wn Body Matenal SA 182 F316 Reg'd To Open Y
Wedge Matenal SA351 Or CF8M Dp To close 1520 BB nr PS Presswe feal Dp To Open 1520 Dwnstrm Press 0
Design Temp 650 ThIrmal Binding Review in irutsal screetung using the data sheet, is this valve susceptable to thermal binding concerns?
YES The temperature differential is
/ The system design temp is 70 650
!s the wedge design flex and the system design temperature 200 F. or less ?
No is w;dge design flex and temp differential 100 F or less / or solid and temp ddierential 50 F or less ?
Yes 2N1121 A has been detemuned to be susceptable to thermal binding? Yes / No No H draulically Induced Pressure Locking 3
in imtial screenmg using the data sheet, is this valve susceptable to rapid depressurization concems?
YES Was this valve confirmed to be leaking during the time tius valve was last tested?
N/A H;s a bonnet vent been added or has the seat or bndge wall been tapped to reheve pressure?
No 2N1121 A has been deternuned to be susceptable to hydrauhcally induced pressure locking? Y/N Yes if tius valve is susceptable. see page 2 for sizing equation?
Thermally Induced Pressure Locking in amual screemng usmg the data sheet, is tius valve susceptable to liquid entrapment concems?
YES is vilve bonnet designed such that air will be entrapped?
N/A Was this valve confirmed to be leaking during the time tius valve was last tested?
N/A Has a bonnet vent been added or has the seat or bridge wall been tapped to relieve pressure?
No 2N1121 A has been determmed to be susceptable to thermally induced pressure locking? Ym No Page 1
Calcul:ti:n (2) 2N1121 A Calculation Inout and Outout Summary E5onnet hess (PSIG)
Pb 2235 Lc.edmgConstants (ib0
_L11 0.000897242 Upstream Press (PSIG)
Pu O
1.osdmg Constania (ib0
_Lif 0.062865036 Dwnstrm hess (PSIG)
Pd 0
seat Coefficient (m)
==
0.520792372 Disk Tiuckness (m) 1.38 Average DP DPovg 2235 Mean Seat Diam (m) de 3.75 Duk Constant D
6700307.186 Duk Radius (m) a 1.875 Duk Constant G
10615384.62 Valve Hub Radius (m) b I.12 Moment Mrb
-821.8223093 Hub Length (m)
L 0.4000 Moment Ob 2256.177623 seat Angle (deg) theta 5
Deflect from press & bnds Ybq 1.48534E-05 stem Diam (m)
Datens 1.375 (Deflect due to press )
Ese
-0.116210118 Poissan Ratio v
O.3 (and shear stress
)
Yaq
-6.21516E 05 Modulus of Elasticity E
27600000 (Denect due to )
Pferee 15877.09994 Static Unwedgmg Thnut Fpe 5.980 lbs (Hub Stretch
)
Ystretch 2.91948E 05 Valve Factor tT 0.50 Total deflect due to press (m)
Yq 1.06E-04 Plate Cornants
_c2 0.068870443 o.a.ce dw io seai f & shemnnibem)
Ysw
-7.8914E-08 Plae conmants
,,cJ 0.008354102 o.n idueio.e.trabadnsimabemi Yb.
-2.53691E-03 Pist Cormianu
_cs 0.774882489 o.a.cidmiobub.om - minem>
Yes.npr 2.16629E-08 Plt.e Constants
_co 0.267301135 Toiaiden du i..eai niciam1bem>
Yw
-1.25946E-07 sesisanast force to creau vabo Fs 9933.927615 Urmeatmg forces Fpistem 3318.736755 rver 4302.847441 rp,tsi.ek 8576.05621 i
Requeed Tetal Ferce Fletal i$,540lbs i
Calculation.
Coefficient Of Friction Between Disk & Seat Rings mu= sT*(CO S(thets
- P10/180))/(1 -0T
- SIN (t heta
- PIO/180)))
inu= 0.5207924 AYerage Dp across disks DPng=Pb4(Pu+Pd)/2)
DPavg= 2235.00 Disk Stiffness Constants D=(E*ta3)'(12*(1-v 2))
D= 6700307.2 a
G= E/(2 *(1+v))
G= 1.1E+07 Geometric Influences C2-0.2P(1 -(h/s )* 2 *(l + 2
- LN(a/b)))
C2= 0.0688704 C3= b/(4 *a)*(((b/a )^2 + 1 )* LN(a/b )+(b/a )* 2 - 1 )
C3= 0.0083541 C8=0.5'(1+v+(1-v)*(b/a)^2)
C8= 0.7748825 Page 2
C lculation (2) 2N1121 A C9-(b/ )*(((l+vy2)*LN(a/b)+(((1 v)/4)*(14bla)^2)))
C9= 0.2673011 i
Lt!=(1/64)*((1+4*(b/a)A2 H5*(b/a)^4H(4 *(b/s)^2)*(2+(b/s)^2)*LN(a/h)))
Lil- 0.0008972 L17=0.25*(1 -((1 -v)/4)*(1 (b/s)^4H(b/a)^2 *(1+((1 +v)* LN(a/h)))))
L17= 0.062865 Moment Mrb=(-DPavgan'2/,01)*(LCw(2 *s' b))*(a^2.b^2) _L17)
Mrb= -821.82231 Qb=(DPavg/(2
- b))*(s*2-ba2)
Qb= 2256.1776 Deflection due to pressure and bending Ybg=((Mrb*e 2* C2)/D)+((Qb*a^3* C3yDH(DPavg's"4* L11)/D)
Ybg=
1.5E-05 a
Denection due to pressure and shear stress Ksa=(-0.3*(2*LN(a%)-l+(b/s)^2)
Esa-
-0.1162 Ysq=(Kse*DPavg'a 2)/(t*G)
Ysq=
-6.2 E-05 a
Deflection due to hub stretch P force =P10*(a^2-ba2)*Dravg P force =
15877.1 Ytretch=(Prorce/( PIO* b^2))* 11(2
- E)
Ystretch=
2.92 E-05 Denection due to pressure forces Yq=Ybq+Ysq-Ystretch Yq=
-1.lE-04 Deflection due to seat contact force and shear stress Ysw=-( 1.2 *(a/s )* LN(a/b)* a)/(t
- G)
Ysw=
-7.9 E-08 Denection due to seat contact force and bending Ybw=4a*3/D)*(LC2/_C8)*((a* C9/b)M(a/b)* C3))
Ybw=
-2.5E-08 Denection due to hub compression Yeom pr=( 2
- a
- PIO/( P10* b'2 ))*(U(2
- E))
Yeoenpr=
2.17E-08 Tetti denection due to seat contact force Yw=Ybw+Ysw-Yeompr Yw=
-1.3F 07 1
l Se"t contact force to create Fs Fe=2
- P10*a*Yq/Yw Fs=
seas.o Page 3
j Criculation (2) e 2N1121 A Urse: ting forces Friston=(PIO/4)*(Dstem^2*Pb)
Fpleton=
3318.74 Fvtrt=(PIO*m 2)* SIN (thete*P10/ise)*(2*Pb-Pu-Pd)
Fvert=
asoa.es a
Fpreslock= 2
- Fs *(mu
- COS(theta
- PIO/180)-SIN (theta
- PIO/I so))
Fpreslock-8576.1 i
e Required Total Force FteFpiston+Fvert+Fpreslock+Fpo Flotal=
15540.2 j
1i The actuator is capable of producing 22,iss i6s er rorce.
The force required to overcome pressure locking is 15.540 lbs Actuator Margin is Margin = (Fmax - Fmin) / Fmin
=
42.s %
The limiting component is the Actuator, 25,000 lbs The following provides the corrective actions l'or this valve to alleviate the concerns of:
Perfom calibrated test in the open direction to obtain actual unwedging force and a more accurate PL pullout force required Page 4
i AVMLABLE ACTUATOR THRUST FOR THE OPEN DIRECTION FOR PL/TB 2Hl121A ACTUATOR MODEL/ SIZE / SERIAL NO.:
ROTORK 30NAX186 B3494/B3 OPEN STALLTOROUE AVMLABLE (FT-LBS):
450 (SEE TEST CERTIFICATE)
STEM FACTOR 0.015 ASSUMING 0.15 COEFFECIENT OF FRICTION OPEN VOLTAGE AVAILABLE (%):
86 OPEN VOLTAGE FACTOR 0.86 OPEN HIGH TEMPERATURE FACTOR 1
(NO HIGH TEMP EFFECT)
OPEN TOROUE AVMLABLE = (STALL TOROUE)(VOLTAGE FACTOR ^2)/(HIGH TEMP EFFECTS FACTOR)
OPEN TOROUE AVAILABLE =
450 X
0.86 X
0.86 1
OPEN TOROUE AVAILABLE (FT-LBS) =
333 OPEN THRUST AVMLABLE (LBS)=
22188 121 DADDY.XLS
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Criculati:n (2) 1N11528 Valva information Actuator Information funcuan NI Pwnp B to NC1mps A & D HL !solauen Type EMO unufactwer Sces Wamer Manufactwer ROTORK hem Nwnber 09J-219*
Mode l No 30NAXI 86 Orwing No CNM 1205 000057 RPM 3600 ans class 1s00 PLTB System Calc Inputs ocarRau.
Size 4 00 rA) Rshest Svstem Temp dunns closms i10 Torque Raung Disc Type Flex (B) Lowest system Temp since closing 40 Unit Ef!ie Mean Seat Diem 3 75 (C) Rghest Press on either side smce closwe 2235 Undervoltage Disc Diam 45 (D) Lowest Press for opening on same side as sob Diam 2 24 (C)above o
Systam information Hub Length 04 (E) Lowest Press For opemng on opposite GL8910 Yes Disk Thickness 1 38 side as (C) above on either side since closure 3
Flow Diagram CN-1562-12 Wedge Angle 5
FI Lowest System Temp when closed 40 Coordmates D-5 Stem Diara 1375 (0) Rghest Svsteem Temp when opened i10 Normal Position close Bcanet Vent No Safety Posinon Open Body Matenal SA 182 F316 Req'd To Open Y
Nedge Material 5 A351 Gr CF8M Dp To close 1520 BB or PS Presswe Seal Dp To Open 1520 Dwnstrm Ftess 0
Design Temp 650 Thermal Binding Review in initia? screemng using the data sheet. is this valve susceptable to thermal bindmg concerns?
