ML20077G848

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Rev a to Seismic Qualification Analysis of Clow 18-Inch Wafer Stop Valve, Technical Rept
ML20077G848
Person / Time
Site: Limerick  Constellation icon.png
Issue date: 05/17/1983
From: Davidson N, Joel Jenkins, Klutts J
PATEL ENGINEERS
To:
Shared Package
ML20077G840 List:
References
PEI-TR-83-14, PEI-TR-83-14-R-A, NUDOCS 8308090019
Download: ML20077G848 (300)


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l REVISION A f TECHNICAL REPORT PEI-TR-83-14 APRIL 25,1983 REVISION A SELSMIC QUALIFICATION NIALYSIS OF CLOW 18-INCH WAFER STOP VALVE JOB NUMBER 82-2053-04(N),-05(N) I ITEM No. 1.9. 1.11 18"-HBB-BF-AO-57-104 18"-HBB-BF-MO-57-112 BY N. ALLEN DAVIDSON 10 PREPARED FOR I BECHTEL POWER CORPORATION FOR PHILADELPHIA ELECTRIC LIMERICK PLANT IN ACCORDANCE WITH BECHTEL SPECIFICATION NUMBER 8031-P-144, REVISION 1 Work Performed Under Clow Purchase Order Number 30-10469 Bechtel Purchase Order No. 8031-P-144-AC, Items 1.9 and 1.11 Patel Job Number 8220 for Clow corporation, Engineered Products Division Westmont, Illinois l. O potel engineers huntsville, clabomo DO 8 0802 A 05000352 PDR

Report No. PEI-TR-83-14 Page No. 1 REVISION A O REPORT NO.: PEI-TR-83-14 PREPARED BY: ')/ xvA_ Am

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N.' Allen Davidson APPROVED BY: w 7 <[ john . (gdins, Vice-President Q.A. REVIEW: 21 M J69ceVKlutts, Quality Assurance Administrator ORIGINAL ISSUE: April 26, 1983 I 10 REVISIONS i REV. REV. REV. CHECKED Q.A. DESCRIPTION OF CHANCES NO. DATE BY BY BY AND PAGES REVISED r, A 5/17/83 NAd JFJ [ JK Page iv - Change " input" to

                                                                                                             " Analysis" and " Frequency "

RPP p  % to " Modal". T Page 2 - Change "5/8-11" to l "1/2-13". Page 8 - Change "350 F" to "340 F' .

          ;                                                                                     Page 15 - Change "350 F" to "340 F'      .

Page 28 - Change "A" to "D". Appendices Title Page - Change

                                                                                                 " Input" to " Analysis" and
          ;                                                                                      " Frequency" to " Modal".

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I ,O PEI Form So. 611 - 7/1982 l potel engineers huntsville alcDomo

Report No. PEI-TR-83-14' h Page No. ii ( I i CERTIFICATION OF CONFORMANCE This is to certify that the Clow 18-inch Wafer Stop Valve described in Patel Engineers' Technical Report PEI-TR-83-14 has been evaluated to determine its compliance with Bechtel Power Corporation Specification 8031-P-144, Revision 1 as described herein. -The information contained in

 -I      this report is the result of complete and carefully conducted analyses and to the best of my knowledge is true and correct in all respects.

I TK+1L l Robert Parker Professional Engineer Registration No. 13143 State of Alabama ggg s Y 784p T

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l Report No. PEI-TR-83-14 i' O Page No. iii I . .I ABSTRACT j A seismic qualification analysis was conducted to verify the structural in-tegrity of the Clow 18-Inch Wafer Stop Valve , Job Number 82-2053-04(N),- 05(N), for Bechtel Power Corporation for use in Philadelphia Electric Limerick Nuclear Plant. A finite element model was developed to simulate valve components. The model was subjected to static seismic accelerations plus normal operating load environments and were shown to conform to the ASME Section III - 1980 Edition through and including Sumner 1981 Addenda as described in Bechtel Power Corporation Specification Number 8031-P-144, Revision 1. ii 1

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Report No. PEI-TR-83-14 f Page No. iv REVISION A

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TABLE OF CONTENTS PAGE 1.0 IN TROD U CTO RY S UMHARY . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . I 1.1 Introduction............................................... I 1.2 Summary of ResQlts......................................... I 1.3 Con c l us i o n s . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .*. . . . . . . . . . . . . . 5 1.4 Limitations................................................ 5 2.0 DES CRIPTION OF 18-IN CH STOP VALVE. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6 3.0 DESIGN ENVIRONMENT SPECIFICATION................................ 8 3.1 Seismic Environments....................................... 8 3.2 Operational Environmentr................................... 8 4.0 TE CHN IC AL AP P R0 ACH . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9 ( 4.1 General.................................................... 4.2 Finite Element Representation.............................. 9 9 4.3 Modal Analysis...............................,............. 10 4.4 S t a t i c A na ly s i s . . . . . . . . . . . . .\. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 10 4.5 S t r e s s Ana ly s i s . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 11

5.0 DESCRIPTION

OF MATHEMATICAL M0 DEL............................... 13 6.0 RESULTS OF VALVE FREQUENCY ANALYSIS. . . . . . . . . . . . . . . . . . . . . . . . . . . . . 16 7.0 RESU LTS OF VALVE STRES S ANALYSIS . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 17 8.0 DEFLE CTION S OF MAJOR COMP 0NENTS . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 27 9.0 RE FE RE N C E S . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 28 APPENDIX A MATHEMATICAL MODEL APPENDIX B APPENDIX OF CALCULATIONS APPENDIX C ANSYS STATIC ANALYSIS A APPENDIX D ANSYS MODAL ANALYSIS A APPENDIX E ANSYS POST 27 LOAD COMBINATIONS APPENDIX F ANSYS POST 23 VALVE BODY NODAL STRESS AND NODAL DISPLACEMENT DATA APPENDIX G ANSYS POST 25 VALVE DISC AND ADAPTER PLATE NODAL STRESSES AND DISPLACEMENTS

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i i il Report No. PEI-TR-83-14 Page No. v

     <                                                                                  LIST OF ILLUSTRATIONS
     .i FIGURE                                                                                                                            Page 1         C low 18-Inch Waf e r S top Valve . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 4 2         ANSYS Calculated Mas s and Centroid Information. . . . . . . . . . . . . . . . . . . 7 3         Valve Body Max Stress Plot z = 1 Section                                Cut..................... 18 4         Valve Body Max Stress Plot z = 3 Section                                Cut..................... 19 5         Valve Body Max Stress Plot z = 5 Section                                Cut..................... 20 L

6 Valve Body Max Stres s Plo t z = 6.5 Sec tion Cut. . . . . . . . . . . . . . . . . . . 21 7 Ad a p t e r P la t e Max S tr e s s P lo t . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 22 lI 8 D i s e M ax S tr e s s P 1o t . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 23 l lu LIST OF TABLES

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t TABLE 1 Modal Participation Factors for Clow 18" Valve Assembly.......... 2 2 Stress Ratio's for Clow 18-Inch Wafer Stop Valve 4.5 g Seismic Condition.......................................... 2 3 Maximum Deflection............................................... 3 4 Summary of Allowable Stresses................................... 25 5 Net Reaction Forces at Boundary Nodes........................... 26 / J [ l' l i l t' potel engineers ' huntsville, alobomo

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l. ~ Report No. PEI-TR-83-14 Page No. I 1.0 'INTRODUCTCRY

SUMMARY

)l 1.0 Introduction This report presents the results of seismic qualification analysis of a 18-inch diameter stop valve for the Limerick Nuclear Plant. The analysis was performed for the Clow Corporation, Westmont, Illinois, in accordance with Bechtel Power Corporation Specification 8031-P-144, Revision 1. !' Complete details of valve geometry, structural components, and assemblies are given in the engineering drawings of Reference 1. The basic approach taken for this seismic qualification analysis was: o Utilize finite element techniques to fonsulate a mathe-matical model of the valve; iI o Calculate valve fundamental natural frequency; E o Apply the static analysis method to determine stresses, forces and deflections for operating and seismic loading conditions; and

I o Calculate resultant stresses against appropriate allowable stresses.
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I The ANSYS finite element computer program developed by Swanson Analy-sis Systems, Inc., Houston, PA, was used to develop a mathematical

l model and to determine frequencies, stresses, forces, and displace-

'g ments. ANSYS computations were performed on the Control Data Cybernet System. This public domain program has had sufficient history of use

 ,,                              to justify its applicability and validity.

