ML073170678
| ML073170678 | |
| Person / Time | |
|---|---|
| Site: | Millstone, Kewaunee, Surry, North Anna  |
| Issue date: | 05/19/2007 |
| From: | Gallagher M, Mizer C Dominion Energy Kewaunee, Dominion Nuclear Connecticut, Swagelok Co, Virginia Electric & Power Co (VEPCO) |
| To: | Office of Nuclear Reactor Regulation |
| References | |
| N-756, N-757, SS-45S8-18622-NSR, SS-45XS8-18623-NSR SCS-00684, Rev. Draft-2 | |
| Download: ML073170678 (61) | |
Text
Serial No. 07-0416A Docket Nos. 50-305, 50-336/423, 50-338/339, 50-280/281 RAI Response - ASME Code Cases N-756 and N-757 NON-PROPRIETARY VERSION ENCLOSURE 2 RESPONSE TO NRC REQUEST FOR ADDITIONAL INFORMATION USE OF ASME CODE CASES N-756 AND N-757 SECTION III DIVISION 1 DESIGN REPORTS DOMINION ENERGY KEWAUNEE, INC. (DEK)
DOMINION NUCLEAR CONNECTICUT, INC. (DNC)
VIRGINIA ELECTRIC AND POWER COMPANY (DOMINION)
KEWAUNEE POWER STATION UNIT 1 MILLSTONE POWER STATION UNITS 2 AND 3 NORTH ANNA POWER STATION UNITS 1 AND 2 SURRY POWER STATION UNITS 1 AND 2
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date:
Design Report Page 1 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Swagelok Company 29450 F.A. Lennon Drive Solon, Ohio 44139 Design Report ASME BP&V Section III, Class 3 SS-45S8-18622-NSR Ball Valve SS-45XS8-18623-NSR Ball Valve Created/Approved by: Reviewed by:
6,/4>
Michael T. Gallagher Craig Mizer Professional Engineer Professional Engineer State of Ohio registration E-50154 State of Ohio registration E-68125 05-19-07 05-19-07 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be
.copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 2 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Table of Contents 1.0 Design Report Certification Statement 2.0 Scope 3.0 References 4.0 ASME Section III Code Components 5.0 Material Specifications 6.0 Stress Analysis - Discussion 7.0 Conclusion 8.0 SS-45 Diagram 9.0 Body - main bore 10.0 Body - bottom 11.0 Body and Packing Bolt - packing threads 12.0 Stem 13.0 End Connection 14.0 ND-3521 analysis 15.0 Appendix - Code Case N-757 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 3 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
1.0 Design Report Certification Statement CERTIFICATION I, the undersigned, being a Registered Professional Engineer competent in the applicable field of design and using the certified Design Specification and the drawings identified below as a basis for design, do hereby certify that to the best of my knowledge and belief the Design Report is complete and accurate and complies with the design requirements of the ASME Boiler and Pressure Vessel Code,Section III, Division 1, 2004 Edition.
Design Specification and Revision: BSPEC-04940-00004, Rev. 001 (BP)
Design Report and Revision: SCS-00684, Rev. DRAFT-2 Certified by: Michael T. Gallaqher I P.E.
Registration No. E-50154 State: Ohio Date: 05/22/2007 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report' Page 4 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
2.0 Scope The Swagelok 45S8 and 45XS8 valve has been analyzed to verify conformance to ASME Boiler and Pressure Vessel Code,Section III, Subsection ND, Class 3 components, 2004 edition. Code case N-757 will be invoked in this design report. These two valves are included in this design report because of their similarity.
This report includes the following: a description of the nuclear code components and their materials of construction; a stress analysis of the valve features determined to be critical to pressure containment; a diagram of the valve showing the location of these features.
3.0 References 3.1 ASME Boiler and Pressure Vessel Code,Section III, 2004 edition 3.2 ASME Boiler and Pressure Vessel Code,Section III, 2004 edition - Appendix XIII 3.3 ASME Boiler and Pressure Vessel Code,Section III, Code Case 757 4.0 ASME Section III Code Components Following the guidelines of ND-1 100(d) the following components are classified as ASME section III nuclear code components:
Description Part number Body (45XS8) SS-1-45XS8-18623-NSR Body (45S8) SS-1-45S8-18622-NSR Packing Bolt SS-4A-45-18622-NSR Stem (45XS8) SS-3-45X-K-1 8623-NSR Stem (45S8) SS-3-45-K-18622-NSR See Figure 1 for part schematics 5.0 Material Specifications Body - 316 SS extrulded bar UNS S31600 ASTM A276 / A479 Packing Bolt - 316 SS - UNS S31600 -ASME SA479 Level 2 Strain hardened Stem - 316 SS - UNS S31600 -ASTM A276 condition B Material Strength (psi /1000)
Part Type of Stress 1000F 150°F Notes Description Sm (ksi) (1)(4)
Sy (ksi) (1)(3)
Packing Sm (ksi) (1)(4)
Bolt Sy (ksi) (1)(3)
Sm (ksi) (1)(4)
Stem Sy (ksi) (1)(3)
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SS-45S8-18622-NSR Rev. DRAFT--o SS-45XS8-18623-NSR DCN #07-0 DCN Date: TBD Design Report Page 5 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Notes:
(1) Section ND2121(d) was implemented to allow the use of materials not listed in ASME Section II - Part D.
(2) Sm values obtained from ASME Section II, Part D, Table 2A (3) Sy values obtained from ASME Section II, Part D, Table Y-1 (4) Sm values obtained from ASME Section II, Part D, appendix 2 criteria 6.0 Stress Analysis - Discussion The stress analysis portion of this report is organized based on locations of the valve that are considered essential to pressure containment in the valve.
Several valve locations/features are analyzed in this report. The analyzed locations are shown on the drawing on the following page. The applicable loading scenarios and resulting stresses are calculated at each location. Calculated stress components are categorized into the appropriate design and loading level. Principal stresses are then calculated.
Code Case N-757 specifies ASME Section III, Appendix XIII as one of the options that can be used to analyze a valve product, and Swagelok has selected this option for the analysis in this design report. This appendix contains Five Basic Stress Intensity Limits that must be satisfied. Based on the type of loading the valve will be seeing, not all of the five limits may be applicable for a given feature.
ASME Section III, Appendix XIII, paragraph XIII-1 145 - Primary plus Secondary Stress Intensity requires that the combination of primary and secondary stress not exceed 3 Sm. Swagelok will use this allowable stress intensity for cases when the secondary loading results from a displacement load, i.e. a threaded joint assembled to a particular angular displacement.
There are cases where a secondary type loading results from a non-displacement type load (such as a threaded joint loaded to a given torque). Swagelok will treat these the same way that bolt stress intensities are addressed in ASME Section III Appendix XIII: Total loading cannot exceed 3 Sm. Bolting material Sm values typically equal 1/3 x yield strength, therefore 3Sm will typically equal the minimum yield strength at temperature.
7.0 Conclusion The ball valve part numbers SS-45S8-18622-NSR and SS-45XS8-18623-NSR meet therequirements of ASME Section III, Subsection ND, as described in this design report.
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 6 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
8.0 Figure 1: SS-45S8 diagram Stem Packing threads Body, side wall
/
/- End connection Body, bottom wall Stem Packing Nut Upper Gland Bushing Lower Gland Upper Packing -
Lower Packing This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SS-45S8-1R8622-NSR SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 7 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
9.0 Body - main bore Pressure Load: tangential (hoop) and longitudinal stress, ND-3324.3 PR PR Sh= +.6P SL: - .2P t 2t Where: P = pressure=( )
R = inside radius =4 )
t = wall thickness =(
Sh = hoop (tangential) stress SL = longitudinal stress Sh =( )
SL =[
Radial stress is also present:
Sr = - pressure (acting at the ID) I Sr = 0 (at the OD)
Assembly load, tangential pressure from packing The assembly/adjustment torque on the packing bolt creates an axial force that acts on the packing components. In turn, this axial force results in a radial fprce in the packing. A consrative ratio of radial packing pressure / axial '
packing pressure for the axial stress at Jis 0.6, ref. "Valve Packings that Don't Leak", Lyons Valve Designer's Handbook, 1982.