YES Re temperature dtfrerential is
/ The system design temp is 70 650 is the wedge design flex and the system design temperature 200 F. or less?
No Is wedge design flex and temp differential 100 F or less / or solid and temp differential 50 F or less ?
Yes 1 N1152B has been determmed to be susceptable to thermal binding? Yes / No No Hydraulically Induced Pressure Locking in initu.I screemng usmg the data sheet. is this valve susceptable to rapid depressunzation concems?
YES Was this valve confirmed to be leakmg dunng the time this valve was last tested?
N/A Has a bonnet vent been added or has the seat or bndge wall been tapped to relieve pressure?
No 1 N1152B has been detemuned to be susceptable to hydraulically induced pressure locking? Y/N Ye5 If this valve is susceptable. see pace 2 for sizine equation?
Thermally Induced Pressure Locking in initiil screenmg using the data sheet is this valve susceptable to liquid entrapment concerns?
YES ls volve bonnet designed such that air will be entrapped?
N/A Was this salve confirmed to be leaking dunng the time this valve was last tested?
N/A Has a bonnet vent been added or has the seat or bndge wall been tapped to relieve pressure?
No 1 N11528 has been deiermmed to be susceptable to thermally induced pressure locking? Y!N No Page1
Calculation (2) 1N11528 Calculation Inout and Outout Summarv Bonnet hens (PSIO)
Pb 2235 Londmg constants (ibf)
.L11 0.000897242
'Jpsirsam Press (P510)
Pu 0
Londma onstants (Ibf)
_Ll?
0.062865036 c
Dwnsirm Press (PSIG)
Pd 0
seat coefficient (m) me 0.531692734 Disk Thkness (m) e 1,38 Average DP DPavs 2235 Mean Seat Diam (m) dm 3.75 Disk Constant D
6700307.186 Disk Radius (m) a 1.875 Disk Constant G
10615384.62 Valve Hub Radius (m) b I.12 Moment Mrb -
-821.8223093 Hub 1.ength (m)
L 0.4000 uoment Ob 2256.177623 seat /,ngle (des) theta 5
Nr.ect inxn press a bnds Ybq 1.48534E 05 stem Diam (m)
Desem 1.375 (Deflect due to press )
Esa
-0.11621(>l18 Poisson: Ratio e
0.3 (and shear stress
)
Ysq
-6.21516E 05 Modulus of Elasticity E
27600000 (DeRect due to }
Pforce 15877.09994 Static Unwedgma Thnast Fpe 17.095 lbs (Hub Stretch
)
Ystretch 2.91948E45 Valve Factor VF 0.51 Total deflect uue to press (m)
Yq 1.06E-04 Plate Constants
,C2 0 068870443 Denect du. to sesi t a shearievnbemi Ysw
-7.8914E-08 Plate Constams
_ca 0.008354102 o.n.ct du. io s i ra bnon,inu1bomi Ybw
-2.53691 E-08 see cimiants
.cs 0.774882489 can.c due io bub compr.s.unlibem>
Ycempe 2.16629E 08 Plate Constants
,C9 0.267301135 Toisi oen.c ou. io s.ar snict s.Abeso Yw 1.25946E 07 s.mi comact rocce so cr as yabo Fe 9933.927615 Unscatmg forces Fpisten 3318.736755 rvers 4302.847441 Fpremieck 8791.798929 Required Total Force Ftatal 26,871 lbs i
Calculation Coefficient Of Friction Between Disk & Seat Rings mu= W'(COS(theta
- PIO/180))/(1 -(VF
- SI N(thets
- PIO/180)))
me= 0.5316927 AYertge Dp across disks DP;ve-Pb-((Pu+Pd)/2)
DPasg= 2235.00 Disk Stiffness Constants D=(E*t*3)/(12*(1-v 2))
D= 6700307.2 a
G=E/(2 *(1+ v))
G= 1.1E+07 Geometric Influences C2-0.25 *(1 -(b/s)^2 *(1 + 2
- LN(a/b)))
C2= 0.0688704 C3=b/(4's)*(((b/a)^ 2 + 1 )* LN(a/b)+(b/s)^ 2 -1 )
C3- 0.0083541 CS=0.5 *(1 +v+(1 -v)*(b/s)* 2) 0 8- 0.7748825 Page 2
l Calcul tion (2) 1N11528 C9-(b/I)*(((I +,1/2)* LN(a/h)+(((I -v y4)*( 1 -(b/a)^2 )))
C9= 0.2673011 Li t =(1/64)*((I + 4 *(b/a)^ 2 H 5 *(b/a)^4H(4 *(b/s)*2 )*(2+(b/s)^ 2)* LN(a/h)))
Lil- 0.000e972 Ll7=0.25*(1-((I-sy4)*(I (b/s)^4H(b/s)*2 *(l +((1 +v)* LN(a/b)))))
L17= 0.062865 Moment Mrb=(-DPsv g *a ^2/_01)*((09/(2 *a* b))*(a^2.ba2) _L17)
Mrb= -821.82231 Qb=(DPavg/(2
- b))*(n*2-b^2)
Qb= 2256.1776 Deflection due to pressure and bending Ybg=((Mrban*2* C2FD)+((Qb*a^3* C3)/DH(DPavg'a*4* L11)/D)
Ybg=
-1.5E-05 Def1:ction due to pressure and shear stress Kan=(-0.3 *(2
- LN(a/b)-l +(b/s)^2)
Kan=
-0.1162 j
Ysq=(Kse
- DPas g'a ^2y(t* C)
Ysq=
-6.2 E-05 2
]
Deflection due to hub stretch P f:rce=P10*(n 2-ba2)*DPasg P forre=
15877.1 a
Ytretch=(Pforce/(P10* ba2))* U(2
- E)
Ystretch-2.92 E-05 Deflection due to pressure forces j
Yq=Ybq+Ysq.Ystretch Yq=
-1.l E-04 Deflection due to seat contact force and shear stress 4
i Ysw=41.2 *(a's)* LN(a'b)*a V(t *U)
Ysw=
-7.9 E-08 5
Deflection due to seat contact force and bending f
Ybw=-(a^3/D)*((_C2/_C8)*((a* C9/b)M(alb)* C3))
Ybw=
-2.5E-08 1
i Deficction due to hub compression Yeom pr=(2
- a
- PI(y(F10* b "2 ))*(L/(2
- E))
Yeompr=
2.17E-08 Tot:1 deflection due to seat contact force Yu-Ybw+Yrw-Yeompr Yw=
lJE-07 Seit contact force to create Fs j
Fa=2* P10*a* Yq/Yw Fa=
esas.es Pape 3
Criculation (2) 1N11528 Urseiting forces i
Frisson =&IO/4)*(Datem^2*Pb)
Fristen-3318.74 d
Fuert=(PIO*a 2)* SIN (theta *PI0t:80)*(2*Pb-Pu-PJ)
Feest=
esoa.as a
Fpreslock=2*Fs*(mu*COS(theta *PI(y180)41N(th ta*P10/180))
Fprestorb=
8791.8 Required Total Force Flotak Fpiston+ Fe est+ Fyreslock+ F ro Flota>=
26870.9 The actuator is capable of producing 32,400 lbs errorce.
The force required to esercome pressure locking is 26.87 Ibn Actuator Margin is Margin = (Fmas - Fmin) / Fein
=
20.6 %
The limiting coraponent is the Actusser.
25.000 lbe Tb2 following provides the corrective actions for this valve to alleviate the concerns of:
Perfom calibrated test in the open direction to obtain actual unwedging force and a more accurate PL pullout force required Note: Increase in required actuator opening thrust over its stuctural limit is within 10%
~
Page 4
AVMLABLE ACTUATOR THRUST FOR THE OPEN DIRECTION FOR PL/IB f
1N1152B ACTUATOR MODEL/ SIZE / SERIAL NO.:
ROTORK 30NAX186 B3494/A4 OPEN STALL TOROUE AVMLABLE (FT-LBS):
800 (SEE TEST CERTIFICATE) i STEM FACTOR:
0.015 ASSUMING 0.15 COEFFECIENT OF FRICTION OPEN VOLTAGE AVMLABLE (%):
90 4
f OPEN VOLTAGE FACTOR:
0.9 j
OPEN HIGH TEMPERATURE FACTOR:
1 (NO H6GH TEMP EFFECT) t OPEN TOROUE AVMLABLE = (STALL TOROUE)(VOLTAGE FACTOR ^2)/(HIGH TEMP EFFECTS FACTOR)
OPEN TOROUE AVMLABLE =
600 X
0.9 X
0.9 1
OPEN TOROUE AVMLABLE (FT-LBS) =
486 OPEN THRUST AVMLABLE (LBS)=
32400 l
i 121 DADDY.XLS
) (,h d,Y ll b dn II A t.i.io
. p Cu. tamer corfe
(/Cf Actuator
,/0 /Q.
EncI:surs
/gr7?(
Data / /. '[. 7*6
[f09////[fg, Type f ygg, /,
Model
$g
~
Job no.
4 Liectrical check Performance details Cucuit continuity checked to di.iyram
})o ')/. M. c_
Condition Open Closed Control oscuit lla.hed at Jgh tighi ron ib/f t d. 2 amp ib/li
.d. 2, A O P 1 potentiometer value obtained
/p8#,
M in torque setting joo
'[. 0
._Je o
'f.O h(79
,fcp. O gim
,jf. g A O P.2 relays operaicts at Sialt j
Ph ir= que sci at g,'
jt,/,'g, Costorners voiearv ff((
v o
Hg Ics volta'N
//MG V
60 lir,j Ph j\\ F{(
inspected by 1
Motor Details Motor check Second stage operators
[ff07 Speed (W/G ratio)
Type W/S No Make g/
Poles 2.