1.2 Summary of Results A frequency analysis of the valve system yielded a fundamental natural frequency of 131 Hz for the Bettis operator assembly and 139 Hz for the Limitorque operator assembly. Table 1 represents participation y factors for a few key frequencies. Application of the operational loads and the seismic design environ-ment specifications of Section 3.0 gave the strees ratios contained in j Table 2. A b O potel engineers huntsville, alabama I

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Report No. PEI-TR-83-14 O Page No. 2 REVISION A Table 1. Modal Participation Factors for Clow 18-Inch Wafer Valve Assemblies ITEM NODE FREQUENCY PARTICIPATION FACTORS NO. (HZ) X Y Z Limitorque 1 . 139 -0.227 1. 319 -1.249 Motor Operated 2 154 -1.455 0.614 0.8971 valve Assembly 3 314 1.027 1.177 1.059 l Bettis 1 131 -0.375 1.646 -0.8796 5 Air Ope rated 2 137 -1.267 0.428 1.321 Valve I Assembly 3 315 1. 30 4 0.904 1.115 c (\ Table 2. Stress Ratios for Clow 18-Inch Wafer Stop Valve 4.5 g Seismic condition STRESS RATIO IDCATION (S TOTAL /S ALLOWABLE) I Valve Body . 0.12 Disc 0.29 Drive Shaft , 0.64 Adapter Plate 0.18 3/4-10 UNC Operator to l l, Adapter Plate Bolts 0.24

(Hybrid Worst Case Assembly) 1 1/4-8N Valve Body 0.09 to Adapter Bolts Cover Plate 0.68 1/2-13 UNC Cover Plate Bolts 0.02 A
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k l 1 Report No. PEI-TR-83-14 i Page No. 3 Full descriptions of all stress calculations ~ are given in Section 7.0 Total deflections of the major valve components due to the applica-tions of the specified seismic acceleration environments and operating loads are given in Table 3. P nble 3. Maximum Deflection DEFLECTION IN G ABAL COORDINATE DIRECTION

  • IDCATION X(IN) Y(IN) Z(IN)

Operator C.G. 0.003 0.004 0.004 Valve Body 0.002 0.002 0.003 Adapter Plate 0.002 0.003 0.002 Disc 0.0004 0.0004 0.0008 IO

  • Refer to Figure 1 for definition of coordinate directions.
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I Descriptions of all deflection calculations are given in Section 8.0

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Report No. PEI-TR-83-14 Page No. 5

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1.3 Conclusions (

 .;              The conclusions drawn from this seismic qualification analysis of the
    '            Clow 18-Inch Stop Valve Assemblies are as follows:

i 1) The valve's major components, as analyzed, do not l exceed ASME allowable stress values as described in Bechtel Specificati'on 8031-P-144, Revision 1.

2) A check of critical area deflections was made and showed that the valve's deflections will not prevent it from performing its specified functions.

1.4 Limitations The analysis was performed on the structural drawings of Reference 1, l the operator definitions of Reference 2, and the design environment specifications of Reference 3. The applicability of the results is subject to the following limitations: I 1) The results do not apply to design, materials, and environments not contained or identified in the above references.

2) Neither pipe structures nor operator structure are included in the qualification analysis.
3) The results do not apply for structural changes or alterations not identified in this report.
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o Report No. PEI-TR-83-14 Page No. 6 i l 2.0' DESCRIPTION OF 18-INCH STOP VALVE JOB NUMBER 82-2053(N) The valve has a 18-inch naminal diameter and is configured as shown in I Figure 1. An internal disc is actuated by a drive shaft which extends through the valve body and adapter plate section into either a Bettis l operator model NT820-SR5-S or a Limitorque SMB1-60-HSBC. A sealing i gland is located in the opera, tor end of the valve body, thus making the adapter section and operator non pressure boundary components. Full structural descriptions of all valve components are given in the complete set of structural drawings of Reference 1. Bettis and Limitorque operator inertial definitions are given in Reference 2. Figure 2 presents mass and center of gravity information for a hybrid worst case operator / valve assembly. This hybrid operator was taken to be the most massive of the two operators with the worst-case center of gravity combination possible. This hybrid was used for the static analysis only. For determination of worst-case hybrid, see appropriate sections of Appendix B. Each proper weight and C.G. was used to determine frequency data for each valve assembly. The valve (without operator) data were generated by the ANSYS Computer program from the mass information of all elements in the mathematical model. The data for the valve with operator were generated using the finite f--)s (_ element model used to determine loads, stresses, and deflections.

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l, Report No. PEI-TR-83-14 Page No. 7 NOTE: XY ORIGIN AT CENTER OF DISC Z ORIGIN AT BACK FACE 'g N

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                 .wes la !*:* vetyt L:mtmitt N PEI 8220 ACTUAL                     MODEL                          CENTROID
 ]        COMPONENT                        WEIGHT                     WEIGHT                   X(g)       Y(IN)     Z(IN )
  ;                                        (LB)                       (LB)

Valve 1650 1082 -6.41 -0.48 3.25 Operator 1305 1305 -27.88 -10.405 -4.3  : Valve & Operator 2355 2387 -18.15 -5.9 -0.88 l Figure 2. 1 I ANSYS Calculated Mass And Centroid Information 4 O patel engineers huntsville, clabama

l i I Report No. PEl-TR-83-14 l Page No. 8 REVISION A I 3.0* DESIGN ENVIRONMENT SPECIFICATION 3.1 Seismic Environments Ioading Conditions Horizontal vertical Specified Seismic Loading 4.5 g 4.5 g 3.2 Operational Environments The operational environments for the subject Stop Valve are defined in References 1 and 3 and are summarized below: o Design pressure = 285 psig o Differential pressures = 65 psig o Design temperature = 340 F A o Seating torque = 63,300 in.-lb Reference 3 notes that the temperature is uniform and thermal gradients are negligible. s I - P, l I i 1 i l l l potel engineers huntsville, clabamo l

Report No. PEI-TR-83-14 Page No. 9 4.0 TECHNICAL APPROACH l 4.1 General .I The technical approach was formulated to provide a high technology analytical solution to the seismic qualification of the subject valve. The analytical methods identified herein were selected to insure com-pliance of the qualification program with controlling documents such as Bechtel Specification Number 8031-P-144, Revision I, IEEE 344-1975, and industry guidelines and standards as represented by NRC Regulatory Guides. lg A finite element analytical approach was selected to develop a mathe-