Calculate assembly force from the empirical relationship: F = T / k x d where:
Fa = Axial assembly Force lb T = Assembly Torque, max. =
k = thread friction factor -*
d = nominal thread size jT I Ro = radius: packing bor~, min.,[ )
R = radius: stem, max. 4 Ap= pressure area, packing; = iT (Ro 2 - R2) = ]
Fa(
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent. of Swagelok Company,
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 8 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Axial packing pressure = Fa / Ap (packing pressure area) =[
Radial packing pressure = .6 x Axial packing pressure =
Stress components from resulting packing. pressure:
Use thin wall equations, since t < .5 R Tangential (hoop) and longitudinal stress from equation above:
Where: P = radial packing pressure 4=
R = inside radius ]
= wall thickness =( )
Sh from radial packing pressure =
SL from radial packing pressure=t Radial Stress:
SR= - Radial Packing Pressure, P (from above) =
Design Loading Primary membrane stresses, resulting from pressure, ref XIII -1142.
Since there is no shear stress in this region the 3 principal stresses equal SH; SL, and SR The 3 principal stresses, stress intensity, and allowable stress intensity are tabulated below.
Temperature (Ff) Principal 1 Principal 2 Principal 3 S, Sm allowable 150 Service Level A Loading Primary + secondary stresses, ref. XIII-1145 resulting from pressure and assembly loads.
Since there is no shear stress in this region the 3 principal stresses equal XSh, X-SL, and XSR Where:
- Sh = hoop stress from system pressure and assembly force ISL = longitudinal stress from system pressure and assembly force YZSR = radial stress from system pressure and assembly force Note: Adding the pressure and assembly stresses is a conservative step: Typically the packing pressure is sufficiently high to allow system pressure to be acting in all of the areas that are included in the calculation.
The 3 principal stresses, stress intensity, and allowable stress intensity are tabulated below.
Temperature Principal 1 Principal 2 Principal 3 S1 Sm allowable (ff) 150 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in.any form without the written consent of Swagelok Company.
SS-45S8-18622-NSR SCS-00684 Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 9 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
10.0 Body - bottom Pressure Load; Bending and shear stress Bottom of the bore will be modeled as a circular plate with fixed edge constraints. From Roark, Formulas for Stress and Strain, table 24, case 10b, 51h ed.
2 3 Pr 4 t2 Where: P =,max. system pressure +
r = radius of main bore, max 4 t= wall thickness, 4 I SBP = Bending stress, from pressure SB=(3%x 500 x.53252 .1412=
)
Shear:
Tp= PxAp/As where: Ap = Pressure area, bottom of bore = I As = Shear area, bottom of bore = ]
Assembly load - bottom of bore The assembly/adjustment torque applied to the packing nut results in a distributed force (pressure) at the bottom of the bore. The radial packing pressure and the resulting friction will cause a reduction in actual packing pressure at the bottom of the bore, as calculated below:
Packing force, bottom = Packing force - radial packing pressure, mean x packing surface area x coefficient of friction, bore to packing Packing force, bottom=[ ,")
Packing Pressure, bottom of bore =
Bending:
As is the case above, bottom of bore will be modeled as a circular plate with fixed edges.
SBA = bending stress from assembly = )
Shear-TA = Packing pressure x Ap/ As where: Ap = Pressure area, packing = )
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-1 8622-N SR Rev. DRAFT-2 SS-45XS8-1 8623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 10 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
As = Shear area, bottom of bore = ( )
TA Design Loading Primary membrane stresses, resulting from pressure, ref XIII -1142.
Principal stresses are calculated using the standard equation for a general 2D state of stress 0-,O2O- x +" o0y +/-I
+
Z-2x T
+(x
+ O'x
- aY ))2 2 4 2 Where:
-x= SBP = bending stress from pressure
- xy = TP = shear stress from pressure The 3 principal stresses, stress intensity, and allowable stress intensity are tabulated below.
Temperature Principal 1 Principal 2 Principal 3 S, Sm allowable (OF) 150 Service Level A Loading Primary + secondary stresses, ref. XIII-1145 resulting from pressure and assembly loads.
Principal stresses are calculated using the standard equation for a general 2D state of stress 0
~x -'-O' 2 ,_ -- O-y xy + )2 YTY 2 ý/ 2 Where:
"x = SBA = bending stress from assembly Txy = TA = shear stress from assembly Note: Packing pressure is sufficient to seal system pressure.
The 3 principal stresses, stress intensity, and allowable stress intensity are tabulated below.
Temperature Principal 1 Principal 2 Principal 3 S, Sm allowable (OF) 150 The 45X body has a minimum bottom wall thickness of( ),thicker than the 45 body analyzed above, therefore no analysis will be required for the 45X bottom bore.
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the Written consent of Swagelok Company.
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 11 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
11.0 Body and Packing Bolt - packing threads Pressure Load System pressure will result in forces that cause shear stress in the packing bolt and body threads, and axial stress in the body adjacent to the threads.
Shear:
Tp = P xAp /As where: Ap = Pressure area, packing bore =
As = Shear area, threads=1 ,body (internal) thread
= ,'packing bolt (external) thread Tp (Body thread)4 )
Tp (packing bolt)=( )
Axial:
Sp = PxAp/AT Where: Ap and P as noted above AT = Tensile area, upper body threads )
SP =[
Assembly load Shear:
TA = FA / As where: FA = Assemblyaxial force =( )
As = Shear area, threads, from above TA (Body thread) = )
TA (Packing bolt)
Axial:
SA = FA /AT Where: FA and AT as noted above SA =(
)
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 12 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Design Loading Primary membrane stresses, resulting from pressure, ref XIII -1142.
Body thread principal stresses are calculated using the standard equation for a general 2D state of stress, at the thread root. Stresses at body thread and packing bolt thread are pure shear.
(7x+ C' +ý ry (°'
i-1 "-2 + )
2 2 Where:
Oy = Sp = axial tensile stress from pressure rxy T'p = shear stress from pressure The 3 principal stresses, stress intensity, and allowable stress intensity are tabulated below.
Feature Temperature Principal 1 Principal 2 Principal 3 S, Sm allowable Body 150 Thread Packing bolt 150 Service Level A Loading Primary + secondary stresses, ref. XIII-1145 resulting from pressure and assembly loads.
Principal stresses are calculated using the standard equation for a general 2D state of stress Body thread principal stresses are calculated using the standard equation for a general 2D state of stress, at the thread root. Stresses at body thread and packing bolt thread are pure shear.
-- O-x 0-1 0-2+o-y +- Z2xy (
+(- -OY-Y )2 2 2 Where:
O'y = Sp = axial tensile stress from assembly 7xy= "p = shear stress from assembly Note: Packing pressure is sufficient to seal system pressure.
The 3 principal stresses, stress intensity, and allowable stress intensity are tabulated below.
Feature Temperature Principal 1 Principal 2 Principal 3 S, Sy allowable Body 150 Thread Packing bolt 150 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
sxwýQRev. SS-45S8-18622-NSR SCS-00684 DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 13of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before'use.
12.0 Stem Design Loading Stresses created by pressure loads are negligible.
Operation Loading Torsional shear will result from the torque required to operate (rotate the ball) the valve. The stem region analyzed here is the minimum section within the pressure containing region The ball valve will experience it's maximum torque value at the start of stem/ball rotation, the initial operating torque.
This is the initial torque required to overcome static friction. This torque will be present for approximately 1 degree of rotation. This torque value will be included in the primary + secondary analysis (service level A).
The stem will experience a lower value of operating torque for the remainder of the stem/ball rotation, the run torque.
This torque value is included with the primary membrane +primary bending loading analysis.
Tox = Tox x r / J where:
To, = Initial (maximum) operating torque, (.
TOR= Run torque, )
J = polar moment inerti .
r = radius of stem( J TORI Primary loading (membrane + bending)
Shear and axial stresses resulting from pressure and operation (run torque) will be combined to solve for principal stresses and stress intensity.