Finat ditcciion of output clock /anticlock Speofication g
w/ gear rasio yg-l Bore and keyway dimensions Thermostat trip Flashed at
[. T/V Actuator imid gearbox bght run current Insulation cla s N.
Actuator speed
'l'2,lQ(,(f)(M Inspected by Mechanical check Final inspection Compiled by
/ Isl@ected by fy A.4. p (u G-g
/[
L/ switch ratio
[,.[
Cable entrics Leadscrew j7 Drive sleeve retainer
,$g) A )(
[. h, Turn set at
- 9. t o Drive steeve J O A )(.
[kk}b Direction of actuator clock /fbrMh4 Cover tulic lland eaf fatiO l-(
f ]f Stub shalt/ pedestal D
Inspected by h/p,
Tags Special paint g4 kg7 Clearance by inspection supervisor l
Special labets Misce'raneous Om.nle impection (if applicehle)
1 l
Criculation (2)
- 2N1152B Valve information Actuator information Functacn N1 Pu ip D to NC Imps A A D HL 1solauen Type EMO
'Annufacturer Borg Wamer Manufacturer ROTORK llem Number 09L219' Model No 30NAX1 86
'AswmgNo CNM 1205 00 0087 RPM 3600 Press cims 1500 PLTB System Calc Inputs Gear Ratso Las 4 00
/A) Rshest System Temp dunna closins llo Torque Ratmg Disc Type Flex (B) Lowest System Temp smce closmg 40 Umt Effic.
Mean Seat Diam 3 75
/C) Highesi Press on either side sure closure 2235 Undervoltage Dise Diam 45 (D) Lowest Press for opemns on same side as sub Diam 2 24 (C) above O
System Information l
Hub Length 04 (E) Lowest Press For operung on opposite OL 89-10 Yes Disk Tiuckness 1 38 side as (Cl ahove on either side smce closure 0
Flow Diagram CN.25621 Wedge Angle 5
(F) s.owest System Temp when closed 40 Coordmates D5 i
Stem Diam i375 (G) Rahest Systeem Temp when opened i10 Normal Position 0
Bonnet Vent No Safety Position Open
]
Body Matenal SA 182 F316 Req'd To Open Y
wedge Metenal SA351 Or CF8M Dp To close 1520 BDorPS Pressure Seal Dp To Open 1520 Dwnstrm Press 0
l Dessam Temp 650 Thermal Binding Review l
ln initial screcrung usmg the data sheet, is tius valve susceptable to thermal bindmg conwems?
YE5 The temperature dtNerential is
/ ne system design temp is 70 650
!s the wedge design flex and the system design temperature 200 F. or lesa?
No is wwige design flex and temp diferential 100 F or less / or solid and temp diNerential 50 F or less ?
Yes 2N1152B has been determmed to be susceptable to thermal bindmg? Yes / No No Hydraulically Induced Pressure Locking in mitid screenmg usmg the data sheet, is this valve susceptable to rapid depressurtzation concerns?
YES Was this valve confumed to be leaking durmg the time this valve was last tested?
N/A lias a honnet vent been added or has the seat or bndge wall been tapped to relieve pressure?
No 2N1152B has been determmed to be susceptable to hydrauhcally induced pressure locking? Y/N Yes If this valve es susceptable. see pare 2 for sizmg equation?
l Thermally Induced Pressure Locking in initial screenmg usmg the data sheet, is this valve susceptable to hquid entrapment concerns?
YES la velve bonnet designed such that air will be entrapped?
N/A Was this valve confirmed to be leaking during the time this valve was last tested?
N/A lias a bonnet vent been added or has the seat or bndge wall been tapped to relieve pressure?
No 2N1152B has been determmed to be susceptable to thermally induced pressure locking? Ym No Page 1 l
l l
Criculition (2) 2N1152B Calculation Inout and Outout Summary Bonnet hans (PSIO)
Pb 2235 Loadmg Comtants (ibf)
_L11 0.000897242 Upstream Press (PSIO)
Pu 0
Londmg Constants (Ibf)
_Ll?
0.062865036 j
Dwnsum Press (PSIO)
Pd 0
Seat Coefficient (m) mu 0.520792372 Duk Tiuckness (m) e 1.38 Average DP DPavs 2235 Mean Seat Diam (m) den 3.75 Disk constant D
6700307.186 Duk Radius On) a 1.875 Dir.k Constant G
10615384 62 Valve Hub Radius (m) b 1.12 Moment Mrb 821.8223093 Hub length (m)
L 0.4000 Moment Qb 2256.177623 Seat Angla (des) theta 5
Deflect from rrens & bndg Ybq
-1.48534E45 stem Diam (m)
Dstem 1.375 (Deflect due to press )
Kaa
-0.116210118 Poisson:Raue v
0.3 (and shear sness
)
Ysq
-6.21516E 05 Modulus of Elasucny E
27600000 (Deflect due to )
Pforce 15877.09994 Staus Unwedgma Thrust Fpe 15.461 lbs (Calibrated)
(Hub Stretch
)
Ystretch 2.91948E-05 Valvs Factor VF 0.50 Total deflect due to pressc m)
Yq
.l.06E-04 Plate Constants
_C2 0.068870443 Denect dus e semi f & sheanm1bCm>
Yew
-7.8914E-08 Plate Constants
,c3 0.008354102 o.n eu. io sesi f & bndnralbem>
Ybw 2.53691E-08 Plate Constanis
_Cs 0.774882489 o.a.<t au. io hun mpr.asi.vibem>
Ye.mpr 2.16629E-08 Plate Constants
,C9 0.267301135 Ya 4.n au. m s.si n= antbemi Y-
.l.25946E 07 sent aantact force e ersaw Yabo Fs 9933.927615 Umeaung forces Fp6 sten 33IB.7367$5 rvers 4302.847441 Fpresleck 8576.05621 n ared T. tai r.ru ri. tai 25,021 lbs i
Calculation Coefficient Of Friction Between Disk & Seat Rings mu=VF*(COs(theta
- PIO/180))/(1 -(VF* SIN (theta
- PIO/Is0)))
me- 0.5207924 Avsrtge Dp across disks DPatr=Pb-((Pu+ Pd)/2)
DPavg= 2235.00 Disk Stiffness Constants D-(E*t*3)/(12*(1-v 2))
D= 6700307.2 a
G= E/(2 *(l + + ))
G= 1.1E+07 Geom:tric Influences C2=0.23*H.(b/a)*2 *(1 +2
- LN(a/b)))
C2= 0.0688704 C3=b/(4 *a)*(((b/m)^2+ 1)* LN(a/h)+(b/a)a2-1)
C3= 0.0083541 C5-0.550 +v+(1 -v)*(b/a)^2 )
08= 0.774ss25 Page 2
a C:lculation (2) 2N1152B l
C9-(b/s)*(((1 +v)/2)* LN(a/h)+(((1 -vy4)*(1 -(b/a)^2)))
09= 0.2673011 L11 =(1/64)* dl +4 *(b/s)^2 H5 *(b/a)^ 4)-((4 *(b/a)^ 2)*(2+(b/s)a2)* LN(a/b)))
L11= 0.0008972 L17-0.25 *(1 -((1 -s y4)*(1 -(b/s)^4H(b/a)^2 *(1+((t h)* LN(a/h)))))
L17= 0.062865 Moment Mrb=(-DPavg*a ^2/_C8)*((_C9/(2*a* b))*(a^2-ba2) _L17)
Mrb= -821.82231 I
Qb=(DPasg/(2*b))*(a*2-b^2)
Qb= 2256.1776 Deflection due to pressure and bending Ybg=((Mrb*a*2* C2FD)+((Qb*a 3* 03)/DM(DPavgas*4* L11VD)
Ybg=
-1.5E-05 a
Deficction due to pressure and shear stress Kan=(-0.3*(2*LN(a/b)-l+(b/s)^2)
Kas-
-0.1162 Yaq=(Kas* DPas g*a^2)/(t*G)
Yaq=
-6.2 E-05 Deflection due to hub stretch P force-P10*(a^2-ba2)*DPas P force-15877.1 Yc' retch =(Pforce/(P10* b'2))* u(2
- E)
Ystretch-2.92E-05 Deflection due to pressure forces Yq=Ybg+Ysq-Ystretch Yq=
1.lE-04
{
Deficction due to seat contact force and shear stress i
Ysw=41.2 *(a/s)*l.NWb)*ay(t*G)
Ysw-
-7.9E-08 Deficction due to seat contact force and bending Ybw=4a^3/D)*((_C2/_C8)*((a* L9/b)M(a/b)* C3))
Ybw=
-2.5 E-08 Deflection due to hub compression Yeomp r=(2
- a
- PI(y(P10* b ^ 2 ))*(U(2
- E))
Yeompm 2.17E418 Tet:1 deficction due to seat contact force Yw-Ybw+Ysw-Yeompr Yw=
-lJ E-07 Seit contact force to create Fs Fe=2*PIO*a*Yq/Yw Fe=
sess.es Page 3
Calculation (2) 2N11528 Unse-ting forces Fpiston=(PIO/4)*(Ds'em"2*Pb)
Fpiston=
3318.74 Fvert=(PIO*m 2)*stN(theta *PIO/180)*(2*Pb-Pu-Pd)
Fvert=
esoa.es a
Fpreslock=2
- Fs*(mu* COS(thets* P10/180)-SIN (theta
- P10/180))
Fpreslock-8576.1 Required Total Force Flosak Fpistun+ Fvert + Fpreslock+ Fro Flotal=
25021.2 I
l The actuator is capable of producing 27,119 :bs er rorce.
a j
j The force required to overcome pressure locking is 25.02 abs 4
i Actuator Margin is Margin = (Fmax - Fmin) / Fein l
8.4v.
i j
The limiting component is the Actuator.
