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| REVISION A TECHNICAL REPORT PE!-TR-83-13 APEi.,8, 1983 ,
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| LEVISION A SEISMIC QUALIFICATION ANALYSIS OF C.IDW 24-INCH WAFER STOP VALVE JOB NUMBER 82-2053-06(N),-07(N)
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| ITEM NO. 1.1, 1.7 24"-HBB-BF-MO-57-115 24"-HBB-BF-MO-57-135 24"-HBB-BF-MO-57-147 24"-HBB-BF-AO-57-114 I 24"-HBB-BF-AO-57-123 3 24"-HBB-BF-AO-57-124 I
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| N. ALLE DAVIDSON
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| ; I PREPARED FOR BECHTEL POWER CORPORATION j la ,
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| FOR PHILADELPHIA ELECTRIC LIMERICK PLANT IN ACCORDANCE WITH BECHTEL SPECIFICATION NUMBER 8031-P-144, REVISION 1 I Work Performed Under Clow Purchase Order Number 30-10469 Bechtel Purchase Order No. 8031-P-144-AC, Items 1.1 and 1.7 f Patel Job Number 8220 i e for Clow Corporation, Engineered Products Division Westmont, Illinois 1
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| ,- , huntsville, alabama ,
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| 8308090016 830802 PDR ADOCK 05000352 A PDR
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| Report No. PEI-TR-83-13
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| .m Page No. 1 REVISION A l
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| l REPORT NO.: PEI-TR-83-13 l
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| PREPARED BY: @,/2dIw 1m . S N. Allen Davidson APPROVED BY: w[ ['
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| John .J ins, Vice-President Q.A. REVIEW: _
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| wp MM pJoyfeKlutts,QualityAssuranceAdministrator ORIGINAL ISSUE: April 8, 1983 I
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| 10 .
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| REVISIONS .
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| REV. REV. REV. CHECKED Q.A. DESCRIPTION OF CHANGES NO. DATE BY BY BY AND PAGES REVISED
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| ! A 5/17/83 Nb JFJ #
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| JK Page iv - Change " Input" to
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| { RPP h,% -"Analysis" and "Frequenc3 "
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| ~
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| Page 8 - a b F" to "340 F' ,
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| l Page 15 - Change "350 F" to "340 F" ,
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| i Appendices Title Page - Change
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| " Input" to " Analysis" and " Frequency"
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| to " Modal".
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| Page B21 - Change "95469" to "9549E ".
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| l Page B80 - Add "24 Igeh" to title.
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| PageB83-Chgnge"t /Fvb "t "t /F vb l
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| . PEI Form No. 611 - 7/1982 patel engineers i huntsville, clabomo
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| Report No. PEI-TR-83-13 .
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| Page No. ii O
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| s CERTIFICATION OF CONFORMANCE This is to certify that the Clow 24-inch Wafer Stop Valve described in Patel Engineers' Technical Report PEI-TR-83-13 has been evaluated to determine its compliance with Bechtel Power Corporation Specification 8031 -P-144, Revision 1 as described herein. The information contained in this report is the result of complete and carefully conducted analys es and to the best of my knowledge is true and correct in all respects.
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| 9Mk Robert Parker Professional Engineer Registration No. 13143 iO- State of Alabama j ty>BAm?
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| I Report No. PEI-TR-83-13 i, Page No. iii i
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| ABSTRACT A seismic qualification analysis was conducted to verify the structural in-tegrity of the Clow 24-Inch Wafer Stop Valve, Job Number 82-2053-06(N),-
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| d 07(N), for Bechtel Power Corporation for use in Philadelphia Elec tric Limerick Nuclear Plant. A finite element model was developed to simulate j valve components. The model was subjected to static seismic accelerations
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| ] plus normal operating load environments and were shown to conform to the ASME Section III - 1980 Edition through and including Sununer 1981 Addenda as described in Bechtel Power Corporation Specification Number 8031-P-144, Revision 1.