Temperature P 1.5 Sm OF Principal 1 Principal 2 Principal 3 Si allowable 150 j Service Level A Loading Primary + secondary stresses, ref. XIII-1145 resulting from operation loads.
The only component stress present is the torsional shear from operation.
The 3 principal stresses, stress intensity, and allowable stress intensity are tabulated below.
Temperature Principal 1 Principal 2 Principal 3 S, Sy allowable
( 0F) 150 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 14 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Fatigue loading Fatigue loading will be considered for the stresses resulting from valve operation.
Sa will be calculated, Sa is the alternating stress component. When the ball valve is fully cycled (open to close followed by close to open) the state of stress will be totally reversed. The stress that alternates during operation is the torsional stress.
The initial (maximum) stress resulting from the( ) initial torque will be used in this analysis.
SA = ( )
Note: .6 factor is used to convert shear stress to principal stress since alternating stress is pure shear.
Peak Stress SA will be multiplied by Ks, the stress concentration factor, to find the peak stress. Peak stress will be compared to the tabulated values of N, number of cycles, and SAP, peak alternating stress from the fatigue tables in ASME Section iIl, Appendix I to determine cycle life. Figure 1-9.2.1 applies to austenitic stainless steels, and values are tabulated in table I-9.1 SAP = Ks x SA where: Ks = 2.3, ref. Stress, Strain and Strength, Robert Juvinall, figure 13.8.1 ]
SAP -'
]
The tables can be interpolated to solve for number of cycles:
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 15 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
End Connection Pressure Load, tangential (hoop) from ND-3324 PR Sh = PR t +.6P Where: P = pressure,( )
R = inside radius,( )
t = wall thickness, see below Sh = hoop (tangential) stress t (ext. root diam - max. int throat diam) / 2 - pos. tolerance Sh =( )
Longitudinal stress SL = P xAp /AT Where: R = radius @ end of 200 flare: ( ]
Ap = pressure area, PIxR 2 ="
AT = thread cross-section area, ext. )
SL = longitudinal stress SL =( )
Radial stress, SR is also present:
SR @ ID =(
)
SR@OD=( )
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-1 8622-NSR Rev. DRAFT-2 SS-45XS8-1 8623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 16 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Pressure Load, thread shear stress External (end connection) thread shear area, min )
=,PAP As Where:
P = pressure R = radius @ end of 20 flIre:l Ap = pressure area, PIR 2 =1 b As = thread shear area, ext., noted love Tp (thread shear) )
Assembly Loading Longitudinal (axial) stress, threaded area The axial force, Fa, generated by the assembly of the Swagelok fitting is calculated from the empirical equation:
Fa=T / (kd) where:r T = assembly torque =( J k = thread friction factorr d = fitting thread sizef=J Fa =[ )
Longitudinal stress SL= Fa / AL where:
Fa ==from abo e ALI
)
Thread Shear Stress, threaded area:
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-1 8622-NSR swkQ.Nd ce SS-45XS8-1 8623-NSR Rev. DRAFT-2 DCN # 07-0 DCN Date: TBD Design Report Page 17 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
FA As Where: A = shear area, fitting thread, ext = ')
Fa = Axial make-up Force lb (from above)
TA (thread) =
Design Loading Primary membrane stresses, resulting from pressure, ref XIII -1142.
Principal stresses are calculated using the standard equation for a general 2D state of stress o-x +o-y + + (0-x Y 2 2 2 Where:
0x= Sr = radial stress from pressure cry = S, = axial (longitudinal) stress from pressure Txy , Ss = shear stress from pressure Note that the tangential pressure stress Sh is orthogonal to the other stresses and is therefore a principal stress.
The 3 principal stresses,. stress intensity, and allowable stress intensity are tabulated below.
Feature Temperature
('F) Principal 1 Principal 2 Principal 3 Sm Sm allowable Thread 150 [.
Service Level A Loading Threaded area Primary + secondary stresses, ref.,XIlI-1145 resulting from pressure and assembly loads.
Principal stresses will be calculated using this standard equation for a general 2D state of stress, equation above Where:
0x = Sr = radial stress from system pressure ry = SI +SA = axial (longitudinal) stress from system pressure and assembly force
-xy = Ss = shear stress from assembly and pressure The 3 principal stresses, stress intensity, and-allowable stress intensity are tabulated below.
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose.. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-00684 SS-45S8-18622-NSR Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 18 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Feature Temperature Principal 1 Principal 2 Principal 3 Sm allowable Thread 150 13.0 ND-3521 Analysis To satisfy ND-3521, both cross sectional area and section modulus of the component in question must be greater than 1.1 times that of the attached tube member. Tubing tolerances are taken from ASTM Al 016/A 1016M - 04A, Standard Specification for General Requirements for Ferritic Alloy Steel, Austenitic Alloy Steel, and Stainless Steel Tubes, page 766, Table 2.
ZB = bh 2 _ Ai4 S ection modulus of cross section, body crotch 6 32h N
where: b = body width =
h = body height =(
di = body port ID if 2 Aa =bh-- di area of cross section, body crotch 4
ZT = 32 (D -D) section modulus of connecting tubing (1/2" OD, .083 wall) where: Do = tubing OD = .505 in Di = tubing ID = .3058 in (min ID, based on max. wall tolerance)
AT = -7(D 2 -D2) area of cross section, connecting tubing 40 II Therefore,
(.5054 --.30584) = .0109 in4
)=
ZT _
( 1 = 1
1.879 4522 in2 in 3 32x.505 AT =4(.5052 -. 30582)
4
.1268 in2 ZB =.452 in3 > .012 in3 = 1.1 x ZT AB = 1.879 in2 > .1395 in2 = 1.1 x AT This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
ss-45s8-18622-N SR SCSo00684 Rev. DRAFT-2 SS-45XS8-18623-NSR DCN # 07-0 DCN Date: TBD Design Report Page 19 of 19 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
14.0 Appendix - Code Case N-757 BC06-872 Approval Date January 22, 2007 Case N-757 Alternative Rules for Acceptability for Section III, Division 1, Class 2 and 3 Valves, NPS I (DN 25) and Smaller With Welded and Nonwelded End Connections other than Flanges Inquiry>-Under what rules may instrunent. control and sampling line valves, NPS 1 (DN 25) and smaller, with welded and nonwelded end connections other than flanges, meet the design requirements of Section III. Division 1. Class 2 and 3 rules of NC/ND-3512. when the valve minimiun wall thickness does not meet the t, requirements of ASME B 16.34?
Reply: It is the opinion of the Committee that instrunment, control and sampling line valves. NPS 1 (DN 25) and smaller. having valve mininmm wall thickness not in accordance with the tm requirements of ASME B 16.34. with welded and nonwelded end connections other than flanges, may meet the design requirements of Section IIL Division 1. Class 2 and 3 rules of NCIND-3500, provided the following additional requirements are met:
(a) Valves not meeting the tm wall thickness requirements of ASME B 16.34., shall meet the pressure design rules of NC/,ND-3 324; an experimental stiess analysis (Section III, Division 1, Appendix II); or Design Based on Stress Analysis (Section III, Division 1, Appendix XIII).
The desion shall be qualified in accordance with'the requirements of MSS-SP-105-2005.
Section 5.
(b) The end connections shall meet the requirements of NC/LND-3661. -3671.3 or -3671.4. for welded. threaded. and flared. flareless and compression type fitting tube ends.
(c) Valve bonnets tluheaded directly into valve bodies shall have a lock weld or locking device to assure that the assembly does not disengage either through stem operation or vibration.
(d) This Code Case number shall be identified on the NPV-1 Data Report Form.