[ matical representation of the valve. The ANSYS Engineering Analysis System, as developed by Swanson Analysis System, Inc., was used to define the finite element mathematical model and to calculate results l

u including stresses, forces and deflections. A brief sununary of the analytical approaches for these various types of analyses follows. .g 4.2 Finite Element Representation

g The structural problem is. defined in terms of geometric node point location, structural finite elements that connect the node points, and

'l\E nodal masses that describe the inertia characteristics of the struc-ture. The ANSYS computer program then used this finite element repre-sentation as follows:

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.I o The stiffness matrix of the complete structure [K) synthesized from the stiffness of the element [k]. is This is accomplished through the coordinate transforma-

la tion [8], into (global) coordinates. The general equa-tion for this stiffness relationship is T

[K) = [B] [k] [6] o The mass matrix [M] of the complete structure is formed from th'e elemental consistent mass matrices and the in-put lumped mass values. 1 a - I O patel engineers huntsville, clabamo

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Report No. PEI-TR-83-14 Page No. 10  ; O l 4.3 Modal Analysis

{ The modal equation -

([K] - W .t [M]) (4i) = 0 il where ,. g [K] = the reduced stiffness matrix of the structure [M] = the reduced mass matrix of the stureture W = the eigenvalue of mode i ($g)

                                                =     the eigenvector of mode i is solved for the eigenvaluesg U and the eigenvectors ( & g) of the system.               The   eigenvectors calculated by the ANSYS program are orthonormal; that is , they are normalized such                 that the generalized mass for each mode equals unity, T

{ @g) [M] (&g) = Gen. Mass. = 1 Once the modal solutions are obtained in terms of the dynamic degrees of freedom, the eignevectors can be expanded to the full set of displacement degrees of freedom, if desired. 4.4 Static Analysis For a static seismic analysis, accelerations, gn , are applied to the mass matrix [M] to form an inertia loading matrix (F) for each seismic or gravity condition: 1 iI (F) = n g[M] where ng is the acceleration constant. il The static equilibrium equation (F) = [K]{d)

  .!                        is solved to obtain the displacement (d).                  From these displacements, the           forces and stresses within each structural element can be calcu-lated.             Each of the      three coordinate       directions    is   evaluated
   !I                       separately and the results superimposed on a Square Root of the Sum of ii                       the Square (SRSS) basis with the operational conditions added by absolute sum:

o = \ Ea 2 static + o . + c . T gravity operational n v potel engineers I huntsville, alobomo

Report No. PEI-TR-83-14 Page No. 11 'l O where,

                                         =    t tal elemental stress T
                                         "    *1******1 stress    due to static seismic static                               .

acceleration 0 .

                                         =    elemental stress due to dead weight or I#***EY                gravity o      ,gg
                                         =    elemental stress due to operational loads.

4.5 Stress Analysis Stress values for all structural elements in the mathematical model are determined independently for each seismic excitation direction, ,I for dead weight, and for each operational load. Each of these types of load constitutes an individual load case. All load cases are summed as defined in Section 4.4 to achieve a conservative definition .I of the total stress on each element of the mathematical model. The model has been developed to be representative of all components of the valve, therefore, it is capable of reproducing stress levels in

ls all components and at all interfaces with high accuracy.

3 The particular load cases for thet subject valve are defined by the

l design environments of Section 3.0 and are as follow

o Load Case 1 - Design pressure, 285 psig and 65 psig differential pressure across dise; o IAad Case 2 - Seating torque 63,300 in.-lb; . o Load Case 3 - Static x-direction seismic acceleration; o Load Case ,4 - Static y-direction seismic acceleration; 1 I '1 e potel engineers huntsville, alobomo .I

L Report No. PEI-TR-83-14

        %                                   Page No. 12 o      Load Case 5 - Static z-direction seismic acceleration; l                o      Load Case 6 - Gravitational acceleration.

i Total stresses resulting from the above load cases are compared with allowable stress values. ASME allowables, S, are taken from ASME Section III Tables I-7.1 through I-7.3, at the design temperature. The allowable stresses for the dynamic design condition were taken to be the "S" values , for conservatism. Bolt stresses were evaluated to the criteria in ASME, Section III, Appendix XVII, subsubarticle 2460. STRESS STRESS IDADING LIMIT FOR LIMIT FOR COMBINATIONS STRUCTURAL COMPONENTS BOLTING 2 2 2 Seismic condition "S" ft /F eb 2+ v F vb I loads, and design loads i S = ASME Allowable Stress at Design Temperature

                 ,,     . T.n.11. Stre.s I                 F eb
                        =     Allowable Tensile Stress f      =     Shear Stress y

Fg =. Allowable Shear Stress 'I Maximum stresses resulting from the seismic and operational loads are compared with ,the ASME allowable stresses. This comparison is presented in the form of a stress ratio as: Stress Ratio = Maximum Stress Allowable Stress Stress ratio values which are less than 1.0 indicate acceptable stress levels which are within satisfactory ASME design limits for stress allowables .

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r l' Report No. PEI-TR-83-14 Page No. 13 5.0

  • DESCRIPTION OF MATHEMATICAL MODEL The ANSYS structural mathematical model of the subject valve was formed with finite elements available in this computer program. The following element types were used:

o Three dimensional elastic beam element - a uniaxial element with tension-compression, torsion, two plane bending capabilities, and six degrees of freedom at each node. o Elastic flat quadrilateral shell element - a shell element with both bending and membrane capabilities, in plane and normal loads pe rmitted , normal pressure I loading available, six degrees of freedom per node. o Generalized mass element - a point mass element hav- .I ing up to six degrees of freedom, concentrated mass and rotary inertias available, coupled mass or diagonal matrix permitted. o 3-D Isoparametric solid - element used for three-dimensional modeling of solid structure, eight nodal points define the element with three translational ,I w- degrees of freedom per node, pressure loading is avail-i , able. lg s [ o Sprint-Damper - massless spring element with longitu-dinal or torsional capability in one, two, or three dimensional applications. l o 10 Node Isoparametric thick shell - element used for ! three-dimensional modeling of solid structure, ten j nodal points define the element with three translation-l al degrees of freedom per node, pressure loading is availagle. A mathematical model was developed using the above finite elements. l' This model was fonsulated so as to provide adequate definitions of valve interfaces such as shaft penetrations of the valve body, adapter to valve body, disc to seat ring, and drive shaft bearing points. Each structural component of the valve was modeled in sufficient detail to allow accurate computer calculation of the stress levels in the components due to dynamic and operating load environments.