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| .--. l Report No. PEI-TR-83-13 j-
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| - /' 6 Page No. iv REVISION A I
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| TABLE OF CONTENTS l
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| PAGE 1.0 IN TRODUCTORY
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| ==SUMMARY==
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| . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . I 1.1 Introduction............................................... I 1.2 Summary of Resu'1ts......................................... 1 1.3 Conclusions................................................ 5 1.4 Limitations................................................ 5 6
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| ==2.0 DESCRIPTION==
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| OF 24-INCH STOP VALVE. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 6 3.0 DESIGN ENVIRONMENT SPECIFICATION................................ 8 -
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| 3.1 Seismic Environments....................................... 8 3.2 Operational Environments................................... 8 4.0 TE CHN I CAL AP P R0 ACH . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 9 I(D) 4.1 General....................................................
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| 4.2 Finit e E lement Rep re s en t a tion . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
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| 9 9
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| 4.3 Modal Analysis............................................. 10 4.4 S ta t i c Ana ly s i s . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 10 4.5 S tr e s s Ana ly s i s . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 11
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| ==5.0 DESCRIPTION==
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| 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 DEFLECTIONS OF MAJOR COMP 0NENTS . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 27
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| . 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 l
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| : NODAL DISPLACEMENT DATA !
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| APPENDIX G ANSYS POST 25 VALVE DISC AND ADAPTER PLATE NODAL l l STRESSES AND DISPLACEMENTS l n
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| 4 Report No. PEI-TR-83-13 f Page No. v LIST OF ILLUSTRATIONS l.
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| FIGURE Page 1 Clow 24-Inch Waf er S top Va1ve . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 4
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| . 2 ANSYS Calcula ted Mas s and Centroid Information. . . . . . . . . . . . . . . . . . . 7 I
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| 3 Valve Body Max S tres s Plo t z = 1 Sec tion Cut . . . . . . . . . . . . . . . . . . . . . 18 4 Valve Body Max S tres s Plo t z = 3 Sec tion Cut. . . . . . . . . . . . . . . . . . . . . 19 I
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| 5 Valve Body Max Stress Plot z = 5 Section Cut..................... 20 6 Valve Body Max Stress Plot : = 6.5 Section Cut................... 21 7 Ad ap t e r P la t e Max S tre s s P 1o t . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 22 o 8 D i s c M ax S tr e s s P 1o t . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 23 o
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| It LIST OF TABLES
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| :l = TABLE 1 Modal Participation Factors for Clow 24" Valve Assembly. . . . . . . . . . 2 i
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| 2 Stress Ratios for Clow 24-Inch Wafer Stop Valve q 4.5 g Seismic conditien.......................................... 2 3 M ax im uc De f le c t i o n . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 3 4 Summa ry of Allowab le S tr e s s e s . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 25 5 Net Reaction Forces at Boundary Nodes............................ 26 i
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| - = . . .. . . _ - ,-
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| t Report No. PEI-TR-83-13 I.' .
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| Page No. I 1.0 INTRODUCTORY SUle(ARY i 1.0 Introduction ,
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| This report presents the results of seismic qualification analysis of ,
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| ' a 24-inch . diameter stop valve for the Limerick Nuclear Plant. The '
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| . analysis was performed for the Clow Corporation, Westmont, Illinois, i in accordance with Bechtel Power Corporation Specification .8031-P-144, I Revision 1. .
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| Complete details of valve geometry, structural components, and assemblies are given in the engineering drawings of Reference 1.
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| id -
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| The basic approach taken for this seismic qualification analysis was:
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| '[ o Utilize finite element techniques to formulate a ma the-matical model of the valve; l
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| ; o Calculate valve fundamental natural frequency; il i
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| o Apply the static analysis method to determine stresses, forces and deflections for operating and seismic loading conditions; and o Calculate resultant . stresses against appropriate
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| ; allowable stresses.