25.000 ibs i
The following provides the corrective actions for this valve to alleviste the concerns of:
I None Required i
Note: Increase tn requtred actuator opemng thrust over its stuctural limit is within 10%
Page 4
i l
AVMLABLE ACTUATOR THRUST FOR THE OPEN DIRECTION FOR PL/TB 2N1152B ACTUATOR MOD'!L/ SIZE / SERIAL NO.:
ROTORK 30NAX186 B3494/B1 OPEN STALL TOF QUE AVMLABLE (FT-LBS):
550 (SEE TEST CERTIFICATE)
STEM FACTOR 0.015 ASSUMING 0.15 COEFFECIENT OF FRICTION l
OPEN VOLTAGE AVMLABLE (%):
86 OPEN VOLTAGE FACTOR 0.86 OPEN HIGH TEMPERATURE FACTOR 1
(NO HIGH TEMP EFFECT) l OPEN TOROUE AVMLABLE = (STALL TOROUE)(VOLTAGE FACTOR *2)/(HIGH TEMP EFFECTS FACTOR) i OPEN TORQUE AVAILABLE =
550 X
0.86 X
0.86 1
OPEN TOROUE AVAILABLE (FT-LBS) =
407 OPEN THRUST AVAILABLE (LBS)=
27119 l
121 DADDY.XLS 1
N
.~
j ROTORK ACTUATOR CERTIFICATION DATA SHEET 2 tJZ /328 Van WW
)
NN/<5V g
CLOSE TEST DATA
\\
{
OPEN 'IT5r DATA Peak
- Locked Vab-rms Actual As found CSF Peak
- Locked Vab-rms Actual As Found Rotor
- Voltage 5 (A.lbs)
Rotor
- Voltage %
(R.lbs)
(See below) gP (See below) step 10.5.4 step 10.5.4 glPf V
at
{pl7 567 6(A 9 R lo
%~~
S zro 537 5 70 99.t$
/t
'7 9.d N
s9s sys
+ss
<79.vX
""dl 2ay si v 1/s?
ia* 3 a
Actual Voltage % = Tested Voltage (Vab'-rms) 575 V CthSE'IT5f DATA l
OPEN 'IliST DATA l
Step Torque Torque Output 5
Spring Pack Motor 5
Torque C mt Spring Pack Motor Switch (R-Ibs)
Diff Displacement Power Diff (A-lbs)
Diff Displacement Power Diff Setting (inch) e CST (inch)
@ CST O
Mu O
Mu e
Mu e
Mu CST
- CST CSr*
'79 8/?
3/'7 g
. /3 9' 7 99 toa.s MAX (5) 3do I
.t2?
y%
g9p 7 2t$, jgy fy 7jy
/
MAX (5) 5 3). g y g
w/ thrust 303 So3 4
962 963
.109
.(09 61 59
.to9
./o?
90 9I4 9l1 08 T 5 66 op p
.o58,ogg 6 VS-go_,,4 2
152 /53 oto
. o VI t/C 1V5 g
.069 8
Z
//9
- @ g 2341
//3
/13
.038 2
- 8. / 8
Cdculati:n (2) 4 i
1N1009A Valva Information Actuator Information 1
i Funcuan NV Cold Les injecuan Isolauan Type EMO tlanufacturer Borg Wamer Manufacturer ROTORK
! tem Number 093 202*
Model No 30NAX1 86 Drawmg No CNM 1205 00 0083 RPM 3600 Pre = Cians iS00 PLTB System Calc Inputs Gear Raua j
sue 4 00
/A) Rghest System Temo dunna closme 110 Torque Raung Disc Type Flex
/B) Lowest svatem Temo smce closma 40 Umt Effic.
%1ean Seat Diam 3 75 rC) H>ahest Press on either side smce closure 2700 Undervoltage Duc Diam 45 fD) Lowest Press for opemns on same side as aub D=
2 496 fC) above o
System Information Hub Length 0403
/E) Lowest Press For opemns on opposite GL 89-10 Yes Disk T1uckness 1 08 side as (C) above on either side smce closure 0
Flow Diagram CN-156210 Wedge An6 e 5
IFl Lowest Svetem Temp when closed 40 Coordmates D-9 1
stem Diam I375
/G) Rghest Systeem Temp when coened l l10 Normal Position close Bonnet Vent No Safety Postuon Open Body Matenal SA 182 F316 Reg'd To Open Y
Wedge Matenal SA351 Gr CF8M Dp To close 1935 BB or PS Pressure Seal Dp To Open 2700 Dwnstrm Fvens o
Desian Temp 100 Thermal Binding Review in irutail screcrung using the data sheet. is this valve susceptable to thermal binding concems?
YES The temperature dMerential is
' ne system design temp is 70 300
!s the wedge design flex and the system design temperature 200 F, or less?
No is wedge design flex and temp differenual 100 F or less / or solid and temp differential 50 F or less ?
Yes 1 N1009 A has been detemuned to be susceptable to thermal bindmg? Yes / No No flydrculically Induced Pressure Locking in uutsal screenmg usmg the data sheet, is this valve susceptable to rapid depressurization concerns?
YES Wu this salve confirmed to be leaking during the time this valve was last tested?
N/A flas a bonnet vent been added or has the seat or bridge wall been tapped to reheve pressure?
No 1 N1009A has been determmed to be susceptable to hydrauhcally induced pressure loclung? Y/N Yes l
If thss valve is susceptable, see page 2 for sizme equation?
l T!nrmally Induced Pressure Locking In irutial screenmg usmg the data sheet. is this valve susceptable to hquid entrapment concems?
YES is vr.lve bonnet designed such that air will be entrapped?
N/A j
Was this valve confirmed to be leaking during the time this valve was last tested?
N/A i
Has a bonnet vent been added or has the seat or bridge wall been tapped to reheve p. essure?
No 1 N1009A has been detemuned to be susceptable to thermally induced pressure locking? Ym No Page1
Calculation (2) 1NIOO9A Calculation Inout and Outout Summarv Barmet Press hSIO) l Pb 2700 tendesConstants ob0 Lt1 0.000444475 l
Upstream Press (PSIO)
Pu 0
1.oadmg Constants Ob0
.L17 0.045470485 i
Dwnstrm Press (PSIO)
Pd 0
seat CoefLeient (m) mu 0.520792372 Disk Thickness (m) 1.08 Average DP DPevs 2700 Mean seat Diam (m) dm 3.75 Disk Constant D
3139871.223 Disk Radius (m) a 1.875 Disk Constant G
10615384 62 i
Vdve Hub Radms (m) b 1.248 Moment Mrb
-652.7338386 j
Hubl.ength (m)
L 0.4030 Mornent Ob 2118.159736
[
Seat Angle (deg) theta 5
Deflect from press & bnds Ybq 1.80732E 05 i
l Siem Diam (m)
Dstem 1.375 (Deflect due to pren )
Ese 0.077146842 Poisson s Raua 0.3 (and shear stress
)
Yng
-6.41712E-05 l
Modulus of Elasucity E
27600000 (Deflect due io )
Pferee 16609.37008 l
Static Unwedgmg Thrust Fpe 14,746 lbs (Hub Stretch )
Ystreteb 2.47822E.05 Valve Factor VF 0.50 Total deflect due to press (m)
Yq
-1.07E 04 l
Plde Constants
_C2 0.0490742 Desect due to sees f a sheinmnbem)
Yew
-8.02608E.08 Pise Constants
_cs 0.005063497 o.a tdu.io Iabne sabemi Ybw
-3.03635E 08 Plae Constants
_Cs 0.805058176 o.a.cieu.io bub.ompr.abomi Yeompr 1.75779E 08 Plate Constants
_cp 0.240989842 Towden aue.
.mciamnbemi iw 1.28202E 07 seen samase force to cr. air YOb0 Fs 9835.066193 i
1 Unsemma forces Fpwee 4009.212187 Fvert 5198.070734 Fprenneck 8490.708184 Required Total Force Flotal 24,426 lbs Calculation Coefficient Of Friction Between Disk & Seat Rings mu=VF'(COS(theta
- PIO/l 80)y(I QT
- SI N(theta
- P10/180)))
mu= 0.5207924 Averrge Dp across disks DP:v g= Pb-((Pu+ Pd)/2)
DPavg= 2700.00 Disk Stiffness Constants D=(E*t^3)/(12*(1.v 2))
D= 3139871.2 a
G= F/(2 *(I+v))
G= t.lE+07 Geometric Influences C2-0.25 *(1 -(b/s)^2 *(l +2 ' LN(a/b)))
C2= 0.0490742 C3= b/(4
- a)*(((b/a)^ 2 + 1 )* LN(a/b)+(b/s)^2 1 )
C3= 0.0050635 C8=0.C*(1+v+(1-v)*(b/s)^2) 08= 0.8050582 Page 2
Cricutation (2) 1NIOO9A C9-(Wa)*(((1 +v)/2 )* LN(a/h)+(((1 -v)/4)*(1 -(Wa)^2 )))
09= 0.2409898 Li t =( 1/64)*((1 + 4 *(ble)^2 H 5 *(b/s)^4 H(4 *(b/s)^2)*(2 +(Wa)^2)* LN(a/h)))
Lil- 0.0004445 Ll 7-0.25 *(14(I-v)/4)*(14Ws)^ 4 H(b/a)*2 *(1 +((1 +v)* LN(a/b)))))
Ll7= 0.0454705 Moment Mrb=(-DPavg*a^2/_Cs)*((,C9/(2*a*b))*(a*2-b^2) _Ll7)
Mrb= -652.733s4 Qb=(DPavg/(2
- b))*(a^2-b"2)
Qb= 2118.1597 Deflection due to pressure and bending Ybg=((Mrb*a 2* C2)/DF((Qb*a^3* C3)/D)4(DPavg'a*4* L11)/D)
Ybg=
-1.8E-05 a
Deflection due to pressure and shear stress Kan=(-0.3*(2*LN(a/b)-l+(b/s)*2)
Esa=
-0.0771 Ysq=(Ese* DPavgaa*2)/(t*G)
Ysq=
-6.4E-05 Deflection due to hub stretch P fone=P10*(a*2-b^2)*DPsvg P force =
16609.37 Ydrueb=(Pforce/(PIO* b ^2))* 11(2
- E)
Ystretch=
2.48E-05 Deflection due to pressure forces Yq=Ybq+Ysq Ystretch Yq=
-1.lE-04
{
Deflection due to seat contact force and shear stress Ysw=-(1.2 *(a/a)* LN(a/h)*a nt*G)
Ysw=
-8.0E-08 Deflection due to seat contact force and bending Ybw=4a*3/D)*((_C2/_C8)*((a* 09/b)H(alb)* C3))
Ybw=
-3.0E-08 Deficction due to hub compression Yeompr=(2 *a* PI()/(PIO* b^2))*(l>(2
- E))
Yeompr=
1.76FAS Tctil deflection due to seat contact force Yw=Ybw+Ysw-Yeompr Yw=
1.3E-07 Sc;t contact force to create Fs Fe=2
- PIO*a* Yq/Yw Fe=
sess.or Page 3
Calculation (2) 1NIOO9A Unseiting forces FpistonWP10/4)*(Dstem^2*Pb)
Fpiston=
4009.21 Fvart=(PIO*a 2)* SIN (tiwta*P10/180)*(2*Pb-Pu-Pd)
Fvert=
sies.o?