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Swagelok Company 29450 F.A. Lennon Rd Solon, Ohio 44139 4UW Design Report This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
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Revisions Revision Date Scope of the Revision This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
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Index:
Scope 4 References 4 Analysis Method 5 Design Conditions 5 Structure of this report 6 Allowable Stress Intensity Criteria 6 Code Components 7 Stress Limit Criteria 7 Conclusion 7 Valve Analysis Diagram 8 Body thread for Bonnet Nut analysis 9 End Fitting analysis 13 Bonnet Nut bearing stress 18 Bonnet Nut web shear stress 19 Gland Nut Web Analysis 20 Gland Nut / Bonnet Thread analysis 22 Bonnet analysis - lower thread region 25 Finite Element analysis (FEA) 27 Fatigue (Cyclic) Analysis 34 Experimental Stress-Analysis to Finite 37 Element Analysis Correlation This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
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1.0 SCOPE The Swagelok 4 UW valve has been analyzed to-verify design conformance to the ASME Boiler and Pressure Vessel Code Section III, Division I, Sub-section NB, class 1 components, year 2004.
Swagelok bellows valve products typically do not conform to ASME B 16.34, mainly the result of conscious design decisions made on the basis of the industries Swagelok serves. Most of the design rules of NB-3500, Valve Design, require conformance to B 16.34 as a starting point. Accordingly, Swagelok is using alternative design rule NB-3512.2(d), a rule that does not require conformance to B 16.34. Rather, it relies on the in-depth stress analysis required per NB-3200, Design byAnalysis.
Note: Alternative design rule NB-3512.2(d) applies to valves with welded ends. Code case N-756 must be used for valves with NPT and Swagelok compression tube end connections
2.0 REFERENCES
2.1 ASME Boiler and Pressure Vessel Code Section III "Rules for Construction of Nuclear Power Plant Facility Components" 2.2 ASME B 16.34 "Valves - Flanged, Threaded, and Welding Ends" This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
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Analysis Method:
The analysis includes the valve body, bonnet nut, bonnet, and gland nut. A finite element (FEA) model of the bonnet and body was developed and used to analyze the majority of the stresses in these two components. Established engineering equations and method were used to analyze the balance of the key features; this part of the analysis will hereafter be referred to as the "analysis by calculation".
The types of loading analyzed in this report include: Pressure, weight, thermal effects, seismic, external piping. When any one of these loading effects are not included in a particular analysis it is either not applicable and/or negligible for that region.
Design Conditions:
Pressure / Temperature conditions:
Pressure (psig) Temperature 'F 3600 -20 to 100 3095 200 2795 300 2 2570 400 2390 500 2255 600 2220 650 2170 700 2135 750 2110 800 Bonnet Nut Assembly Torque:( )
Handle Closure Torque:( )
Seismic Acceleration: 6g Erosion, corrosion or other effects that would result in a loss of valve component material are not accounted for in this analysis.
Design Piping Loads:
Fitting loads must meet the following equation:
3/8" tube butt weld end fitting:
Fshear / 135 + Faxial / 275 + Mtorsion / 20 + Mbending / 20 < 1 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
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Where:
Fshear - force in pounds applied parallel to the face of the end connection Faxial - force in pounds applied parallel to the flow axis of the end connection Mtorsion - Torsional moment (in-lb) applied to the end connection Mbending - Bending moment (in-lb) applied to the end connection' Note: The absolute value of Fshear, Faxial, Mtorsion, and Mbending must be used in these equations.
Structure of this report:
As noted above, two methods were used to develop this report: Finite Element Analysis (FEA) and analysis by calculation.
The FEA results are reported by first describing the particular valve region analyzed, followed by a table that contains the actual values for stress intensity compared to the appropriate allowable stress intensity value. Values are tabulated from 100' F to 8000 F. The FEA software has performed the calculations, therefore they are not shown in the report. The FEA sotware is ANSYS.
Analysis by calculations are also reported by first describing the particular valve region. Loading and stress calculations, at 1000 F conditions, are then shown. Table(s) containing the calculated stress intensities and allowable stress intensities are then listed for 1000 F to 800' F conditions.
Allowable Stress Intensity Criteria:
The 2004 Edition of the ASME Section III code will be includes a change to requirement NB-.
2121 (d) that will allow 1" and under valves to be constructed of material made to specifications other than those listed in Section II, Part D, Subpart 1, Tables 2A and 2B, provided the valves meet the requirements of NB-3200 or NB-3500. This is the basis by which the allowable stress intensity values have been chosen for the analysis of the 4UW valve.
The ASME criteria of using the minimum of either 1/3 of the tensile strength at room temperature and 1.1 x 1/3 of the tensile strength at elevated temperatures or 2/3 of the yield strength at temperature forms the basis for the allowable stress intensities used in this report. Raw material product shape and size (hex, round, etc.) as well as proximity to weld joints dictate the allowable stress intensity value.
Here is a tabulation of the components/features and the room temperature tensile and yield strengths used to obtain the allowable stress intensiy:
Bonnet, gland nut, bonnet nut Body Body, at pipe welds Bonnet, close to weld Minimum tensile and, yield strength at elevated temperature are listed in Section II for 316 stainless steel at ( ). The values not directly listed in Section II are obtained by interpolation. These minimum tensile and yield values are then used to obtain allowable stress intensity, as described above. The( ]
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strength value, and is applied when the feature being analyzed includes a weld. The( )is a conservative value, chosen based on the feature being near the weld. Strength values for this feature are not expected to be affected by the nearby welding, but for the sake of conservatism are being reduced.
Code Components:
Part Number Drawing Description Material Rev. Deviation /
NCM SS-4B-PO-xxxxx-NSR 4B-BW6-049-PO-NSR Body 316 SS SA479 x 4U-UPPERBODY-NSR Upper Body detail x 174PH-4BS-P3-xxxxx-NSR 4BS-P3 Stem Insert 174 PH SS ASTM A564 x SS-4U-P4-xxxxx-NSR 4U-P4-NSR Weld Ring 316 SS SA479 x SS-4U-P6-xxxxx-NSR 4U-P6-NSR Bonnet 316 SS SA479 x SS-4B-UA7A-xxxxx-NSR 4B-UA7A-NSR Bonnet Nut 316 SS SA479 x SS-4U-P12-xxxxx-NSR 4U-P12-NSR Gland Nut 316 SS SA479 x Stress Limit Criteria:
All regions analyzed include design loading and service level A limit analysis, with the exception of regions that experience special stress states as described in NB-3227.
The relatively small mass of this valve results in seismic loading and stress magnitudes that are quite low. Regions that contain non-negligible seismic stress are analyzed to service level C limits.
treating seismic loading as a primary load.
A fatigue analysis per NB-3222.4 is included in this report. Thermal stresses are assumed to be general thermal stresses in the fatigue analysis, which allows the use of a constant value for Poisson's ratio, ref. NB-3227.6(b).
Thermal stress analysis is based on the valve being in the open position, with system temperature on the internal flow passages and ambient external conditions.
==
Conclusion:==
'The results of the FEA analysis and analysis by calculation show that all regions analyzed by these methods meet the requirements of ASME Section III.
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4UW stress analysis diaaram This diagram shows the FEA and analysis by calculation regions that are analyzed in this report Gland Nut Web* upper BonetThreadd
-.Bonnet FEA (1)
Bonnet FEA(2)
Bonne FEA()
Bonnet Lo.ie r th reaodFrg ion BonnetfNut Bear~ing.
Bonnet. Nut Web.
Body Thread~s for Bonnet Nut En d F itti g'Body FEA (4fý yyF EA (5)
Body FEA. (6)
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4UW Body thread for Bonnet Nut analysis Length of Engagement:
C, Shear Area:
3 1 -20UNEF 2A/2B Max minor, int .957 Max pitch, int .9734 Min major, ext .9905 Min pitch, ext .9616 Internal (bonnet nut) = SAbn External (body) = SAb I i
)
Additional dimensions:
Body bore ID, max =o (
Tensile (axial) area of upper body
)
Loading:
Pressure Loads Pressure Area, based on ID of bonnet to weld ring seal weld =
Axial force resulting from pressure, Fay -
Thread shear stress due to pressure, rxyp txyc 4 The pressure stress will be evaluated at the body thread shear diameter, equal to the minor diameter of the bonnet nut Use the general equation for tangential (hoop) stress o'hoop = pressure x ri21 (ro2-ri2) x ( 1+ ro2 / r 2 )
ri --inner radius This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
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ro = outer radius r = radius at point of interest Tangential
( (hoop) azp stress due to pressure, )
aT~p (shear diam.)