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| 1 The ANSYS finite element computer program developed by Swanson Analy-sis Systems, Inc., Houston, PA, was used to develop a mathematical j model and to determine frequencies, stresses, forces, and displace-L ments. ANSYS computations were performed on the Control Data Cybernet System. This public domain program has had sufficient history of use lr to justify its applicability and validity.
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| 1.2 Sussnary of Results A frequency analysis of the valve syst'em yielded a fundamental natural frequency of 86.2 He for the Bettis operator assembly and 85.5 Hz for the Limitorque operator assembly. Table 1 represents participation i factors for a few key frequencies.
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| Application of the operational loads and the seismic design environ-ment specifications of Section 3.0 gave the stress ratios contained in Table 2.
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| Report No. PEI-TR-83-13
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| : l. Page No. 2 Table 1. ,
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| , Modal Participation Factors for
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| .- Clow 24-Inch Wafer Valve Assemblies ITEM NODE FREQUENCY PARTICIPATION FACTORS (HZ) -
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| NO. X Y Z Limitorque 1 85.5 -0.557 1.682 -1.428 Motor ,
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| Operated 2 97.0 1.997 -0.228 -1.03 !
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| Valve
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| ;la Assembly 3 234.8 0.889 1.583 1.499 Bettis 1 86.2 1.867 -0.4328
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| -0.6138 Air Operated 2 94.3 0.1346 1.852 -0.8393 Valve ,
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| Assembly 3 253.8 0.7258 0.7807 1.834 Table 2.
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| 'IO Stress Ratios for Clow 24-Inch Wafer Stop Valve 4.5 g Seismic condition b1RL55 RATIO IDCATION (S TOTAL /S ALLOWABLE)
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| Valve Body 0.23 I
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| Disc 0.40 Drive Shaft 0.79 l
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| Adapter Plate 0.34 3/4-10 UNC Operator to g Adapter Plate Bolts (Limitorque) 0.61 3/4-10 UNC Operator to l
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| Adapter Plate Bolts (Bettis) 0.57
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| , 1 1/2-8N Valve Body 0.19 to Adapter Bolts l Cover Plate 0.92 5/8-11 UNC Cover Plate Bolts 0.01 Q
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| Page No. 3 i Full descriptions of all stress calculations are given in Section 7.0 !-
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| 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.
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| Ta'ble 3.
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| Maximum Deflection DEFLECTION IN CIDBAL COORDINATE DIRECTION
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| * IDCATION X(IN) Y(IN) Z(IN)
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| Operator C.G. 0.016 0.011 0.014 Valve Body 0.006 0.005 0.004 I
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| Adapter Plate 0.014 0.005 0.004 i.
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| Disc 0.0006 0.0003 0.0009 l
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| [o
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| * Refer to Figure 1 for definition of coordinate directions.
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| Descriptions of all deflection calculations are given in Section 8.0 I .
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| : c. huntsville. clabama 1 .- - - - - _ - . - . _________
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| Report No. PEI-TR-83-13 Page No. 4 1
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| < 2
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| s !! 1 MIDQ[M 4N$1$ 4 LLSJ 24 14CM VA v! 't! 0220 i!MERICK MPP l
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| Figure 1.
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| ! Clow 24-Inch Wafer
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| . Stop Valve
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| Report No. PEI-TR-83-13
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| [ h Page No. 5 V
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| 1.3 Conclusions I
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| The conclusions drawn from this seismic qualification analysis of the
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| [
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| Clow 24-Inch Stop Valve Assemblies are as follows:
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| : 1) The valve's major compcnents, as analyzed, do not exceed ASME allowable stress values as described in Bechtel Specification 8031-P-144, Revision 1.
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| : 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.
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| 1.4 Limitations The analysis was performed on the structural drawings of Reference 1, 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:
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| : 1) The results do not apply to design, materials, and environments not contained or identified in the above re ferences .