a Fpreslock=2
- Fs *( mu
- COS(theta
- PIO/180FSIN(theta
- P10/I so))
Fyreslock=
8490.7 Required Total Force i
Ftotal=-Fy6ston+ Fs ert+ Fpnslock+ Fro Ftotal=
24425.6 i
j The actuatoris capable of producing 25,600 lbs er rorce.
i i
i l
The force required to overcome pressure locking is 24,426 8bs I
]
Actuator Margin is Margin = (Fmax - Fmin) / Fmin j
=
4.s%
l The limiting component is the Actuator.
25,000 lbs 1
l Ths following provides the corrective actions for this valve to alleviate the concerns of:
5 l
Perfom calibrated test in the open direction to obtain actual unwedging force and a more accurate PL pullout force required 3
s 1
i i
i a
i 1,
I' l
Page 4
AVMLABLE ACTUATOR THRUST FOR THE OPEN DIRECTION FOR PL/TB 1N4000A ACTUATOR MODEL/S!ZE/ SERIAL NO.:
ROTORK 30NAX1 86 B3494/A7 OPEN STALL TOROUE AVMLABLE (FT-LBS):
000 (SEE TEST CERTIFjCATE)
STEM FACTOR-0.015 ASSUMING 0.15 COEFFECIENT OF FRICTION OPEN VOLTAGE AVMLABLE (%):
80 OPEN VOLTAGE FACTOR; 0.8 OPEN HIGH TEMPERATURE FACTOR 1
(NO HIGH TEMP EFFECT)
OPEN TOROUE AVMLABLE = (STALL TOROUE)(VOLTAGE FACTOR'2)/(HIGH TEMP EFFECTS FACTOR)
OPEN TOROUE AVMLABLE =
600 X
0.8 X
0.8 1
i OPEN TOROUE AVMLABLE (FT-LBS) =
384 i
i OPEN THRUST AVMLABLE (LBS)=
25600 e
d I
i 9
90ADDY.XLS
un n.tJO fi
, Cust:mer ced]
Test cs.rtificate g(*/
Actuitar lfy[ - G) l A
sah no.
,Gp9sk/f.
Enclosuro r pe
//[(
v ivM. /.
Date
//, f.
h l
/A)1^o0 78 yodal SNif
~
4 Electrical check 1
p Circuit continuity checked to disgr.un I
Qg.)/- NO-C Performance details
}
Control circuit flashed at Condetion
(
)4'[e Open A.O.P.1 potentiometer value obtained Light run Cio>cd gt.DAQ ib/f
,7./ amp A O P.2 relays operated ai tb/f t '
1,.
Max torque setting
[o
[*, d
,300 c
Customers voltage
' 8[
- Stail
[O He d
[gG g//.O
[(rO IJ v
Ph i Torque set at A/,j'g
[1e5I voit09"
//,' f l
A
//f0 v
.i O Hz,3 Ph l 4
i,
[ Inspected by j
' Motor Details
['dff[lO
! otor check M
W/S No
$~f0 $~
. Speed (W/G ratial Second stage operators Make g[gv Type Pcles
[
' Specification
[
//() /
[w_nal direction of output Fi Thermostat top
, W/gcar ratio clock /anticlock Flashed at Bore and keyway dimensions
]nsulation class
[.
/.ph,
Actuator speed Actuator and gearbox light run current 73 ((((/L7 Inspected by
/
l Machanical check
_~
L/ switch ratio
,((
[ Final inspection Leadscrew Compiled by I
Cable entoes
, -9 Inspected by
~2 Turn set at g,fgp p h g
[
, (.
(([,( -
Drive sleeve retainer 2o
,fgA/
Direction of actuator
[
Dr ve sleeve
'/M
/
Hand gear ratio clock /N-o /Q g
/- /
Cover tube
.hgb Inspected by gj Stub 5haf t/ pedestal i
[g kiIM 95 t
Clearance by inspection supervisor L specia p.>ini
]g gQ7 i
t
~
t special sabeis s
F..inspvcsion i,appiicasici 2
a
'q Miscello.mous f
~
f-
C11culation (2) e '2N1009A Valva information Actuator information Funcuen NV Pump Cold Les Irgection Isolanon Type EMO unufacturer Borg Wamer Manufactwer ROTORK
' tem Number 091-202' Model No 30NAXi B6 Drawn:3 No CNM 1205 00 0083 RPM 3600 Press eios 1500 PLTB System Calc Inputs Gear Rauo Size 4 00 (A) Highest System Temo dunna closms i10 Torque Ratmg Dias Tvpe Flex (B) Lowest System Temp smco clasms 40 Umt EfLc.
Mean Sea Diam 3 75 (C) Highest Press e enher side smee closure 2700 Undervoltage Disc Diam 45 (D) Lowest Press for opemns on same side as Hub Dum 2 496 (C) above 0
9yStam Information Hub Length 0403 (E) Lowest Press For openmg on opposite GL 3910 Yes Disk Tluckness 1 08 side as (C) above on enher side smce closure 0
Flow Diagram CN-2562-10 Wedge Angle 5
(F) Lowest Svetem Temo when closed 40 Coordinates C-9 Stem Diam I375 (0) Highest Systeem Temp when opened i10 NormalPosiuon close Bonnet Vent No safety Position Open Body Attenal SA 182 F316 Req'd To Open Y
Wedge Matenal SA351 Gr CT8M Dp To close 1935 BBorPS Presswe Seal Dp To Open 2700 Dwnstrm Press 0
Design Temp 100 ThIrmal Binding Review in initiil screening using the data sheet, is this valve susceptable to thermal bindmg corwerns?
YES lhe temperature differential is
/ The systern design temp is 70 300 is the wedge design flex and the system design temperature 200 F. or less?
No is wedge design flex and 3 yp Merential 100 F or less / or solid and temp ddrerential 50 F or less ?
Yes 2Nl009A has been detemuned to be susceptable to thermal bmdmg? Yes / No No flydreulically Induced Pressure Locking in mitial screenmg usmg the data sheet. is this valve susceptable to rapid depressuruation concems?
YE5 Was tius valve confirmed to be lealung during the tune this valve was last tested?
N/A ths a bonnet vent been added or has the seat or bridge wall been tapped to relieve pressure?
No 2N1009A has been determmed to be susceptable to bydraulically induced pressure lockmg? Y,N Ye5 If this salve is susceptable. see page 2 for sizme equation?
Th:rmally Induced Pressure Locking in irutial screenmg usmg the data sheet is this valve susceptable to liquid entrapment cotwems?
YES la vilve bonnet designed such that air will be entrapped?
N/A Was this valve confirmed to be leakmg durmg the tune this valve was last tested?
N/A Has a bonnet vent been added or has the seat or bndge wall been tapped to reheve pressure?
No 2N1009A has been detemuned to be susceptable to thermally induced pressure locking? yen No Page 1
1 f,
Cciculati:n (2)
~
2NIOO9A Calculation Inout and Output Summary j
Bonnet Press (PS10)
Pb 2700 Londmg Constants (Ibf)
_ Lit 0.000444475 Upstream Press (PSIG)
Pu 0
Loadmg Constants (1b0
.Ll7 0.045470485 Dwnstrm Press (PSIO)
Pd 0
seat Coefficient (m) me 0.520792372 Disk 71uckness (m) 1.08 Average DP Drevs 2700 Nican Seat Diam (m) de 3.75 Disk Constant D
3139871.223 Disk Radms (m) e 1.875 Disk Constant C
10615384.62 valve Hub Radms (m) b 1.248 Moment Mrb
-652.7338386 j
Hub Length (m)
L 0.4030 Moment Qb 2118.159736 I
seat Angle (deg) theta Deflect from press a bnds Ybq
-1.80732E 05 stem Diam (m)
Dstem 1.375 (Deflect due to press )
Kna
-0.077146842 Poisson's datio v
0.3 (and shear stress
)
Ysq
-6.41712E-05 Niodulus of Elasticity E
27600000 (Deflect due to )
Pferee 16609.37008 l
Static Unwedsme nrust Fp.
I3.352 lbs (Calibrated)
(Hub Stretch
)
Ystretch 2.47822E 05 valve Factor VF 0.50 Total deflect due to press (m)
Yq
-I.07E-04 Plate Constants
_C2 0.0490742 Dec.ct du to s Ia sheenn1brmi Ysw
-8.02608E-08 Plate Cunstania
_Cs 0.005063497 o.a ieu.io irannone.abemi Yb.
3.03635E-08 Plate Constanu
_cs 0.805058176 o.a.cido. io hub sonwmademi Ye.mpe 1.75779E 08 Plate Constants
_c9 0.240989842 toui4.n 4 io==.ni.ienabe=>
Yw
-1.28202E-07
$est sonenet force to ensa. Yabo Fs 9835.066193 Unscatma forces Fpi.e.m 4009.212187 Fver 5198.070734 Fp.esack 8490.708184
)
l l
as,wred T. tai r.rce rt.t.