Axial stress.due to pressure, a'yp
yp axial pressure force / tensile area of upper body
Radial stress due to pressure, c'xp Cxp (shear diam.) = -
Assembly Stresses resulting from the assembly of the bonnet nut to the body Assembly-torque{c Use T =KFd to fin F, empirial reiationship between torque, friction and force in threaded assemblies.
K=( ) thread friction factor,( )
d - 1.00, nominal thread size Assembly Force, Fa = T/kd = ( )
Thread Shear Stress, assembly (1 00F):
Txya =Fa/SAb = )
Along with the shear stress generated by the assembly load there will also be a compressive stress Compressive stress, adjacent to threads:
C'ya=.Fa/Aub=( )
where:
Aub --cros, section area of the cylindrical region adjacent to the body threads Handle closure Loads Handle Torque )
Handle Closure Force, Fc = T /kd 4 )
Where : k =4 ,)thread friction factor witl ]
d = .375, nominal diameter of stem threads Shear stress, due to Fc, Txyc = Fc / Sab =( .
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Seismic Loading Fxs = 6x Fys = 6 xl Fzs = 6 x oe Total seisihic moment om Fxs and Fys, Mts = sqrt (9.62 + 9.62) x moment arm
, Where moment arm = y~distance from threads to valve c.g.
Mts = J Section Modulus of upper body )
Axial seismic stress =)
Bending seismic stress =
Shear seismic stress, threads 4 )
Shear seismic stress, across section =
Thermal Loading Thermal stresses in this region were obtained from the Finite Element analysis and included in the Service level A calculations..
Relative Stiffness The relative stiffness of this joint was conservatively set at 0.5, based on FEA results of a similar joint. This means a service load applied to the joint, such as pressure or closure, will be distributed such that 50% of the load will act on the threads, and increase the shear and axial stresses accordingly. The remaining 50% of the load will act to decompress the compressed portion on the joint.
Resolution of Stresses:
The stresses calculated above will be combined, and principal stresses will be calculated. The principal stresses are then used to determine stress intensities. Calculated stress intensities are then compared to the allowable stress intensity or allowable stress intensity multiple, per NB-3220.
Design Loadings: Primary Stresses.
Principal stresses determined from pressure stresses Service level A limits: Primary and secondary stresses:
Principal stresses determined from the combination of pressure, assembly, closure and thermal stresses.
Service level C limits: Primary stresses:
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Principal stresses determined from the combination of seismic and pressure stresses The first table below contains the appropriate combinations of stress intensities compared to the specific allowable stress intensities, for design conditions and service level A conditions. The alpha factor for the NB-3221.3 allowable stress intensity is conservatively chosen as 1.0. The second table contains the appropriate combinations of stress intensities compared to the specific allowable stress intensities, for service level C. Allowable stress intensities are conservatively based on annealed material, since this region is close to the weld ring to body weld.
Design Loading Level A Service Limits NB-3221.1 NB-3221.1 NB-3221.3 NB-3221.3 NB-3222.2 NB-3222.2 Temp. General allowable Primary allowable primary + allowable
°F Primary stress membrane + stress secondary stress Stress intensity , primary intensity, stress intensity sity Ir____ Sm bending 1.0 Sm intensity 3 Sm 100 200 300 400 500 600 650 700 800 __ _
Level C Service Limits NB-3224.1 NB-3224.1 Temp. Primary allowable OF Stress stress Intensity intensity (greater of 1.2Sm or
_ _ _ yield) 100 200 300 400 500 600 650 700 800 _
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4UW End Fitting analysis 3/8" x .049 tube ends are included in this analysis.
Minimum OD Maximum Area =[( ID =
Moment of Inertia =( ]
Polar Moment of Inertia Pressure Use the general equation for tangential (hoop) stress:
2 2 2 pressure x ri / (ro2 - ri 2) x 2 (1+ ro ri )
2 Ohoop (ID) crhoop (OD) = 2 x pressure x ri / (ro - ri )
C'hoop (ID) = )
ayhoop (OD) =1, Axial stress due to pressure:
2 2 2 2
'axial - pressure x ri / (ro - ri ) = pressurex ID2 / (OD - 1D2)
C axial=( )
Radial stress due to pressure:
Oradial (ID) = -pressure Oradial (OD) = 0 Seismic 6g acceleration values are employed to determine the seismic forces, which are simultaneously applied in three orthogonal directions, at the center of mass of the valve. The valve is assumed to be fully constrained at one of the end fittings.
Fx= Fy= Fz= )
Ly J
Distances from fitting centerline to center of mass:
Lx (along fitting axis) l(along stem axis)
Lz J(perpendicular to x and y)
The moments that result from these loads and positions:
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Bending:
Mx= 0 My=FzxLx Mz =FxxLy Fy xLx-.
) )
Torsion:
Tx= Fz x Ly =
Ty = Tz = 0
)
Weight We will use the same assumption that was used in the seismic analysis, the valve is fully constrained at one end fitting.
Fyw =i )
Mzw =t
)
Shear stress from Fyw 4 )
Bending stress from Mzw (OD)-
Bending stress from Mzw (ID) =
2 External Tubing Loads, Design conditions:
Allowable force and moment values are based on not exceeding the Design loading allowable stress intensity.
C Force axial =
Force shear =
Moment bending =
Moment torsion= .
External Tubing Loads, service level A The 3/8 x .049 tube loads are based on 30 ksi tensile yield strength and 24 ksi shear yield strength, per the requirements of NB-3512.2(d)(1)
Here are the loads at 100F, loads at elevated temperatures are based on the yield strength at temperature Tube Bending (in-lb) Axial (lb) Torsion (in-lb) 3/8 x.049 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
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Design Load Analysis This analysis will include the primary effects of pressure and weight and design pipe loadings:
The worst case for stress intensity occurs at the ID of the fitting.
Since this analysis includes the maximum primary stresses , NB-3221.1 and 3221.3 can be accounted for simultaneously. Alpha factor for NB-3221.3 is conservatively chosen as 1.0 Design Loading 3/8" x .049 NB-3221.1, Temp. NB-3221.1 , N1b3221.3 OF NB-3221.3 stre General Generalintensity, srs Primary Sm Stress
__________ __ ntnsity 100 200 300 400 500 600 650 700 800 ____ _
Service Level A analysis This analysis will include pressure, weight, thermal and the service level A tubng loads listed above. NB-3512.2(d)(1) requires that these piping loads be applied in four separate ways:
- 1. Direct tension (axial) in the x direction
- 2. Bending about the z axis (In the plane of the valve)
- 3. Bending about the y axis (perpendicular to the plane of the valve)
- 4. Torsion about the x-axis Direct Tension:
yx, axial tube = axial piping load / area c" x, axial pipe
)
To complete the analysis, a x, axial pipe, is added to the axial pressure stress, axial thermal stress, and bending stress from the weight to obtain the x normal stress. The other two normal stresses include the hoop, radial pressure, and thermal stresses. The x, y and z normal stresses are combined with the xy, xz, and yz shear stresses to find the principal stresses. Combinations including both tensile and compressive axial pipe forces are included in our spreadsheet analysis.
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Bending about z axis:
ay x, z bending pipe = pipe level A bending moment x distance from neutral axis / moment of inertia + axial pressure stress + bending stress from weight. The remainder of the analysis is similar to Direct Tension, above Analysis will include the effects of compressive and tensile bending, to capture the worst case stress intensity.
From the spreadsheet review of the above combinations, the worst case is the tensile bending case, at the fitting OD. The stress intensities are compiled in the table below Bending about y axis:
Due to the symmetry of the fitting, this analysis would be identical to bending about the z axis.
Torsion about the x axis:
Pressure stresses C'hoop, C axial , and O-radial are combined with torsional shear and thermal to find principal stresses.
Thermal stresses obtained from the FEA are included in all of the Level A service limit stresses tabulated below.