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patel engineers huntsville, olabomc

4 l 1 Report No. PEI-TR-83-14 Page No. 14 s t .' b The ANSYS finite element model of the assembly consisted of: o 530 nodes o 198 isoparamet'ric solids o 8 isoparametric thick shells o 48 beam elements o 50 quadrilateral shells o 2 springs o 1 concentrated mass These elements were described in several local coordinate systems to facilitate the description of the various major components. Each was referenced to the global coordinate system so that all final outputs l could be expressed in a common system. The resulting detailed finite element model of the stop valve is shown in Figure 2. This figure illustrates the complexity of the model and its attention to detail in the critical areas 'of the valve. Note I specifically the increased modeling detail in the neck area where the largest bending stresses would be produced. The wafer valve body was represented with 206 three dimensional solid l elements wtiich reproduces the flexibility of the body at all of its intersections with other valve components. The nodal picture of the valve body is shown in Appendix A. The body was developed with two i levels of elements through its thickness, except in the neck area where there art four levels, so as to provide a more accurate stress resolution in the valve body. Inside the valve body opening, the seat ring was modeled using beam o elements with proper section properties to simulate its inertial char-acteristics. Pressed against the seat ring is the disc, which was i modeled using 24 quadrilateral shell elements. I > l t ( potel engineers huntsville, olabomo t

( . t I Report No. PEI-TR-83-14 Page No. 15 REVISION A

  • The effects of seating the disc against the ring was accomplished by
      ,       using coupled nodal displacements. This mathematically " coupled" selected nodes on the seat ring to selected nodes on the disc.         Any
      'I      displacement     in one node of the coupled set was limited by the resis-tance to displacement of the other node in the set.

l The disc ears were modeled as shell elements, but the shaft to disc torque was transmitted by' use of spring elements with stiffness proper-ties several times that of the shaft. The operator adapter plate' was modeled with plate elements as was the disc. This approach yields excellent membrane and bending data. For the static analysis, the Bettis operator p1 ate was used in the model

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because separate analysis proved it to be a worst-case component. For the frequency analysis, the proper operator plate was used with its appropriate operator. (See Appendix B for details of worst-case de termina tion) . The shaf t was modeled with beam elements with properties that provide proper load carrying characteristics of the shaft. The shaft pene-I trates the valve body in the plane between the two middle section thicknesses of the body. Bearing forces are transmitted to the valve g body at bearing locations by use of coupled nodes. The shaft is l' restrained axially ,by coupling the lower end shaft node to a valve body node. This simulates the presence of the annular key and dowel

  ,          pin.

l' ' The operator was modeled with a lumped mass element at its center of gravity and very stiff beam elements from the mass to the operator [ adapter plate simulated the rigid operator body and housing. For the l static analysis the worst possible mass, C.G. location, and torque was used. Again for modal analysis, appropriate mass and C.G. locations were used for the specific valve assembly. The shaft and operator section was modeled such that dise loads would not be transmitred through the shaft to the operator, as verified in previous testing performed for Clow. A definition of node point numbering systems, coordinate systems, com-ponents, and general math model development data is given in Appendix A. For a more detailed definition and understanding of this complex and sophisticated model, attention should be given to this appendix. The weights of all valve components were generated by ANSYS using con-sistent mass formulations. The operator mass was simulated with a translational lumped mass at its center of gravity. j The physical properties of the various materials in the valve were I taken from ASME Section III Appendix I, Table I-6.0, for a design temp-l 1 erature of 340 F. A potel engineers huntsville, olobama i

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1 Report No. PEI-TR-83-14 Page No. 16 r-5.0 RESULTS OF VALVE FREQUENCY ANALYSIS A modal analysis, as described in Section 4.3 and using the model of Section 5.0, was performed. The lowest fundamental frequency of the Bettis assembly was found to be 131 Hz. The lowest fundamental

  -l            frequency of the Limitorque assembly was found to be 139 Hz. The
'),             motion of these modes is characterized by a torsional motion occurring in the operator adapter pla~te and neck section. No friction coupling between the adapter plate and valve body was taken into account.       The operator loads were transmitted to the valve body only at bolting locations.

Participation factors for a few key resonances are given in Table 1. a These participation factors are calculated for each excitation direc-tion and indicate participation or activity of each mode in that direc-g tion. For a static analytical approach, as in this case, the partici-g pation factors serve only to provide insight into the character of the modes. Total frequency analysis for both valve assemblies are given in the I appropriate section of Appendix D which lists pertinent ANSYS print-outs. O w

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() Page No. 17 t 1 . 7.0 RESULTS OF VALVE STRESS ANALYSIS I The mathematical model of Section 5.0 was subjected to the following

{

load cases: o Load Case 1: Internal valve pressure of 285 psig with a differential disc pressure of 65 psig o Load Case 2: Seating torque applied to shaf t 63,300 in.-lb t . o Load Case 3: X direction dynamic acceleration 1.0 g

    '.                    o     Load Case 4:   Y direction dynamic acceleration 1.0 g o     Load Case 5:   Z direction dynamic acceleration 1.0 g i

The results from these five individually calculated load cases were conservatively summed as shown in Section 4.4; i.e., dynamic load

l= stresses were combined by SRSS and then combined with gravitational and operational stresses by absolute summation. . This was achieved by using ANSYS post processing subroutine POST 27 which allows multiplica-llg tion by scale factors, summations of several load cases by SRSS, abso-lute sum, or algebraic sua methods. Proper scale factors were used to bring the g values of load cases 3 through 5 to design environment levels (see Section 3.0) before (oads were combined.

!I POST 27 also is a powerful tool to scan information. By setting an upper boundary stress limit, the program will scan all stress data and -lq flag stresse.s over the threshold value. This data printout is given in Appendix E. Static analysis input and typical stress printout are given in Appendix C. By use of ANSYS POST 23, principal stresses were calculated at nodal i points throughout the sections modeled with solid elements (valve body). Nodal displacements and stress data compiled by POST 23 are given in Appendix F. Along with calculating nodal stresses, POST 23 also plots section views to show areas of maximum stress. Figures 3 through 8 show maximum stress plots with lines of constant stress for the valve body for the dynamic plus operational loading conditions. r-la j ( i patel engineers huntsville, olabomo

~l

;i 1,

Report No. PEI-TR-83-14 'l' Page No. 18 I i Fe=%\ , w~c . pJ 244 l i. BCDY SECTION CUT Z=1.0 48 INCH VALVE 'SMAX RNSYS 1 l' i i i Figure 3. Valve Body Max Stress Plot z = 1 Section Cut patel engineers huntsville, o!abama

                                                                                                                                                                                                                                       ^

i Report No. PEI-TR-83-14 i i Page No. 19 s! h P \ I h- \

                                                                                                                                                                                                        /

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                        .vE SODY SECTION CUT Z=3.0                                                                      16 INCH YALVE                                                                                 SMRX ANSTS 3
   ,r ir i                                                                                                                               .

l ll Figure 4. Valve Body g. !* Max Stress Plot I z = 3 Section Cut jO potel engineers huntsville, clabama l l

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t Report No. PEI-TR-83-14 {

    ).                                                                 Page No. 20
    )                   .

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D.- y;i ) !ss E ScoY SELT!cN cut Z=5.0 IS INCH VALVE SMAX ANSYS i' I Figure 5. Valve Body z=5 e t on Cut

   .Ol                                                            potel engineers huntsville, alabama

L Report No. PEI-TR-83-14 Page No. 21 I . i i I - v 1 \.'\

]                                      1                       \

j gpA . Scot SECTI3N cui Z=6.5 le INCH VALVE SMAX RNSYS l 0 0 Figure 6. p Valve Body Max Stress Plot

0' z = 6.5 Section cut potel engineers huntsville, aloboma

f i Report No. PEI-TR-83-14 Page No. 22 i --

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{ t N / Figure 7. Adapter Plate Max Stress Plot l . l LO h patel engineers

                      -                                       huntsville, clobomo l

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o i Report No. PEI-TR-83-14 Page No. 23

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 ,0 .

] Report No. PEI-TR-83-14 Page No. 24

  • These figures also show maximum stress plots for the disc and adapter plate for the loading condition. These plots were made using ANSYS
![                                                     POST 25, the same type post processing routine as POST 23 except that it
j calculates displacements and principal stresses for nodes on plate elements. The data compiled by POST 25 are given in Appendix G.