23,032 lbs l
Calculation Coefficient Of Friction Between Disk & Seat Rings mu=VF*(COS(theta
- PIO/l 80)V(I-0T
- SIN (thets* PIO/180)))
me= 0.5207924 AY2r:ge Dp across disks DPa g=Pb-((Pu+Pd)/2)
DPavg= 2700.00 l
l Disk Stiffness Constants 1
(>=(E*t^3)/(12*(1-v 2))
D= 3139871.2 a
G= E/(2 *(1 +v))
G= 1.lE+07
?
Geometric Influences C2-0.23 *(1 -(b/s)^ 2 *(1 + 2
- LN(a/b)))
C2= 0.0490742 C3= W(4
- a)*(((Wa)^ 2 + 1 )* LN(a/by+(b/s)^ 2 -1 )
C3= 0.0050635 C5-0.5*(l +v+(1 -v )*(b/s)^ 2 )
Cs= 0.8060582 Page 2
J Cilculation (2)
{
2NIOO9A C9=(b/s)*(((1 +v)/2)* LN(a/h)+(((14 )/4)*(1 -(b/s)^2)))
09= 0.2409898 L11 =( t /64)*((1 +4 *(b/s)^ 2)-(5 '(b/a)^ 4)-((4 *(b/a)^2)*(2 +(b/s)^ 2)* LN(a/b)))
L11= 0.0004445 L17=0.25 *(1 -((1 -v)/4)*(1 -(b/a)^ 4H(b/s)^2 *(1 +((1 +v)* LN(a/b)))))
Ll7= 0.0454705 M: ment Nlrb=( DPavg's^2/_C8)*(LC9/(2*a*b))*(a*2-b^2) _L17)
Mrb= -652.73384 Qb=(DPsvg/(2
- b))*(a*2-b^2)
Qb= 2118.1597 Def1:ction due to pressure and bending 1
Ybq=((Af rb*a^2* C2)/D)+((Qb*a^3* C3)/DH(DPavgas^4* L11)/D)
Ybg=
-1.8E-05 Deflection due to pressure and shear stress Ksa=(-0.3 *(2
- LN(a/h)-l+(b/a)^2)
Kan=
-0.0771 YaqMKas* DPav g *a^2)/(t *G)
Yaq=
-6.4FA5 Deflection due to hub stretch P force =P10*(a^2-b^2)*DPas g P force =
16609.37 i
Ys: retch =(Pforce/(P10
- b ^ 2))* U(2
- E)-
Ystretch=
2.48E-05 Deflection due to pressure forces i
Yq=) bq+Ysq-Ystretch Yq=
-1.1E-04 Deflection due to seat contact force and shear stress i
i Ysw=-(1.2 *(a/a)* LN(a/h)*ay(t *G)
Ysw=
-8.0E 08 Deflection due to seat contact force and bending Ybw=-(a^3/D)*(LC2/_C8)*((a* 09/b))-((a/b)* C3))
Ybw=
-3.0 E-08 Deflection due to hub compression YeomprM2 *a
- PIO/(PIO* b^2 ))*(U(2
- E))
Yeompr=
1.76E-08 Tctri deflection due to seat contact force Yw-Ybw+Ysw-Yeompr Yw=
- 1.3 E-07 Se:t contact force to create Fs Fe=2*PIO*a*Yq/Yw Fe=
sess.o?
Page 3
Calculation i2) e 2NIOO9A
}
Unseatingforces,
j Fpiston=(PIO/4)*(Datem 2*Ph)
Fpiston=
4009.21 a
Fwrt=(P10
- a^2)* SIN (theta
- P10/180)*(2
- Pb-Pu-Pd)
Fvert=
sies.or l
Fpreslock=2
- Fs*(mu* COS(theta
- PIO/180)-SIN (theta
- P10/1 so))
Fpreslock=
8490.7 j
Required Total Force 1
4 Ftotal -Friston+Fver1+Fyreslock+Fpo Ftotal=
23031.6 d
i l
The actuator is capable of producing 25,600 ibs er rorce.
i 1
The force required to overcome pressure locking is 23.032 lbs 1
Actuator Margin is Margin = (Fmax - Fmin) / Fmin
{
=
11.2 %
i i
j The limiting component is the Acts. tor.
27.000 16s The following provides the corrective actions for this valve to alleviate the concerns of:
None Required 1
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I Page 4
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AVMLABLE ACTUATOR THRUST FOR THE OPEN DIRECTION FOR PL/TB a
2N1000A ACTUATOR MODEL/ SIZE / SERIAL NO.:
ROTORK 30NAX186 B3494/A3 OPEN STALL TOROUE AVMLABLE (FT-LBS):
600 (SEE TEST CERTIFICATE)
STEM FACTOR:
0.015 ASSUMING 0.15 COEFFECIENT OF FRICTION OPEN VOLTAGE AVMLABLE (%):
80 OPEN VOLTAGE FACTOR:
0.8 OPEN HIGH TEMPERATURE FACTOR:
1 (NO HIGH TEMP EFFECT)
OPEN TOROUE AVMLABLE = (STALL TORQUE)(VOLTAGE FACTOR ^2)/(HIGH TEMP EFFECTS FACTOR)
OPEN TOROUE AVMLABLE =
800 X
0.8 X
0.8 1
OPEN TOROUE AVMLABLE (FT-LBS) =
384 OPEN THRUST AVMLABLE (LBS)=
25600 9 DADDY.XLS
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Criculation (2) t.
1N1010B Valva information Actuator Information Function NV Pump Cold Leg injecuan Isolauon Type EMO Nianufactwer Borg Wamer Manufactwer ROTORK ltem Number 091-202*
Model No 30NAX1 86 Omvmg No CNM 1205 00-0083 RPM 3600 nres Cims 1500 PLTB System Calc loputs Gear Rauo Size 4 00 (A) Rghest Svstem Tema dunns closme Ito Torque Ratmg Disc Type Fles eB) Lowest System Temp smce closmg 40 Urut Effie Nican Seat Diam 3 75 (C) Rghest Press on either side smce closwe 2700 Undervoltage Disc Diam 45 (D) Lowest Press for opemns on same side as sub Diam 2 496 (C) above o
System information Hub Length 0 403 (E) Lowest Press For operung on oppoone GL 8910 Yes Disk T1uckness 1 08 side as (C) shove on either side smce closwe 0
Flow Diagram CN 1562-10 Wedge Angle 5
(F) Lowest System Temp when closed 40 Coordmates D-6 Stem Diam 1 375 (G) Rghest Systeem Temp when opened i10 Normal Position close Bonnes Vent No Safety Posinon Open Bodv Matenal SA 182 F316 Req'd To Open Y
Wedge Matenal SA351 Gr CF8M Dp To close 1935 BB or PS Presswe Seal Dp To Open 2700 Dwnstrm Press 0
Design Temp 300 Thermal Binding Review in irutsal screemng using the data sheet is this valve susceptable to thermal bindmg concerns?
YES The temperature differential is
/ The system design temp is 70 300 is the wedge design flex and the system design temperature 200 F. or less?
No is wedge aesign fie,: and temp differential 100 F or less / or solid and temp differential 50 F or less ?
Yes 1 N1010B Ias been deternuned to be susceptable to thermal bindmg? Yes / No No Hydraulicall3 Induced Pressure Locking in initial screcrung, using the data sheet, is this valve susceptable to rapid depressurization concems?
YES Was this valve cor.Srr w.a o be leaking durmg the time this valve was last tested?
N/A a
Has a bonnet vent bem adds d e r has the scar. bndge wall been tapped to relieve pressure?
No 1 N1010B has been detemuned to be susceptable to hydrauhcally induced pressure locking? Y/N YES If this valve is susceptable, see page 2 for sizme equation?
Thirmally Induced Pressure Locking in irutial screemng using the data sheet, is thas valve susceptable to hquid entrapment concerns?
YES is vthe bonnet designed such that air will be entrapped?
N/A Was this valve confirmed to be leaking dunng the time this valve was last tested?
N/A Has a bonnet vent been added or has the seat or bridge wall been tapped to relieve pressure?
No l
1 N1010B has been detemuned to be susceptable to thermally induced pressure locking? Ym No l
Page 1
Calculati:n (2) 1N10108 Calculation Inout and Outout Summary BonnetPress hSIG)
Pb 2700 Londmgconsumts Obf)
_Lil 0.000444475 Upstream Press (PSIG)
Pu O
landmg Constants (ibf)
_L17 0.045470485 Dwnstnn Press (PSIG)
Pd 0
seat Coefncient (m) mm 0.520792372 Disk Thickness (m) 1.08 Average DP DPavs 2700 Mean Seat Diam (ms dm 3.75 Duk Constant D
3139871.223 Duk Radius (m) a 1.875 Disk Constant C
10615384.62 Vdvs Hub Radius (m) b 1.248 Moment Mrt.
-652.7338386 Hub Length (m)
L 0.4030 Moment ob 2118.159736 Seat Angle (deg) theta 5
Deflect from press & bnds Ybq 1.80732E-05 stem Diam (m)
Decem 1.375 (Deflect due to press )
Kas
-0.077146842 Pouson's Rat o v
0.3 (and shear stress
)
Ysq
-6 41712E-05 Modulus of Elasucity E
27600000 (Deflect due to )
Pfme 16609.37008 Stauc Unwedgmg Thrust Fpe 12.111 lbs (Hub Stretch
)
Ystretch 2.47822E-05 Valve Factor VF 0.50 Total deflect due to press (m)
Yq
-1.07E44 Plate Constants
_C2 0.0490742 oes.ct due to s.st f & sheart.wlbem)
Ysw
-8.02608E-08 Pinte Constam.