The summary table below contains the calculated stress intensities compared to the allowable limits. Stress intensities are based on annealed material, due to the welded joint Level A Service Limits 3/8 x .049 end NB-3222.2 NB-3222.2 Temp. primary + primary + primary + allowable OF secondary secondary secondary stress stress sed stress intensity, intensity, stess intensity axial pipe bending torsion pipeSm loading pipe loading loading 100 200 300 400 500 600 650 700 800 ___
Service level C analysis This analysis will include seismic effects, along with weight, pressure and design piping loads This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
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The state of stress resulting from these loads has all six components of stress, x, y ,and z normal stresses etc. We will conservatively add the shear stresses together directly, creating a slightly more conservative model, but much simpler. Also, the seismic bending stresses will be added together directly: This is a conservative step compared to locating the theoretical maximum combined moment.
(For reference: the location of the maximum bending stress, resulting from the combined effects of Mz and My is:
tan 0 =Mz/My, 0 measured from z axis.)
The summary table below contains the calculated stress intensities compared to the allowable limits. Stress intensities are based on annealed material, due to the welded joint.
Temp. Level C Service Limits OF 3/8 x .049 NB-3224.1 allowable NB-3224.1 stress Primary intensity, Stress (greater of Intensity 1.2Sm or 100 yield,_..N 200 300 400 500 600 650 700 800 _ __
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4U Bonnet Nut bearing stress The contact area between the inside face of the bonnet and the bonnet lip will experience bearing stress:
Bearing area = {( bonnet lip OD- bonnet lip,chamfer )2 _( bonnet nut ID-bonnet nut ID chamfer )2 } x PI / 4 Bearing Area = ( )
Bearing Loads, from bonnet nut thread analysis I
Assembly loadr Pressure load: l Closure load: I These loads are combined, based on NB-3227.1, including the relative stiffness factor of 0.5 described above in the "12UW Body thread for Bonnet" analysis.
Bearing stress =( )
The table below compares the bearing stress to the yield strength, the allowable bearing stress per NB-3227.1 NB-3227.1 NB-3227.1 OF Bearing Stress Allowable bearing stress 100 _
200 300 400 500 600 650 700 800 The top of the bonnet lip is not expected to be in the heat affected zone following the bonnet to weld ring weld.
However, the allowable bearing stress has been reduced, conservatively, to account for the possibility of some strength loss in this region.
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4U Bonnet Nut web stress Stresses are analyzed in the inner corner of the web. Thermal stresses, obtained from the FEA analysis, are included Shear area = web thickness x Bonnet nut ID x PI Shear area =(
I Tensile area 4 )
NB-3221.1 NB-3221.1 NB-3222.2 NB-3222.2' Temp. General allowable primary + allowable OF Primary General secondary stress stress Primary stress intensity intensity stress intensity 3 Sm intensity 100 200 300 400 500 600 650 700 800 _" J This document. and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, 6r furnished to others in any form without the written consent of Swagelok Company.
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4U Gland Nut Web Analysis Relevant Dimensions:
Stem OD =
Bonnet Nut Web Thickness =
Gland Nut Radius =
Load Radius =
Gland Nut Internal Radius =
Poisson's Ration (316 SS) = .27 Gland Nut Thread = 11/16-28 UN-2E Nominal Thread Size = 11/16 Thread Coefficient of Friction =
Design Loads:
- 1. Primary:
- a. 3600 psi internal pressure Pressure Area =i {(Bonnet Packing Bore ID)2- (Stem OD)2 }/4 Pressure Load )
- 2. Secon ary: )
Axial load due to gland nut torque = Fa Fa = Gland Nut Torque /(Thread Coefficient of Friction
- Nominal Thread Size)
F, Bending Stress Formula:
Source: Roark & Young Mra Mra = unit radial bending moment per inch of circumference rd b ~ Mra = w*a ( L 9 - C 7 L6/C 4 )
SWhere L9, C7, L6, and C4 are defined by:
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Desiqn Report Template Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 21 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
L9= (rd/a)[.5(l+v) In (a/rd) + .25(1-v){1-(rd/a) 2}]
C 7 .5(1-v 2)(a/b - b/a)
L6 = (rd/4a)[(rd/a) 2 - 1 + 2 In (a-rd)]
C4 = .5[(l+v)(b/a) + (1-v)(a/b)]
Substituting variables, L9= .256 C7 = .722 L6= .052 C4= 1.057 4U Gland Nut Analysis- 100 in/lbs Assembly Torque:
Design Loading Level A Service Limits NIB-3221.1 NB-3221.1 NB-3221.3 NB-3221.3 NIB-3222.2 NB-3222.2 Temp. General allowable Primary allowable primary + allowable OF Primary stress membrane stress secondary stress Stress intensity, + primary intensity, stress intensity Intensity Sm bending 1.5 Sm intensity 3 Sm 100 200 300 400 500 600 650 700 800 k,,.,
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, orfurnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 22 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled cooies must be verified as current before use.
4UW Gland Nut / Bonnet Thread analysis Length of Engagement:
11 Min. Engage.
Chamfer size:( )
Shear Area:
11/16-28UN 2 Max minor, int Max pitch, int Min major, ext Min pitch, ext
.657 in
.6692
.6799
.6594 Internal (gland nut) -
External (bonnet) I Additional Dimensions:
Pressure seal area of packing =
]
Loading Pressure Loads Valve pressure will result in primary hoop, axial, and shear stress.
Use the general equation for tangential (hoop) stress Ohoop pressure x ri2 (ro2 - r 2 ) x ( 1+ ro2./r 2 )
Cyhoopt
)
Axial pressure stress:
Axial pressure stress = pressure x seal area / upper bonnet tensile area This document and information on it are tht confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
A% ,4UW Design Report Template SCS-xxxx DCN #: xx-xxxx DCN Date: xx/xx/xx Page 23 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Shear stress: =
1) pressure x seal area / thread shear area Assembly Forces resulting from assembly of gland nut to bonnet Nominal assembly torque use T =KFd to find F Assume a maximum asse bly torque o K=( ]
d = .6875, nominal thread size F = Td )
This force will generate a shear stress in the threads and axial stress in the bonnet, and the axial force in the packing will create radial sealing pressure Shear Stress Shear Stress(.
Axial stress in bonnet Bonnet tensile area =
Axial stress in packing
[
Seal area cross-section =
)
Use the stress ratio, K, defined in "Valve Packings that Don't Leak" ref. Valve Design Handbook At 1333 psi axial stress, K = .8, upper bound At 5322 psi axial stress, K = .5, upper bound At 9313 psi axial stress, K = .5, upper bound Radial packing pressure = K x Axial packing pressure Radial packing pressure at Radial packing pressure at Apply this radial packing pressure:
Use the general equation for tangential (hoop) stress cThoop =pressurex riI2 (ro2 - ri2 ) x ( 1+ ro 2 1r2)
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
4UW Design Report Template SCS-xxxx Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 24 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled cooies must be verified as current before use.
ri = inner radius ro = outer radius r = radius at point of interest tang stress due to packing pressure, Ghoopr C'hoopl note: radial stress is negligible in this region Resolution of Stresses Design conditions: Primary stresses Principal stresses are determined from pressure stresses Service level A conditions: Primary and secondary stresses Principal stresses are determined from the combination of pressure, assembly and thermal stresses.
The table contains the appropriate combinations of stress intensities compared to the specific allowable stress intensities. The alpha factor for NB-3221.3 allowables is conservatively set to 1.0 Design Loading Level A Service Limits (using 350 in-lb gland nut torque)
Temp. NB-3221.1 NB-3221.1 NB-3221.3 NB-3221.3 NB-3222.2 NB-3222.2 OF General allowable Primary allowable primary + allowable Primary stress membrane + stress secondary stress Stress intensity , primary intensity, stress intensity Intensity Sm bending 1.0 Sm intensity 3 Sm 100 200 300 400 500 600 650 700 800 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Redort Template Rev. -
EPM(&*Wýý, DCN #: xx-xxxx DCN Date: xx/xx/xx Page 25 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
4U Bonnet analysis - lower thread region The 13/16 -20 threaded region of the bonnet is analyzed in this part of the report. The 13/16 threads are used for the panel mounting nut, and the load effects of that connection are included here.