The maximum stress values for other valve components, such as drive shaft and adapter plate bolei'ng, are detailed in Appendix B. The max-usum stressed element was flagged by POST 27 and a detailed stress analysis is contained in this Appendix. s I The maximum stresses for all valve components were compared to the

!g                                                     allowable stress values of Section 4.5. Table 4 gives the maximum
 'g                                                    stress in all sections of the valve due to the dynamic 1cading condi-tion and operational loads.         This table also lists ASME allowable stress values for each material.

The maximum stress values for the isoparametric elements (valve body) i and the quadrilateral shell elements (disc and adapter plate) were cal-culated for each corresponding node. This stress value includes both membrane and bending stress. For conservatism, this value was I compared to only the ASME "S" allowable stress. The stress levels were found to be well within the allowed limits. The drive shaf t stresses were also compared with their allowables and found to be within their limits, tg s lg Cover plate stresses were also compared with the ASME design and Level l A allowable stress ' values. This resulted in a stress ratio well within range. The stress value calculated for the cover plate bolting (la l was also compared to its "S" value and was found acceptable. These calculations. can be found in Appendix B. Table 5 lists the load reactions at the support points. For be tter I unders tanding of nodal locations refer to valve body section of Appen-dix A. The forces shown in these tables represent the net reaction at g nodes where bolts are located. The two flanges which sandwich the valve body must provide a restraining force distribution to the valve body as indicated in the reaction table. Full reaction results are found in Appendix E. The section modulus and area at the plane normal to the flow passage through the region at the valve body crotch is greater than 110 percent of that for the piping connected to the valve i body inlet and outlet nozzles. Also, the ' allowable stress for I the valve body material is greater than the allowable stress of the connected piping material. It is assumed the mating pipe is SA106 GR.B with a 0.375 inch wall. The detailed calculations are

h. listed in Appendix B.

patel engineers huntsville, olabama

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O O O Table 4. , Suasaary of Allowable Stresses _ ~ . - - _ _ . _ . - . . . . . . _ _ . .. .. IDCATION MATERIAL ALIDWABLE STRESS STRESS ELEMENT STRESS ( ps i) VALUE RATIO (PER ASME SECTION (psi) III, TABLES I-7.1 THROUGH I-7.3) l Valve Body SA 516 ' 17500 2156 81 0.12 GR.70 m f Disc SA 516 17500 5043 214 0.29 $ < GR.70 h Drive Shaft SA 564 34550 22168 232 O.64 Type 630 f H-1045 ,o g Operato' Adapter SA 516 17500 3053 261 0.18 U P lat e GR.70 hI Adapter Plate SA 193 25000 9839 N/A 0.09* E Bolts GR.87 6645 Operator / Adapter SR 193 25000 10479 N/A 0.24* Bolts (Hybrid GR.B7 11806 Worst Case Assenably) i-Cover Plate SA 516 (1.5)(17500) 17641 N/A 0.68 GR. 70 =26250 Cover Plate Bolts SA 193 25000 8072 N/A 0.02* GR.B7 26 l

                          *Per ASME, Section III, Appendix XVII, Subsubarticle 2460.

I. - 1

  !                                                     l Report No. PEI-TR-83-14 Page No. 26 Table 5.

Net Reaction Forces at { Boundary Nodes i FX(LB) FY(LB) FZ(LB) NODE SHEAR SHEAR NORMAL 15 1888 653 504 16 441 602 434 17 38 6 371 251 18 260 255 212 19 300 211 228

   ,        20       333                 172   147 23       266                163    106 24       208                172    205 25       188                221    209 1          26       236                360    251 27       313                60 8   429  -

l 28 684 633 613 g 107 2300 829 972 108 555 856 636 109 434 434 375 110 263 268 327

     '-    111       320                197    30 3 112       338                183    192 115       266          \     176    164 116       224                153    281 117       198                237    327 118       289                417    391 119       360                855    617 120 . 799                931    889 148      3691               1709    792 149      4227               3328   1794 152      6463               5375   3112 153   ,  7302               2633   2559 364      5402                997   1557 365      6215              '1854   2074 368      6503               3356   2749 369      8453               2144   2712 I

i O l patel engineers huntsvik, clabamo

r Report No. PEI-TR-80-14 { Page No. 27 8.0 DEFLECTIONS OF MAJOR COMPONENTS Maximum deflections of major valve components resulting from the appli-I cation of all dynamic loading conditions plus operating environments are found in the appropriate sections of the Appendices. The body dis-placements are found in Appendix F, disc and adapter plate displace-ments in Appendix G. The ,. remaining component displacements were checked by summation of individual displacements due to the applica-tion of the load cases listed in Section 4.5 and found in Appendix E. The operator center of gravity experiences the largest displacement in the pipe axia direction. The values given in Table 3 of Section 1.2 give the maximum deflections in the global coordinate system. These values indicate that the valve's deflections will not prevent it from performing its specified function. I I IO s I . I i

 .l.

1. O patel engineers huntsville, clabamo

I Report No. PEI-TR-83-14 Page No. 28 REVISION A

9.0 REFERENCES

1. Clow Engineered Products Division data transmitted included the following items:

Drawing Number Title D-0702 18" Lug Stop Valve Assembly D-0703 18" Lug Stop Valve Assembly B-3945 Machining 18" Wafer valve B-3946 18" Disc and Seal Assembly B-3942 Disc and Ear Assembly (18") B-3920 Lugged Body Plate I,' B-3938 Drive Shaft (Limitorque ) B-3940 Operator Adapter Plate (Bettis) g B-3959 Seat Ring l B-3958 B-3943 Dise L.H. Dise Ear - B-3944 R.H. Disc Ear Cover Plate i B-3967 B-3941 Drive $ haft (Bettis) B-3939 Operator Adapter Plate (Limitorque)

2. General operator , definition: G. H. Bettis drawing SPC-9152 Revision D of a Base II NT820-SRS-S operator; A Limitorque Valve Controls drawing 02-442-0497-2 with center of gravity repor't 1735.
3. Telecon; Allen Davidson, PEI, to Jim Krueger, Clow Corporation, discussing operational loads and thermal I gr'adients, accessories furnished.

C.C. information for operators with

4. Bechtel Power Corporation Design Specification 8031-P-144, Revision 1 dated 6/29/82 " Design Specification for
Butterfly Valves for Nuclear Service for the Limerick

[ Generating Station Units 1 and 2 Philadelphia Electric l Company". I I O potel engineers j huntsville, olobomo l' I

I. - l l l I REVISION A APPENDICES APPENDIX A MATHEMATICAL MODEL APPENDIX B M PENDIX OF CALCULATIONS APPENDIX C ANSYS STATIC ANALYSIS A APPENDIX D ANSYS MODAL ANALYSIS A APPENDIX E ANSYS POST 27 LOAD COMBINATIONS APPENDIX P ANSYS POST 23 VALVE BODY NODAL STRESS AND NODAL DISPLACEMENT DATA APPENDIX G ANSYS POST 25 VALVE DISC AND ADAPTER PLATE NODAL STRESSES AND DISPLACEME! TIS IO lI These AppenElices have been prepared by N.N. A.dDavidson bd Approved by C ?Z Id4 Robert Parker k l . l, potel engineers huntsville, cicbomo