_Cs 0.005063497 o.a.ct d= to sem t a imdnemarmt Ybw
-3.03635E-08 Plate Constanta
_Cs 0.805058176 o.a.cidueio non pressunarmi Ye.mp, I.75779E 08 Plats Constants
_C9 0.240989842 Tow d.a d= to s
.nmi amarm)
Y=
-1.28202E47 sem contact force to cr.ner Y@0 F:
9835.066193 Unscatms forces Fpisten 4009.212187 r ert 5198.070734 Fpreeleck 8490.708184 Required Total Force Ftend 21,791 lbs Calculation Coefficient Of Friction Between Disk & Seat Rings mu= VF*(COS(theta
- PI(yl #0))/( 1 -0T
- SI N(theta
- P10/180)))
=== 0.5207924 Aver ge Dp across disks DPa g=Ph-((Pu+Pdy2)
DPavg= 2700.00 Disk Stiffness Constants
>(E*t*3y(12 *(I-v^2))
D= 3139871.2 C= E/(2 *(1++))
G= 1.lE+07 Geometric Influences C2-0.23*(1 -(b/s)^2 *(1+2
- L.NWb)))
02= 0.0490742 C3= b/(4
- a)*(((h/a)^2 + 1 )%N(a&(b/a)^ 2 1 )
C3- 0.0050635 C5=0.St(1+v+(1-v)*(b/a)^2) 08= 0.8050582 Page 2
4 Calculation (2) j 1NIO10B C9-(b/s)* (((1 +v y2 )* LN (a/b)+(((1 -* )/4)* (1 -(b/s)^2 )))
C9- 0.2409998 4
L11 =(1/64)*(ll +5 *(b/a)^ 2)-(5 *(b/s)^ 4H(4 *(b/s)^2 )*(2 +(b/a)*2 )* LN(a/h)))
Lil- 0.0004445 L17=0.25 *(1 -((1 -s y4)*(1 -(b/s)^ 4 H(ble)^2 *(1 +((1 +v)* LN(a/b)))))
LI7= 0.o454705 Moment Mrb=(-DPavgaa^2/_C8)*(LC9/(2 *n* b))*(a*2-b^2) _L17)
Mrb= -652.73384 i
Qb=(DPavg/(2*b))*(a^2-ba2)
Qb= 2118.1597 j
Deflection due to pressure and bending 4
)
Ybg=((Mrb*a^2* C2)/DW(Qbas*3* C3)/D)-((DPavg's^4* LilyD)
Ybq=
-1.8E-05
{
Deflection due to pressure and shear stress i
Ksa=(-0.3 *(2
- LN(a/b)-1+(b/s)^2)
Esa=
-0.0771 Ysq=(Ese*DPavg'a^2y(t*C)
Ysq=
-6.4E-05 Deflection due to hub stretch l
P force-P10*(a*2-b^2)*DPavg P force =
16609.37 1
Ystreteb=(Pforce/(P10
- b ^ 2))* U(2
- E)
Ystretch-2.48E-05 l
Deflection due to pressure forces Yq=Ybq+Ysq-Ystretch Yq=
-1.l E-04 j
a l
Deflection due to seat contact force and shear stress Ysw=-( 1.2 *(m/a)* LN(a/b)* a )/(t
- G)
Ysw=
-8.0E-08 Deflection due to seat contact force and bending l
Ybw=-(a*3/D)*((_C2/_CW)*((a* LM))-Ha/b)* C3))
Ybw=
-3.0 E-08 2
1 Deflection due to hub compression Yeom pr=(2 *a
- PI(y(PIO* b'2))*(l>(2
- E))
Yeompr=
1.76E-08 1
Tot:1 deflection due to seat contact force I
Yw=Ybw+Ysw-Yeompr Yw=
-13E-07 Seit contact force to create Fs Fe=2* P10*a* Yg Tw Fe=
sess.o?
Page 3
Calculation (2)
{
a
(
j 1N1010B 1
i j
Utsetting forces.
a Fristen=(PIO/4)*(Dstein 2*Pb)
Friston-4009.21 a
4 f
Fvtrt=(P10*a 2)*slN(theta *P10/180)*(2*Pb-Pu-Pd)
F*ert=
stee.o7 a
l Fpreslock=2
- Fa *(mu
- COS(theta
- PI(y180). SIN (theta
- P10/180))
Fpreslock-8490.7 3
4 Required Total Force
}
Flotal=- Fpiston+ Fi ert+ Fpreslock+ Fro Flotsk 21790.6 1
i The actuator is capable of producing 29,700 lbs er rorce.
t The force required to overcome pressure locking is 21.79: m i
j Actuator Margin is Margin = (Fmas - Fein) / Fein
=
w%
i i
i The limiting component is the Actuator.
25,000 lbe Ths following provides the corrective actions for this valve to alleviate the concerns of:
1 Perfom calibrated test in the open direction to obtain actual unwedging force and a more accurate PL pullout force required 1
I i
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t I
6 t
4 i
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4 Page 4
~
e da AVMLABLE ACTUATOR THRUST FOR THE OPEN DIRECTION FOR PL/TB l
1N1010B ACTUATOR VCDEL/ SIZE / SERIAL NO.:
ROTORK 30NAX1 86 B3494/A2 i
OPEN STALL TOROUE AVMLABLE (FT-LBS):
550 (SEE TEST CERTIFICATE) l I
STEM FACTOR:
0.015 ASSUMING 0.15 COEFFECIENT OF FRICTION OPEN VOLTAGE AVMLABLE (%):
90 OPEN VOLTAGE FACTOR 0.9 OPEN HIGH TEMPERATURE FACTOR 1
(NO HIGH TEMP EFFECT)
OPEN TOROUE AVMLABLE = (STALL TOROUE)(VOLTAGE FACTOR *2)/(HIGH TEMP EFFECTS FACTOR)
OPEN TOROUE AVMLABLE =
550 X
0.9 X
0.9 1
OPEN TOROUE AVAILABLE (FT-LBS) =
446 OPEN THRUST AVMLABLE (LBS)=
PJ700 90ADDY.XLS
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Cricul: tion (2) a
- 2N10108 Valve information Actuator information Funcuan NV P* ump Cold Leg injection Isolauan Type EMO
\\tanufacturer Borg Wamer Manufactwer ROTORK Item Number 09J-202' Model No 30NAXl 86 Dr wmg No CNM 1205 00 0083 RPM 3600 Press Cias.
1500 PLTB System Calc Inputs Gear Rauo Size 4 00 (A) Hishest System Temp dunns closme i10 Torque Ratmg Duc Tvpe Flex (B) Lowest Svstem Temp smcc closmg 40 Unit Effic.
\\tean Seat Diam 3 75 (C) Eghest Press on either side since closure 2700 Undervoltage Disc Diam 45 (D) Lowest Press for openmg on same side as sub Diam 2 496 (C) above O
System information Hub Length 0403 (E) Lowest Press For openmg on opposite GL 89-10 Yes Disk Thickness 1 08 side as (C) above on either side smce closure 0
Flow Diagram CN 2562-10 Wsdge AngJe 5
IF) Lowest System Temo when closed 40 Coordmates C-6 Stem Diam I375 (0) Eshest Svsteem Temp when opened i10 Normal Posiuon close Bonnet Vent No Safety Posiuon Open Body Matenal SA 182 F316 Reg'd To Open Y
Wedge Matenal SA351 Gr CF8M Dp To close 1935 BBorPS Pressure Seal Dp To Open 2700 Dwnstrm Press 0
Design Temp 100 Thermal Binding Review in initid screening using the data sheet, is this valve susceptable to thennal bindmg concerns?
YES The temperature dferential is
/ The systern design temp is 70 300 1s the wedge design flex and the system design temperature 200 F. or less?
No 1s wedge design flex and temp ddrerential 100 F or less / or solid and temp differential 50 F or less ?
Yes 2N10108 has been deternuned to be susceptable to thermal bindmg? Yes i No No Hydraulically Induced Pressure Locking in mitial screcrung using the data sheet, is dus valve susceptable to rapid depressurtzation concems?
YES Was tius valve confirmed to be leakmg dunng the tune dus valve was last tested?
N/A Has a bonnet vent been added or has the seat or bndge wall been tapped to reheve pressure?
No 2NIO108 has been detennmed to be susceptable to hydraulically induced pressure locking? Y/N Ye5 If dus valve is susceptable. see page 2 for sizine equation?
Thermally Induced Pressure Locking In initial screcrung usmg the data sheet, is ilus valve susceptable to liquid entrapment concems?
YES
!s valve bonnet designed such that air will be entrapped?
N, A Was tius valve confumed to bc leaking dunng the time tlus valve was last tested?
N. A Has a bonnet vent been added or has the seat or bndge wall been tapped to reheve pressure?
No 2N10108 has been determmed to be susceptable to thermally induced pressure locking? Y!N No Page1
Calculation (2) 2N10108 Calculation Inout and Outout Summer.y Bonnet Press (PSIG)
Pb 2700 Loading constants (Ib0
_LII 0.000444475 Upsveam Press (PSIG)
Pu 0
Londmg constants (ib0 Ll?
0.045470485 Dwnsum Ptess (PSIG)
Pd 0
Seat CoefLcient (m) me 0.520792372 Duk11uckness (m) 1.08 Average DP DPave 2700 Mean Seat Diam On) dm 3 75 Disk Constans D
3139871.223 Disk Radius On) a 1.875 Disk constant G
10615384 62 Valve Hub Radius (m) b 1.248 Moment Mrb.