Relevant geometry:
( )
Tensile (axial) area of bonnet ( 1 Shear area of bonnet thread at panel nutl )
Loading:
Pressure Loads Valve pressure will produce tangential (hoop), axial and radial stresses in the bonnet wall Use the general equation for tangential (hoop) stress o'hoop = pressure x ri2
/ (ro2-ri2) X ( 1+ ro 2 / r 2 )
ri = inner radius ro = outer radius r = radius at point of interest c'hoop (ID)=( )
CGhoop (OD)=! )
e'axial = pressurex bonnet ID2 x. 785/ tensile (axial) area of bonnet Caaxial 4
)
c'radial (ID) )
Oradial (OD) = 0, negligible Handle closure Loads This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template E)%*1VAM%%\6k Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 26 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Handle Torque 4 ))
Handle Closure Force, Fc = T /kd Where : k = J d = .375, nominal diameter of stem threads Axial bonnet stress, closure =( )
Panel Nut installation load Maximum panel nut torque =( )
Panel nut force, Fpn = T / kd )
Where : k =4 ), thread friction factor, lubed d = .8125, nominal diameter of bonnet threads Panel nut axial stress (in bonnett=4 Panel nut thread shear stress =
I Resolution of Stresses:
The stresses calculated above will be combined, and principal stresses will be calculated. The principal stresses are then used to determine stress intensities. Calculated stress intensities are then compared to the allowable stress intensity or allowable stress intensity multiple, per NB-3220.
The table below contains the appropriate combinations of stress intensities compared to the specific allowable stress intensities. Alpha (ox) factor for NB-3221.3 is conservatively chosen as 1.0 The table contains the worst case stress intensity states: located at the bonnet ID for design loading and at the bonnet OD for level A service limits:
Design Loading Level A Service Limits NB-3221.1 NB-3221.1 NB-3221.3 NB-3221.3 NB-3222.2 NB-3222.2 Temp. General allowable Primary allowable primary + allowable
°F Primary stress membrane + stress secondary stress Stress )intensity , primary intensity, stress intensity Intensity Sm bending 1.0 Sm intensity 3 Sm 100 200 300 400 500 600 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
IONWA 4UW Design Report Template SCS-xxXRev-DCN #: xx-xxxx DCN Date: xx/xx/xx Page 27 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
ir II 650 700 800 IL I I 4U Body & Bonnet Finite Element Analysis Design Loads:
- 1. Primary:
- a. 3600 psi internal pressure
- 2. Secondary:
- a. Thermal Gradient:
- i. Ambient Temperature = 40'F ii. All internal wetted surfaces are at the design temperature iii. The bellows is assumed to be ruptured (bonnet contains pressure) iv. External heat transfer ctefficient.-- )
- b. Union Nut Assembly Preload X
- c. Handle Closure Torque =
- 3. Service Level A Piping Loads:
- a. in-lbs bending moment (My)
- b. in-lbs bending moment (Mz)
- c. in-lbs torsion
- d. Jibs tension The analysis is divided into 6 sections (3 bonnet, 3 body).
Reference page 4 for diagram This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template SNAQqQ\06C Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 28 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Results and comparison to allowable stresses are as follows:
Bonnet Section 1 Design Loading NB-3221.1 General NB-3221.1 NB-3221.3 Primary NB-3221.3 Temp. Primary Stress Intensity allowable membrane + primary allowable oF stress bending stress intensity, intensity, 1.0 Sm Sm 100 200 300 400 500 600 650 7OO_______
800
- Level A Service Limits NB-3222.2 primary + secondary stress NB-Temp. intensity 3222.2 OF allowable stress intensity 3 Sm My Mz Torsion Tension 100 _____"
200 300 400 500 600 650 700 800 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template Rev. -
SN*A(1%Q\06L DCN #: xx-xxxx DCN Date: xx/xx/xx Page 29 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Bonnet Section 2 Desiqn Loading NB-3221.1 General NB-3221.1 NB-3221.3 Primary NB-3221.3 Temp. Primary Stress Intensity allowable membrane + primary allowable OF stress bending stress intensity, intensity, 1.0 Sm Sm 100 "
200 300 400 500 600 650 700 800 _
Level A Service Limits NB-3222.2 primary + secondary stress NB-Temp. intensity 3222.2 OF allowable stress intensity 3 Sm
_,_ y Mz Torsion Tension 100 200 300 400 500 600 650 700 800 k, This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 30 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Bonnet Section 3 Desiqn Loading NB-3221.1 General NB-3221.1 NB-3221.3 Primary NB-3221.3 Temp. Primary Stress Intensity allowable membrane + primary allowable OF stress bending stress intensity, intensity, 1.0 Sm Sm 100 200 300 400 500 600 650 700 800 ,_
Level A Service Limits NB-3222.2 primary + secondary stress NB-Temp. intensity 3222.2 OF allowable stress intensity 3 Sm My Mz Torsion Tension 1~00 200 300 400 500 60O 650 700 800 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 31 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Body Section 4 Design Loading NB-3221.1 General NB-3221.1, NB-3221.3 Primary NB-3221.3 Temp. Primary Stress Intensity allowable membrane + primary allowable OF stress bending stress intensity, intensity, 1.0 Sm Sm 100 200 300 400 500 600 650 700 800U .
Level A Service Limits NB-3222.2 primary + secondary stress NB-Temp. intensity 3222.2 OF allowable stress intensity 3 Sm My Mz Torsion Tension 100 200 300 400 500 600 650 700 800 Allowable stress intensity values are based on annealed material, due to welding in this region.
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 32 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled cooies must be verified as current before use.
Body Section 5 Design Loading NB-3221.1 General NB-3221.1 NB-3221.3 Primary NB-3221.3 Temp. Primary Stress Intensity allowable membrane + primary allowable OF stress bending stress intensity, intensity, 1.0 Sm Sm 100 200 300 400 500 600 650 700 800 Level A Service Limits NB-3222.2 primary + secondary stress NB-intensity 3222.2 Temp. allowable stress OF intensity 3Sm My Mz Torsion Tension 100 200 300 400 500 600 650 700 80 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template Rev. -
E)\1Aý(1%61k-I DCN #: xx-xxxx DCN Date: xx/xx/xx Page 33 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Body Section 6 Design Loading NB-3221.1 General NB-3221.1 NB-3221.3 Primary NB-3221.3 Temp. Primary Stress Intensity allowable membrane + primary allowable OF stress bending stress intensity, intensity, 1.0 Sm Sm 100 200 300 400 500 600 650 700 800 Level A Service Limits NB-3222.2 primary + secondary stress NB-Temp. intensity 3222.2 OF allowable stress intensity 3 Sm 100 MY Mz Torsion Tension "
200 300 400 500 600 650
,700 8000 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 34 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled cooies must be verified as current before use.
Fatiaue (Cyclic) Analysis A fatigue analysis has been performed on the 4UW valve. Cyclic loading resulting from valve operation and packing nut adjustment will be shown here.
Analysis Method: Alternating stress (Salt) is calculated per NB-3216. The Salt values are adjusted for the modulus of elasticity variation with temperature. The Salt value for each transient is used to obtain N, the allowable number of cycles, from the austenitic stainless steel fatigue curves in ASME Section III, appendix I, tables 1-9.1 and 1-9.2.2. It is important to note that Swagelok has obtained advance copies of new fatigue strength data and fatigue curves for stainless steels, working with a member of the ASME sub-group on fatigue strength. There are two new curves, one for air and the other for reactor water. They are both more restrictive than the existing 2001 curve, therefore Swagelok has taken the proactive step of including them in this analysis. The curves can be compared in the plot below. Usage factors for each condition are calculated by dividing the actual number of cycles, n, by the allowable number of cycles, N.. The cumulative usage factor is the total of all usage factors. This value must be less than or equal to 1.0.