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| I (%J''} 2) Neither pipe structures nor operator structure are included in the qualification ana1><is.
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| : 3) The results do not apply for structural changes or alterations not identified in this ~ report. ,
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| ' Report No. PEI-TR-83-13 I, Page No.'6' 'l O- l l k' 2.0 ' DESCRIPTION OF 24-INCH STOP VALVE JOB NUMBER 82-2053-06(N),-07(N) i i The valve has a 24-inch nominal diameter and is configured as shown in b 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
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| operator model .NT820-SR4-S or a Limitorque SMB3-80-H5BC. A sealing
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| (: gland is located in the operator end of the valve body, thus ' making' the adapter section and operator non pressure boundary components.
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| Full structural descriptions of all valve components are given in the l-complete set of structural drawings of Reference 1. Bettis and Limitorque operator inertial definitions are given in Reference 2.
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| ,' Figure 2 presents mass and center of gravity information for a hybrid worst case operator / valve assembly. This hybrid operator.was taken to
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| 'g be the most massive of the two operators with the worst-case center of j gravity combination possible.
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| analysis only. For This hybrid was used for the static determination of worst-case hybrid, see ..
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| appropriate sections of Appendix B. Each proper weight and C.G. was used to - determine frequency data for each valve assembly. The valve I- (without operator) data were generated by the ANSYS Computer program from the mass information of all elements in the mathematical model.
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| The data for .the valve with operator were generated using the finite element model used to determine loads, stresses, and deflections.
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| Report No. PEI-TR-83-13 ;
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| Page No. 7 l y
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| NOTE: XY ORIGIN AT CENTER OF DISC /
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| Z ORIGIN AT BACK FACE i
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| l l 'X unu 24 inen vatve et s22o tintance ner creatiti aasi! 3 ACTUAL MODEL CENTROID COMPONENT WEIGHT WEIGHT (LB) (LB)
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| X(IN) (IN) (IN) t l
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| Valve 1663 1653 -5.929 -0.269 3.49 '
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| Operator 1948 1948 -31.695 -14.56 -11.785 Valve & Operator 3611 3601 -19.781 -7.998 -4.773 i
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| I.
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| Figure 2.
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| ! ANSYS Calculated Mass l And l- Centroid Information j
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| Report No. PEI-TR-83-13 i:
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| Page No. 8 REVISION A 3.0 DESIGN ENVIRONMENT SPECIFICATION I':
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| 3.1 Seismic Environments Leading Conditions Horizontal Vertical Specified Seismic Loading 4.5 g 4.5 g 3.2 Operational Environments l '* The operational environments for the subject Stop Valve are defined in 1 References 1 and 3 and are summarized below:
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| o Design pressure = 285 psig o Differential pressures = 65 psig o Design temperature = 340 F A L.
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| o Seating torque = 135,000 in.-lb Reference 3 notes that the temperature is uniform ad thermal gradients are negligible.
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| N Report No. PEI-TR-83-13 Page No. 9 ,
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| i 4.0 TECHNICAL APPROACH b
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| .1 4.1 General The technical approach was formulated to ' provide a high technology '
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| analytical solution to the seismic qualification of the subject valve.
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| The analytical methods identified herein were selected to insure com- ,.
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| pliance of the qualificati6n program with controlling documents such as Bechtel Specification Number 8031-P-144, Revisien 1, IEEE 344-1975, and industry guidelines and standards as represented by NRC Regulatory 1 Guides.
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| A ' finite element analytical approach was selected to develop a ma the-I 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 I
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| including stresses, forces and deflections. A brief summary of the analytical approaches for these various types of analyses follows. . ,
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| 4.2 Finite Element Representation
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| 'The structural problem is defined in terms of geometric node point
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| { location, structural finite elements that connect the node points, and
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| ; nodal masses that describe the inertia characteristics of the struc-
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| . 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] is synthesized from the stiffness -of the element [k].