      -     - --- - . - - --        - - - - _ - . . - - , _ . - -    _ ,    , , , _- - -        - - , - - ,         ----,----v-                y
'I O

1 APPENDIX A MATHEMATICAL MODEL i O

                                           \

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               .                 huntsville, olabomo i

o O i l - ANSYS MODEL CODING INFORMATION FOR ELEMENT DATA COMPONENT ELEMENT TYPE MATERIAL I TYPE I TABLE Valve Body 3-D Solid 1 1 1 Neck Transition 10 Node 1 2 2 Element Solid g Disc Shell 1 3 3 Shaft 3-D Beam 2 4 4 I Adapter Plate Shell 5 5 5 Disc Ears Shell 1 6 6 Body to Plate 3-D Beam 1 8 8 Bolts Scat Ring 3-D Beam 3 9 9 l Massless Rigid 3-D Beam \ 4 10 10 Links Torque Spring Spring 1 11 11 Operator Center Translational 1 12 12 of Gravity Mass il t '1 1

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E 1 2 ss: N S36 gy A g3b 8C ha e e' CLev 3 3 g,c, ,,g,L LIORffRT 4er3Y5 23 FIGURE All. DRIVE SHAFT PLOT O AIL e

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                       ~

i i . APPENDIX B APPENDIX OF CALCULATIONS 1

                                            -                                                                                                                l 1

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I O OPERATOR ADAPTER PLATE l BOLTING CALCULATIONS (HYBRID " WORST CASE" ASSEMBLY) O

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i l l l DETERMINATION OF WORST CASE OPERATOR ADAPTER PLATE AND EVALUATION OF ADAPTER PLATE BOLTING s O l O patel engineers huntsville. cicbama 6-18

\,                                                                                                  i l

O 4 The ANSYS analysis which follows presents the determinatdon of the worst case adapter plate used in the hybrid valve model for the static analysis. Both Bettis and Limitorque operator plate models were subjected to the l same seismic plus operating load combinations as in Section 3.0 and worst case plate was determined. The hybrid center of gravity for the operation mass location was used along with the highest operator mass and most severe torque. The Bettis plate showed highest stress lesel of 2494 psi, while the Limitorque showed highest stress of 1835. The Bettis plate also showed higher reaction forces at the bolting points to the valve body. Therefore these bolt reaction loads were used to evaluate the resulting adapter plate bolt stresses. I t iO

                                                                  \

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                                                          %          = 158 3 S M 1

O Patel Engineers Huntsville, Alabania B-10 page no. i .

5, . .i I i

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s BETTIS A.DAPTER PLATE i

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i O l DRIVE SHAFI CALCULATIONS 1 i .\ l lO ,

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          ,O l                                  potel engineers huntsville, clabomo                                       -

6-6I

        -                                                                                                            g h8h y  .

iP- i .de OnwE SHRFT CAn.cS Joh No. 6.L'LO

d. s Date w" 3 B y ___.?LQ.M . . __. . Ca te sh.J /_D . C k d b y _ d k._____._ _

Foecc Awo STr.rs:r VALUE 5 TaKEY FRorn avs $45 Porr t. r App. E 15" A s. Low 3 A sm E " S" = 3 'i f s o S H A F T* D e A : L.: f. t'rs { NE"I , ea I .t.$ { n . , Tonoug a t 3Soo in tb R"KinL T = 1 835*nN 1 G- = 2 $4 S o p ,

                                   -                  SHarv Plar. SRse's hPE 63o H-lo ss E495
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6" axini. erSErb ,a P NFy% 4. F i , 7gy .

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                                                  +
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Tot.QuG

                                                                     =   ~2.o s 8 9     g i'

E 7 ~2 1 A N Q* = tS 'J. t A n. O camp ne.s To Asme *s" : #/g P = 16'i-l l l 1 1 9 Patel Engineers Huntsville, Alabama B-n page mo. .._ l l e

i I ['O 1 J COVER PLA,IE CALCULATIONS t 1 ) I 1 i I , 1O I . l . l l l I O potel engineers huntsville, olabama B-63

r Y ' Title Court Pixx Cai e r (/ 8 ") Job No. 9 z t. o

>$ W                                                                                                            '

Date _4/ts/93 Ckdh/ 2 r' Date 0 bt 7 - By -- _77 4 O 'i O

9. s w s.zes N' 4.s tJ< If4 4 f I I Ii a ,t
                                                       )                 :

f, v. s A g- - _e ,2,fL'E. g y,-n . t.z s .a

m. r 6. o .A '- -

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  .r      *J4 r. = c.o'on A +'
  /    --. . 4 c , v. va x 3 - i x ze s . 2. s %.

Wd2 /Xt m Q sh. 4 ** w ws- vg (w.swe)K =.[z.es ( 9.s 'j'f +EC' )'-8 ks =;na. Aa

                                                                     =     i,6zz g 7, , mg . (( n s > < %))k[,,,,g
     % =(31)(%) =01)[@ SX T"*""l)/o.5] = im 4 e,

g rg + ((ryz) + r t ' = 1, s33 g wn .e g a s. s n n - - -

                                                                                > n a s na.a-rp           =   1. 5 *S  c t . 5 ( t 7 s ool = 2. 6 2.5 0           g 2 6 A a m = "Plg_gz$ o                            = o . s 9 __    s 7, o O

Patel Engineers Huntsville, RIabamu 6 , ,, , y o,

o r v v' V' Title Court Purr Ra're De") Job No. 6tto

         >A By 7la b              Date 4'bl83 Ckd by      Oh             Date ~$     'k O

so<r a,<a<ssis

            .n a. : ;vm.                 B'*% = z.s           '%.u = ry < e,

{ f c, fc+r./ r M g

                                                                  =   16       g I

V". N'*)$ = z.6 ffj,,, , y e .___ m . t = 5 /Es x k.,_ z 8 5 y ) = /n o -r, Fxr.rn u= #"3 lb g= Fg u

                                                                    ,      g ,.,

I v n .c. m u .a ,a,.,...xer, w r > w zuo. '1 o.) 9/e, = so ,tAs,.. =or2 l e) R,= t6 Ase n = 0.00r

                                  +           =   o . oia ,    'to l(}             c3 %)Qgt              T){

l r, = m & w g. _ _ . Y2. =225-aN =szsoo ,t gy , = m u m . __ o 6t sg = t s n g s = m e* -

                                  ^     e.~  g c4 ts3 cn a          = iz.sooo g I

1F s 1 I I O Patel Engineers Huntsuille, Riobuma B-65 ,,,,,,,

l 9 I l VALVE TO PIPE COMPARISONS P

                                                        \

O l l l I l l l l I potel engineers huntsville, clabama l 8-GG

1 rv v' 8 TitleXaucs r. P_ter__C_.2censuovs /6") Job No. O 'L"Lo J ' By 71 O O ____. Dates /u/83 Ckd by 22 Date '{ b's s > , I YRLYE *

c. = _. m , o rg= 6.8 4 3 8 in, c Agwg g ss oo g
c. = t . s in. ,

r . - ( c ,* - e c ) , / v =masis s = % = izis ia - Pipe : SA 104, G r. Ih w Au = o 3'8 E s = m.ga a.r ss., u T 0 9 \'N O A LL.o v e ttooo g

   ,l Ru o%w           g              =  f96      */,

rie r I VAur R.E R,,,g 1294 o S l ym.v/s,,,, - n s6 ~7. l l1 !t 1 l1 O Patel Engineers Huntsville, Alabama B - (27 p . g e s o. _ . .. . . _