"j Reactor Water 100 Air
. . . . 2001 10 10 100 1000 10000 100000 1000000 cycles Tabulated Sa vs. Cycle Values cycles 10 20 50 100 200 500 1000 2000 5000 2001 Sa (ksi) 708 512 345 261 201 148 119 97 76 2004 cycles 10000 20000 50000 100000 200000 5E+05 1.OE+06 Sa (ksi) 64 55.5 46.3 40.8 35.9 31 28.3 Air Cycles, N 10 40 100 400 1000 4000 10000 40000 100000 400000 1E+06 Sa (ksi) 700 358 232 137 99 65 50.5. 36.6 29.9 22.7 19.5 Reactor Cycles, N 10 40 100 400 1000 4000 10000 40000 100000 400000 1E+06 water Sa (ksi) 280 146 94.9 56.6 42.6 31.1 26.6 22.2 20 17.9 17 This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
4UW Design Report Template SCS-xxxx DCN #: xx-xxxx DCN Date: xx/xx/xx Page 35 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
The fatigue calculations below include analysis of the Gland nut web undergoing packing adjustments, and the bonnet and bonnet nut experiencing the effects of on-off operation of the valve. Typically, additional features will be analyzed, based on the design specification requirements.
Packing adjustment - Gland Nut web Calculate Salt Stress concentration factor Kt from Peterson tables: Kt = 2.2 Si max =
Si mmi, = conservatively assume that packing load totally relaxes between adjustments Salt =
Calculate Sa & N Packing nut should not normally be exposed to any system media, therefore it is appropriate to use the Sa "air" values. )
Calculate U, usage factor
( )
On / Off Operation - Lower Bonnet (FEA bonnet section 2)
Calculate Salt Stress concentration factor Kf, from LipsonNoll, & Clock: Kf = 2.8 Si max 4 )
Si min = 0 conservatively assume that valve is fully open with no pressure load Salt )
Calculate Sa & N Assuming that the bellows is intact during normal operation the bonnet will not be exposed to system media, however, in the event of a bellows rupture the bonnet will see system media. Therefore Sa values for air and reactor water exposure will be used to calculate N.
Reactor water Air This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 36 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Calculate U, usage factor
(( - and -
)
)
Therefore U = U1 + U2
)
On / Off Operation - Bonnet Nut Web Calculate Salt Stress concentration factor Kt from Peterson tables: Kt = 2.9 Si maxr Si min fr tem
)
No closl e fore and thermal stress, conservatively assume that thermal and mechanical cycles coincide Salt =( )
Calculate Sa & N Bonnet nut should not normally be exposed to any system media, therefore it is appropriate to use the Sa "air" (values
)
Calculate U, usage factor C[ )
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
SCS-xxxx 4UW Design Report Template Rev. -
Ema*\6(ý1 DCN #: xx-xxxx DCN Date: xx/xx/xx Page 37 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
Correlation of Strain Gage Experimental Stress Analysis to FEA
Background:
The UW Series bellows valves are presently being analyzed for conformance to requirements for safety related applications in the nuclear power industry. Per the ASME Boiler and Pressure Vessel Code,Section III, Division I - NB-3512.2d3),
adequacy of stress analysis of the valve body and bonnet shall be verified by experimental stress analysis conducted in accordance with the requirements of 11-1100 through 11-1400.
Objective:
- 1) Conduct experimental stress analysis on a 4UW bellows valve per requirements above.
- 2) Conduct finite element stress analysis with ANSYS Mechanical using boundary conditions similar to those from experimental stress analysis.
- 3) Compare results of stress analysis from both methods.
Results: The correlation between the two methods is detailed in the correlation of experimental results to FEA spreadsheet, shown on the next page. It should be noted that all strain
,measurements less than 50 micro strain (corresponding to stress of 1500 psi) are not considered for correlation with FEA results. This was done because the accuracy of the strain gages is uncertain below this level.
Procedure: Principal strain results (epsilon Iand epsilon3) were taken from the FEA. These results were then corrected for load difference from the experimental analysis and multiplied by the appropriate Young's modulus to get principal stresses in the correlation spreadsheet. For the equations used in the correlation spreadsheet for calculation of principal strains from strain gauge data refer to Mechanics of Materials, 4 th Ed., Higdon, OhIsen, Stiles, Weese and Riley, 1985, pp. 73-84.
Discussion: In general, the correlation of stress intensities from the FEA with those derived from the experimental stress analysis was very good. The differences are consistent with the expected accuracies of strain gage experimental stress analysis and finite element analysis.
This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
S~q%~&
SCS-xxxx 4UW Design Report Template Rev. -
DCN #: xx-xxxx DCN Date: xx/xx/xx Page 38 of 38 Printed copies are uncontrolled unless marked "CONTROLLED" in red Uncontrolled copies must be verified as current before use.
NOTE: All principal strains less than 50micro strain (principal stresses less than 1500 psi) are removed. The accuracy ofthe strain gauges at this low range is questionable.
E (psi) 2.83E+07 Max. principal stress Min. principal stress Percent Difference FEA Results Experimental FEA Results Experimental Results FEA Results Experimental (Experimental vs.
Load Case Location SI Results avg. SI S3 avg. S3 Sint Results avg. Sint FEA) axial r IN Tube Diameter from Weld bending x-plane Tube Diameter from Weld bending z-plane Tube Diameter from Weld torque Bottom Right Front Right Bottom Left Front Left Tube Diameter from Weld internal pressurre Bottom Bonnet Middle Bonnet Top Bonnet Tube Diameter from Weld This document and information on it are the confidential property of Swagelok Company and are loaned to you for a limited purpose. Neither may be copied, exhibited, or furnished to others in any form without the written consent of Swagelok Company.
Serial No. 07-0416A Docket Nos. 50-305, 50-336/423, 50-338/339, 50-280/281 RAI Response - ASME Code Cases N-756 and N-757 ATTACHMENT 2 APPLICATION FOR WITHHOLDING FROM PUBLIC DISCLOSURE AND AFFIDAVIT OF DAVID A. PEACE DOMINION ENERGY KEWAUNEE, INC. (DEK)
DOMINION NUCLEAR CONNECTICUT, INC. (DNC)
VIRGINIA ELECTRIC AND POWER COMPANY (DOMINION)
KEWAUNEE POWER STATION UNIT 1 MILLSTONE POWER STATION UNITS 2 AND 3 NORTH ANNA POWER STATION UNITS 1 AND 2 SURRY POWER STATION UNITS 1 AND 2
10 CFR § 2.390 APPLICATION FOR WITHHOLDING AND AFFIDAVIT OF DAVID H. PEACE 1, David H. Peace, Vice President, Engineering, state that:
- 1. I am authorized to execute this affidavit on behalf of Swagelok Company 2, Swagelok is submitting two documents for NRC review and approval: 4UW Design Report Template and SS-45S8-18622-NSR / SS-45XS8-18623-NSR Design Report.
These two documents contain proprietary commercial information that should be held in confidence by the NRC pursuant to the policy reflected in 10 CFR §§ 2.390(a)(4) because:
- a. This information is being held in confidence by Swagelok.
- b. This information is of a type that is held in confidence by Swagelok, and there is a rational basis for doing so because the information contains sensitive commercial information concerning manufacturing of Swagelok valve components.
- c. This information is being transmitted to the NRC in confidence.
- d. This information is not available in public sources and could not be gathered readily from other publicly available information.
- e. Public disclosure of this information would create substantial harm to the competitive position of Swagelok by disclosing confidential Swagelok manufacturing information to other parties whose commercial interests may be adverse to those of Swagelok. Furthermore, Swagelok has expended significant engineering resources in the development of the information. Therefore, the use of this confidential information by competitors would permit them to use the information developed by Swagelok without the expenditure of similar resources, thus giving them a competitive advantage.
- 3. Accordingly, Swagelok requests that the designated document be withheld from public disclosure pursuant to the policy reflected in 10 CFR §§ 2.390(a)(4).
Swagetok Comr aqy David Hl Vice President, Engineering STATE OF ...
COUNTY OF Subscribed and sworn to me, a Notary Public, in and for the County and State above named, this > day of __., 2007.
M-'7y...... E : ./
My Commission Expires: V,*** : i*,(
0OR A,SARVER :NOTARY PUtLtC STAtE 0F OI 0 SUMMIT COUNiTY MYGM. ONDCIWAPRIL12 0101