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| ! This is accomplished through the coordinace transforma-tion [6], into (global) coordinates. The general equa-tion for this stiffness relationship is
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| -[K]-[55[k][8]
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| !f o The mass matrix [M] of the complete structure is formed from the elemental consistent mass matrices and the in-put lumped mass values.
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| O -
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| i Report No.-PEI-TR-83-13 ;)
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| Page No. 10 .
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| ~O
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| -4.3 . Modal Analysis The modal equation
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| ([K] - w g [M]) {&g) = 0 where"
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| [K]- = the reduced stiffness matrix of the structure
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| {M] = the reduced mass matrix of the sturcture wg = the eigenvalue of mode i (g) = the eigenvector of mode i is solved for the eigenvalues wg and the eigenvectors ( 4 g) of the system. The eigenvectors calculated by the ANSYS program are orchenormal; that is, they are normalized such that the generalized I
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| mass for each mode equals unity, T
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| ( &g) [M] (.$g) = Gea. Mass. = 1
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| ) Once the modal solutions are obtained in terms of the dynamic degrees d' of freedom, the eignevectors can be expanded to the full set of
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| , displacement degrees of freedom, if desired.
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| 4.4; Static Analysis tl For a static seismic analysis, accelerations, n., are applied to the
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| 'l mass matrix [M]' co form an inertia loading matrix (F) for each seismic
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| ;or gravity condition:
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| (F) = n g[M] where og is the acceleration constant.
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| The static equilibrium equation (F) = [K](d) is solved to obtain the displacement (d). From these displacements,
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| - the forces and stresses within each structural element can be calcu-lated. Each of the three coordinate directions is evaluated separately and the results superimposed on a Square Root of the Sum of the Square (SRSS) basis with the operational conditions added by absolute sum:
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| 2 a static + c +
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| *I***"E"l strese due to static seismic '
| |
| , o "
| |
| static .
| |
| , acceleration ;
| |
| = elemental stress due to dead weight or o ,,,,ggy gravity
| |
| / -
| |
| '" = elemental stress due to operational loads. j o operational
| |
| .4.5 Stress Analysis s -
| |
| : p. s - , Stress values for all structural elements in the. mathematical model N ,are determined independently for each seismic excitation direction, s for dead weight, and for each operational load. Each of these types j of load constitutes an = individual' , load case. All load cases are ,
| |
| J ' suunned 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 IO the valve, therefore, it is capable of reproducing stress levels in all components and at all interfaces with high accuracy.
| |
| , The particular load cases for the su$ ject valve are defined' by the I . design environments of Section 3.0 and are as follow:
| |
| y , o Load Case 1 - Design pressure, 285 psig and 65 psig differential pressure across disc;
| |
| [
| |
| o Load Case 2 - Seating torque 135,000 in.-lb; l o Load Case 3 - Stac'ic x-direction seisnie acceleration; L s o Load Case 4 - Static y-direction seismic acceleration; 1
| |
| . q 5
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| x potel engineers huntsvik, olabomo
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| y . . - . -
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| 4 f
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| 1 i
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| . Report No. PEI-TR-83-13 [.
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| . Page No. 12 i' o Load Case 5 - Static s-direction seismic acceleration; I 4 l o Load Case 6 - Gravitational acceleration.
| |
| 1
| |
| . :l Total stresses resulting from the above load cases are compared with '
| |
| I 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, Sectien III, Appendix XVII, subsubarticle 2460.
| |
| STRESS STRESS IDADING LIMIT FOR LIMIT FOR COMBINATIONS STRUCTURAL COMPONENTS BOLTING Seismic condition "S" f /F tb + v F vb loads, and design-loads 1
| |
| i S = ASME Allowable Stress at Design Temperature f, = ,.n.11. Str.ss l ,,, = m o..bie Tens 11e Stress f,
| |
| = Shear Stress F
| |
| vb
| |
| = Allowable Shear Stress
| |
| ;c Maximum stresses resulting from the seismic and operational loads are i compared with the ASME allowable stresses. This comparison is jj presented in the form of a stress ratio as:
| |
| w Stress Ratio = Maximum Stress
| |
| , , Allowable Stress ,
| |
| i !