O DETERMINATION OF HYBRID WORST ' CASE OPERATOR LOADS O patel engineers ' huntsville. Clabama B-6a  : f

a

.I     r v v'J I      I           Titla       ZdM_ h &'m / - 4 19" Job No. OL.t o By     974 8            Date 4'Ar/93 Ckd by f2h                      Date < 'sa O        Le m s To t.A2vE          Wa i s 9 r = 17 1.o 16        pl Acr = 3. !5 73 %
  • C.G. LocaTio V
                               -x = - 7 ~5. 5 - 1. 4 t = - 14. q t Q = - 8. 0 0 5 - 9. H = -lo. 4 0 5 E= S . S - 7. 8 = - 9. 3
                                               ~

7"og quJr = 6 3 / 7.o A /6 o S ETYts W K/Gfra/3of /4 /MA3C a 3.3 TT3 lh$$fa l C. . Cr Loc.arioN x = - 1.3 5 - 4.19 - c.19 = 'L l . B 8

.I                            3 = - 8. 005 ~ 8. 0 -r- C. 8'L = - 6. t G S E      3.5 - 7 94 = - 3 74 I                               7 op,.que = 6 33co A /4 Com Pof s T"E          wof ST~   PassaBiE C RC5         LJEI6tfr = I3oS      B <.t'Gb 7 = - 17. O B       B calt%

i d Q :. ~/O.40S E=-43 fl- Ep T~ot.quK 633eo A /4 1 I I l l O Patel Engineers Huntsville, Richumn B-ro 9 . ,,,,,,,,

2 ) A?PENDIX C STATIC ANALYSIS HYBRID " WORST CASE" ASSDIBLY 4 , s j 4 potel engineers huntsville, olobomo __ _ . _ - _ _ . _ _ . _ . _ _ . _ _ _ _ . _ _ _ ______ _ _ _ _ _ ._,.___ _ _ _ _ _ . . _ __.__.. , _ - _ . . . _ . . . _5 _ _

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-l         4    350                      350                                                                                   1 5    1   45

- 6 2 94 l 7 3 63 , i 8 4 4 1 9 5 63 le 6 63 11 7 63 g l 12 8 4 I i I 13 9 4 I l le le 4 1 1 15 Il le 4 t 3 16 12 23 2 17 al IS I 19 I 20 1 625 i 21 4.9087 1.9375 1.9875 2.5 2.5 e 22 1.5

  • 23 2.5 24 10 #

25 0.9985 G.1198 0.1198 1 25 1.25 ' ' 26 0.75 0.0625 0.0352 0.75 1.0 ' 4 27 800 1000 1000 le 10 Q 20 .216E9

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                                             ***** ANALYSIS UPTIONS 8 CARDS Cl ANO C2) ****e WALuf       wARI4hLE     COLUMNS                                                   ..

NAME

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C00 PLEO DLbREES OF FREEDOM KEY I aCOF le ELEMENT CONSTANT TAhLE . . . I RTO 31-I2 REACTION FONCE REY . . .. . I mRF 15-16 EEFERENCE TEMPENATURE . . . . 350.00 THEF l-12 UNIFORM TEMPERATURE , . . . . IbO.00 fuMIF 13-24 ELEMENT RLORDERING REV ... I E0R0tp 77-70 CORE SITE REcuf5fEJ 80CIALI . 00200000 LCM SITE hEQUESTED EOCTALI. . 00307770 ELOCKED WINARy FILE NAMES . . TAPE 3 TAPE 2 TAPfil TAPE 4 TAPfl0 TAPE 12 BLOCE SITES . . . . . . . . . See See 1860 b00 500 500 ' s

                                              ***** ELEMENT ITPES (CARD DB *****

TYPE STIF DESCRIPTIUN REv5ut NOTION 5 NJ Igo1PR Ib BA I 2h 2A 2 3 4h 150 PAR. SOLIO O O 9 0 0 0 0 0 2 94 36 NOut ISOPAN. SHELL 0 0 0 0 0 0 0 0 8 3 63 uuAu. FLAT SHELL e 0 0 0 0 0 0 0 4 4 ELASTIC btAM, J-u 0 0 0 0 0 1 0 0 S 63 4u60 FLAT SMELL 0 0 0 0 0 0 0 0 8 6 h3 uuAU. FLAI SMtLL 0 0 0 0 0 0 0 0 7 63 OuAH. FLAT SMtLL 0 0 0 0 0 0 0 e a 4 Lt45 TIC 6EAM, J-D 0 0 0 0 0 1 0 0 w 4 tLASTIC BfAM. J-0 0 0 0 0 0 1 0 0 0 0 0

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                                                                                                                            ***** LLEMENT WEFINITIONS (CAAD El essee L L E Nt'N T                                                NO?t5                                   NAI ITPL CLAS5                 ILLMENT atat CON $fANT$

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l l l AN57% - ENielNf ENING ANALY%B5 SY5 tim Nlvlbl0N 3 esp 0AIE 6?Lt CvRRii6 JUNt 1,1970 i sv4N50N ANALySth SystEp5. INC. MOUSTON. PE NN5f Lyaatl A IS342 P40*ef 14179 T46-330e , TOR 0it 63304 IN Los 2.54TS 83/ 3/30 cpm 500.644 LOAD STEP NUMet R e 2 e.*** loa 0 STEP OPil0NS ICARus L AND pp eene. v&Luf vaHIAHLE COLUMNS I NAML LOAD STEP MET . . ... .. . I RDIS 2-3 1[4PERATUNE MEY . . . . ... O MTEMP 4-6 i 8 NUMMER OF ITERATIONS. . ... I NITTEM T-9 SYNE 55 PRINT 001 FREQUENCY . . 2 MRINT 10-12 ilmE AT END OF LOAb STEP. . . 8. TIME 13-24 *

  • lTER FREO OF POST ELEN. DalA I IFED 49-51 (CAND MS llER FREO OF POST NODAL Dal A I If MO 52-54 (CARD MS ITER FRE0 OF POST REACT. UatA I IFR0 55-57 stawo el Ul5PL. PRINIQUT FREQUENCY . . 2 NDPRNI T0-12 (CAND na l ***** SPECIFIED DiSPLACtMENis ICARO at ***** .

1

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                                      ***** SPECIFito toRCES eCAwD 03 *****
40. Muut DIkECTIuh W ALut 3 $30 Ma -63300.0 d 600 ms 63300.0 es*** LOAb SumeFAWY - we Ol5PLAC1kENTS 2 FORCL5 0 PRE 550 pts *****

e KAXInum SilFFhE55 = .34Joi4E*l2 AT ELtrENI 169 GCENINUM SilFFhtSS * .354FF2E+0i AT LLLMENT 276 Mla ism)M th-CONE WAVE f RONT aLL0uto FOR RtoutSTED MEMORY agita 16v OCTAL STORA6E RE0ulREMENTS PO4 WAVE FRONT MATMla SOLUTIow CP= F30.Sm6 CORE = 0014271J ufMORY= 40tf4040 TOTAL = 402374J3 ptMOR, AvalLABLE. 3e30777e M2sinuN IN-CORE WAVE FRONT GEGUAi!0N51 USED= 246 TIME AT START OF 6ACM SumbilTUTION CP= F30.585 tutP= 2 ITERATION = 1 yr... .,m... e** STEP 2 ITER I COMPLETE. Tint a S. eDI5= 1 NILMP= 8 Cuse. II P.= 2 9 NEm IITLE= s DIRECTI0ee ACCEL w

                        +

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                "            *** "       *"**       -          ma===se       enemmun     m             m             m         w                      e      --     .