652.7338386 Hublength (m)
L 0.4030 Moment Ob 2118.159736 seat Angle (deg) theta 5
Deflect from press a bnds Ybq 1.80732E45 Stem Diam On)
Detem 1.375 (Deflect due to press )
Esa
-0 077146842 Passon's Ratio 0.3 (and shear stress
)
Ysq
-6.41712E-05 Modulus of Elasticity E
27600000 (Deflect due to )
Pime 16609.37008 Stauc Unwedgmg nrtat Fpe 8.155 lbs (Hub Stretch
)
Ystretch 2.47822E 05 vcive Factor
%T 0.50 Total deflect due io press (m)
Yq
-1.07E-04 Pl;7.e Constants
_c2 0.0490742 oen.ct du. to seat f & sh.anm1 brin)
Ysw
-8.02608E-08 Piste connanis
_c3 0.005063497 o.n du.io sei f a wemm Ybw
-3.03635E 08 Plate Constants
_cs 0.805058176 o.necidue to hub mp,
<intibu Ye.mpe 1.75779E-08 Plate Constants
_C9 0.240989842 Toi id n.c du.io s i. nut amibw Yw
-1.28202E-07 sees soniact fone e cr.au Yab0 Fs 9835.066193 Unscaung forces Fpi.tes 4009.212187 rmt 5198.070734 Fpre*ck 8490.708184 l
Regared Total Fme Flotal 17s836 Ib5 Calculation Coefficient Of Friction Between Disk & Seat Rings i
mu= VF*(COS(theta
- PIO/180))/(1 -(VF
- S I N(theta
- P10/180)))
m** 0.5207924 Aserage Dp ccross disks DP:vg=Pb-((Pu+Pd)/2)
DPavg= 2700.00 Disk Stiffness Constants D=(E*ta3)/(12*(1-v^2))
D= 3139871.2 C= E/(2 *(1+v))
G= 1.lE+07 Geometric Influences C2-0.25 *(1 -(b/a)^2 *(1 +2
- LN(a/b)))
C2= 0.0490742 C3= b/(4 *a)*(((Wa)^ 2 + 1 )* LN(a/b)+(ks)^ 2 - 1)
C3= 0.0050635 C5=0.*,*(1+v+(1-v)*(b/s)a2)
CH= 0.8050582 Page 2
i i
a Calcul: tion (2) 2N10108 C9=(b/s)* (((1 + v y2 )* LN(a/h)+((( 1 -v )/4)*(14b/a)^ 2 )))
09= 0.2409898 L11 =(1/64)*((1 +4 *(b/a)*2)-($ *(b/a)^4)-((4 *(b/a)^2)*(2 +(b's)^2)* LN(a/h)))
L11= 0.0004445 Ll7-0 25*(1-((1-vy4)*(1-(b/s)^4)<(b/a)*2*(1+((1+v)*LN(a/b)))))
L17= 0.0454705 Moment Mrb=(-DPavg'a *2/,CS)*((_C9/(2 *a
- b))*(a ^2-b a2 ),Ll 7)
Mrb= -652.73384 Qb=(DPav g/(2
- b*(a^2-b^2)
Qb= 2118.1597 Deflection due to pressure and bending Ybg=((Mrb*s*2* C2VD)+((Qb*a^3* C3)/D)-((DPavg'a*4* L11FD) Ybg= 1.8F 05 Deflection due to pressure and shear stress Kan=(-0J'(2*LN(alb)-l+(b/a)^2) Kse= -0.0771 YaqM Kse
- DPav g'a^2)/(t*C)
Ysq= -6.4F 05 Deflection due to hub stretch P force =PIO*(a"2-b^2)*DPas g P force = 16609.37 Yeretc h=(Pforce/(PIO* b ^2 ))* U(2
- E)
Ystretcb= 2.48E-05 Deficction due to pressure forces Yq=Ybq+Ysq-Ystretch Yq= -1.1 E-04 Deflection due to seat contact force and shear stress i Ysw=-(l.2 *(a'a P LN(a/ bra)/(t *C) Ysw= -8.0E-08 Deflection due to seat contact force and bending Ybw=-(a^3'D)*((_C2/_CS)*((a* 09'b))-((a/b)* C3)) Ybw= -3.0E-08 Deflection due to hub compression YeomprM 2
- a* PI()/(PIO* ba2))*(U(2
- E))
Yeompr= 1.76E-08 Tetri deflection due to seat contact force Yw=Ybw+Ysw-Yeompr Yw= -tJE-07 Seit contact force to create Fs Fs=2*P10*a*Yq/Yw Fe= eass o? Page 3
i Calculation (2) 4 l j 2N10108 Ueserting forces. Fpiston=(P10/4)*(Dstem^2*Pb) Fpiston= 4009.21 Fvert=(PIO*a ^2)* SIN (theta
- PI(yl 80)*(2
- Pb-Pu-Pd)
Fvert= stes.c7 Fpreslock=2
- Fs*(niu *COS(theta
- PIO/180)-SIN (theta
- P10/180))
Fyreslock= 8490.7 Required Total Force Flotal -Fpiston+Fvert+Fpreslock+Fpo Ftotal= 17834.6 The actuator is capable of pmducing 29,700 lbs er rorce. The force required to overcome pressure locking is 17, ass ibe Actuator Margin is Margin = (Feas - Fmin) / Fein = 66.5 % The limiting component is the Actuator. 25.000 lbs Th2 following provides the corrective actions for this valve to alleviate the concerns of: Perfom calibrated test in the open direction to obtain actual unwedging force and a more accurate PL pullout force required ) i Page 4
e ~ ,a AVAILABE ACTUATOR THRUST FOR THE OPEN DIRECTION FOR PL/TB i 1 2N1010B 4 ACTUATOR MODEL/ SIZE / SERIAL NO.: ROTORK 30NAX1 86 B3494/A6 OPEN STALL TOROUE AVAILABLE (FT-LBS): 550 (SEE TEST CERTIFICATE) STEM FACTOR: 0.015 ASSUMING 0.15 COEFFECIENT OF FRICTION i ~ OPEN VOLTAGE AVAILABLE (%): 90 OPEN VOLTAGE FACTOR: 0.9 OPEN HIGH TEMPERATURE FACTOR: 1 (NO HIGH TEMP EFFECT) OPEN TORQUE AVAllABLE = (STALL TOROUE)(VOLTAGE FACTOR ^2)/(HIGH TEMP EFFECTS FACTOR) OPEN TORQUE AVAILABLE = 550 X 0.9 X 0.9 1 i OPEN TOROUE AVAILABLE (FT-LBS) = 446 OPEN THRUST AVALABLE (LBS)= 29700 i i 4 90ADDY.XLS
DUKE PCNER IP/0/A/3820/11 CATAWBA NUCLEAR STATION 1.1 ROTORK ACTUATOR CERTIFICATION DATA SilEET Page j of 3 WR No. Y h O $ 0 N 4 2. Initial /Date IV MM M { VALVE TAG NO. PREREQUTSTTES of Saction 4.0 hava been met. /8 22*f2 LIMITS AND PRECAUTIONS of Section 5.0 have been / d ?~ 2 9.7 i reviewed. Correct Component Identified. /MX8U S -24 D i l QC notified before reassembly or replacement of QA /822'II f l parts. YJ4&C V O 10.1.3 Serial No. 1 l Wiring Diagram [OO / A/8 l Actuator Type (SIZE) 8 8 M / [ Actuator Speed Ib Voltage 1* ll. P. Rated Amps Rated Torque 300 b Test Data [# f f-f1:7f 10.2.5 Air pressure leak test satisfactory: Yes o 10.4.3 Megger Reading 1.
- 2. M
- 3. M MD to Ground Motor Winding Resistance b.h Q
1 to 2 b OY n 1 to 3 b'd Q 2 to 3 w MBO M KD 11 eater resistance 10.4.4 Switch contact operation satisfactory: Yes _ No /JOf3 (Explain under comments) 10.4.11 Phase rotation satisfactory: Ye IMN Vac j 10.4.13 Phase 1-3
l DUKE POWER IP/0/A/3820/11 i CATAWBA NUCLEAR STATION 1.1 ROTORK ACTUATOR CERTIFICATION DATA SHEET Page 2 of 3 WR No. 8,2/ M h 2 tl Valve No'. j N C /0 8 l 10.4.14 Phase 1 to ground S N!.O Vac Phase 2 to ground J 90. ~7 yac Phare 3 to ground 3 VI. I Vac 10.4.15 No load current I Amps Open No load current /, y Amps Closed 10.4.16 RPM (no load) ek 10.4.25 As Found Date: etting (1-5) Torque -lbs Open 10.4.26 As Found Data: [ d/A Setting (1-5) Torque /4g-lbsClose 10.2.5 Air pressura leak test atisfactory: Yes No / l'N 10.4.27,28l 1 OPEN (ft-lbs) l CLOSE (ft-lbs) l l 10.4.29,30l t AS FOUND l AS LEFT I AS FOUND l AS LEFT l l 10.8.6 1,.,,} l e/ i W4 1 / I / BE P I1 l n 10.8.7 or I2 l 10 & I / 2d. lf I l il - v i / Y O. 2 12l 10.8.8 I31 V/6 I /27.0 l /ff M~ l 2/4 (/ l 3l 14 1/ l /9F. 2. I /%/% l _2F/, rt !4l l s! A b 't I 3'O f. 9 l - H"fE3.t i 2 7C18 1sl 10.8.8a Stall Torque Open M7 FT-LBS Stall Torque Close 5ff,0 FT-LBS 10.8.10,12 l AS T. EFT l l l l REQUIRED TORQUE I AVERAGE. l SWITCH l l l l l OUTPUT FT-LBS l ACTUAL TORQUE l SETTING l IAE l QC l l l OUTPUT FT-LBS l l l l ~300 3 of. r7 5 2.2r e h Ms I OPEN CLOSE }g / ] y, g f /7224 O 10 8.14 Ilandwheel operation satis factory: Ye No (Explain undex Comments) 10.8.17 Limit switc operation satisfactor /2*M* N TEST EOUIPMENT l MANUFACTURER 'l MODEL NO. I CNS NO. I CAL. DUE I ,&-l# "? ? :, i GN'h l 'r Y 9 ( K - c 'i-is ^ lan l ecco lano l u-anl l /Mcffcx l 2 00 l ///To l 9y-of-a>1 t- /bn 0 7E.zoou ers,. csuMtuz7 7/ztr/:73 bwu TEST EQUIPMENT SIGN-0UT VERIFIED / PERFORMED /v, DATE 2-2 7. f_1 / / I i 10/10 bh00 N/AG$}}