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                        ***** LOAD STEP OPTIONS GCApuS L Apeu Mt              ****e vALUE           V AN t ateLE      COLUMNS feAtet i

LOAD STEP REf . . . . . . . . -2 abl5 2-3 TLMPERATURE MEV . . . . . . . O RIEMP 4-6 3 NuMtfER OF ITERATIONS . . . . I glilElf T-9 STRESS PRifef 0UT FRE00(NCY . . 2 NPRINT 50-12 I TIME AT E*e0 OF LOAO STEP. . . O. TIME 13-24 ITER FREO OF POST ELEM. 0AIA I IFE0 49-51 (CAND M3 ITER FREO OF POST NODAL Dal A I IF NO $2-54 gCAw0 49 ITER FREO OF POST RtACT. DATA I IFR0 SS-ST (CAwo Mp DISPL. PRINTOUT FREQUENCY . . 2 NDPANT 70-T2 ICAND P3 . C00H0IesATL ACCELENATIONS 366.40 9. a. f I .

                      * *
  • L O AD IN6 CHA***E S * *
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                                                                                                                                                                        . p-s.. z ee . ..
                      ***** SPECIFIED PORCES (CARD 0) .....                                                                                                       .

O

    'h      NO.         NOOE       OIRECilDN           VALUE 1           530        MR       0.

j 2 600 MX 0. j OCT AL STORA6E REGUIREleE*ef S P_0R esEw LO AD ON OLO SilFF. Mar oIN CP= 1826.25 T < CCRE= 00142Til tee MOR T = 000e7021 TOTAL = 00lS2012 MEMOR, AVAILawtEm ett0TTTO I TIME Af START OF BACM SUbbilfUil0M CP= 026.267 ttEP= 3 ITERAllON* I . ese STEP 3 ITER I CuMPLETE. TIME = 0. =0IS= -2 MTLMPs e Ctm. ITFP.= 3 NE g IITLE= v OIRECilON ACCEL I i

ANSYS

  • tMGltettklNG ANALf 555 5V5 Tim ht v l5 3 0*e J UPuAft 6fti Cve=pli6 Juset I.teFw SuAN50a0 ANALYSIb SYSTEMbe thC. HOUSIO88 PENNSYLV ANI A 15342 Pre 04t 14123 106-3304 Y DIMELitum ACLLL R.ee61 R3/ 3/30 Cre n53.sti LOAD SILP huMhte * *
                                                                                                                                ***** LOAD STEP DPil0N5 IC ARDS L AhD MI ***ee WALUE         VANIAmLE     COLunN5 NAME LOAD STEP mEv . . . . . . . .                                                          -2            mDIS            2-3 ithPER AiuME stEf . . .....                                                            O            NIE seP         a-6 NUMUER OF liERATIOsas. . . . .                                                          I            NiiiEM          i-9 STRESS PRlteTOUT FRE00EpsCY . .                                                         2            kPRINT         10-12 ilME At thu 0F LCAD STEP.                                                   . . S.                TIME           13-24 litR FREO OF POST ELEM. DATA                                                           I           IFE0           49-58 ICARD M3 ITER FRE0 0F POST De00AL Dal A                                                         I           IF NO         52-54 ECARO MI ITER FREO OF POST NE ACf. paiA                                                         I           IFR0          55-57 4Cau0 ma DISPL. PRINTOUT FREQUENCY .                                                     .       2            hDPRNi         70-12 4CA40 MI C00MolNATE ACCELENATIONS                                                           e.             386.40     n.
                                                                                                                               *** LOADING CMAhesES ese
                                                                                                                                                                                                                                                    .- - --- e.ee-.-

OCIAL 510RabE REQUIREnENil POR DeEW LOAD Ost OLO SilFF. MAyelE CPe 923.242 p CONE = col 42FFl MEMORY = 4000F028 TOTALS 80152032 NEse0R, AV AltadLEe sele 1Fie CP= 923.251 tvtP= 4 liENail0Ne l Q IINE AT STANT OF bACE SUIshiliufl0h b e Cape. IIIR.= 4 O *** SitP 4 ITER I COMPLETE. TIME

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 !          TEMPLRATUNE KEY . . . ....                   O            RTEMP            4-6

, NUMetR of ITERATIONS. .... I FITTER 7-9 l STRESS PRINT 0UT FREQUENCY . . 2 MRINT 10-12 ilME AT Ehu 0F LOAD STEP. . . O. TIME 13-24 ITE R FREO OF POST ELEN. DAIA I IFED 49-58 (CARD MD 11ER FREO OF Post N00AL DaI A I IF NO 52-S4 GCARD MD litR FPEG OF POST REACT. DATA I IFR0 55-57 GCAMD MB DISPL. PklNf 00T FRELUENCY . . 2 NOPRNT 70-72 GCARG N) COONDINATL ACCELERATIONS 0. 8. 106.40

                          *o* LOADING CHANbES ***
                                                                                                    /

OCT AL STORA6E REculREMENTS F OR NEW LOA 0 ON OLD SilFF. MAvoIE CP= 1821 163 * *** CONE

  • 00142Fil MEMORY
  • 00007021 TOTAL = 00152012 NEMOR, AvalLAblEs 00307770 f? ilhE AI START OF DACM SUHbtfiUil0N CPe 8021.172 gYlPs 5 ITERAllDN8 1 b
       '* *ee STEP         5    tier     I CDaPLETE. T I ME =    0.              wul5= -2     RTLMPs   O   CUM. ITER.=          5 eseee PROHLEM COMPLETED esee.            CP e 194R.985

, END OF input EkCOUNTERED ON FILE TAPERS E N Tt R / NOTES Cako AFTER FIN 45N CARO 80R Ai ANT C ARD-A LEwFLI ' F0W DET AILED N0f t5 DN FE AIURtS. CHANGFS. Nt LPe ETC. seese RUN COMPLE TED seees LP = 1948.944 ) esee. ANSYS TWu OIMENSIONAL PLOTS *ee** l esee* eeeeeeE.ND PLOTS eseee

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1 a i l 4 I t APPENDIX D MODAL ANALYSIS. l f l 1 i i r s I i

l
!                                                                                                                                                                                     I 1

\ l potel engineers huntsville, clabama i M

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, BETTIS VALVE ASSEMBLY MODAL ANALYSIS i

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  • e SWANSON mNALYSls SYSTEMS.INC. 15 ENDEAv0 RING TO NAME THE AN5YS PMUGRAM AS COMPLLIE. ACtDRATE. an D E ASY TO USE A5 POSSIOLL. SUGGE5fl0N5 AND COMMENTS Apr bELCOMED. ANY ERRORS thCDUNTERED IN EITHER THE DOCU=rNTAil0M OR THE RESULTS SHOULO BE IMMLUIATELY UROUGHT ,0 OUR ATTENTION.

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  • WE AC T I ON F 04CES * * * * * *
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  • 25 F2 208.743 26 F2 255.433 2F F2 429.244 29 F2 612.496 IDF Fs 2300.06 108 Fu 554.777 109 Fa 434.250 lie Fa 262.Al7 lli Fa 319.vi5 182 Fa 33n.l?6

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