| |
| Stress ratio values which are less than 1.0 indicate acceptable stress
| |
| : levels which are within satisfactory ASME design limits for stress
| |
| ;l allowables .
| |
| il
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| !l n
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| O -
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| potel engineers
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| ; huntsville, olobomo
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| -..._,,.-m--.._-.,,_,,._,,,,m. - -
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| , , , _,-c.._..__,,,_,,.M_m.m__._,.m.,_-,- __m-_m,._m--._,%. _ , ,,-, , . . . . . . . . .
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| Report No. PEI-TR-83-13 l I' -
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| Page No. 13 !
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| | |
| ==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 besa 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 ehell element with both bending and membrane capabilities, in plane and normal loads permitted, normal pressure loading available, six degrees of freedom per node.
| |
| o Generalised mass element - a point mass element hav-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-g , dimensional modeling of solid structure, eight nodal points define the element with three translational
| |
| [f degrees of freedom per node, pressure loading is avail-able, o Sprina-?amper - massless spring element with longitu-dinal or torsional capability in one, two, or three dimensional applications.
| |
| , o 10 Node Isoparametric thick shell -
| |
| element used for <
| |
| l three-dimensional modeling cf solid structure, ten j nodal points define the element with three trans lation-g~ al degrees of freedom per node, pressure loading is available .
| |
| A mathematical model was developed using the above finite elements.
| |
| This model was formulated 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 dynesic and operating load' environments.
| |
| f I D jo potel engineers
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| ! huntsville, clotmmo I
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| -' ewe' -ygiu mer Sm-w-py -yw--g-- ,,-- i,-e.&4 ygr-- y yeymeesyr- we.-weiyye.e, -p. ,-g.- wvmegg--y- p .,g--.y g
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| I Report No. PEI-TR-83-13 I Page No. 14 O
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| I :
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| 1 The ANSYS finite element model of the assembly consisted of:
| |
| o 550 nodes o 226 isoparamet'ric solids o 8 isoparasietric thick shelle o 52 beam elements o 54 quadrilateral shells o 2 springs
| |
| =
| |
| o 1 concentrated mass These elements were described in several local coordinate systems to 1 facilitate the description of the various major components. Each was referenced to the global coordinate system so that all final outputs 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 234 three-dimensional solid elements which reproduces the flexibility of the body at all of its
| |
| , intersections with other valve components. The nodal picture of the
| |
| ;l valve body is shown in Appendix A. The body was developed with two
| |
| ;s levels of elements through its thickness, except in the neck area where there are 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 I elements with proper section properties to simulate its inertial char-acteristics. Pressed against the seat ring is the disc, which was modeled using 24 quadrilateral shell elements.
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| ;u O--
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| patel engineers
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| : huntsville, olobomo
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| }
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| ., .x i
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| Report No. PEI-TR-83-13 Page No. 15 REVISION A The effects of seating the disc against ~t he ring was accomplished by !
| |
| . using coupled nodal displacements. This mathematically " coupled" l selected nodes on the seat ring to selected nodes on the disc. Any displacement in one node of the coupled set was limited by the resis-tance to displacement of the other node in the set. .
| |
| The dise 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
| |
| 'I the static analysis, the Bettis operator place was used in the model 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 determination).
| |
| The shaf t was modeled with beam elements with properties that provide proper load carrying characteristics of the shaft. The shaft pene-
| |
| 'i crates the valve body in the plane between the two middle section thicknesses of the body. Bearing forces are transmitted to the valve m body at. bearing locations by use of coupled nodes. The shaft is 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.
| |
| The operator was modeled with a lumped mass element at its center of gravity and very stiff beam elements froni the mass to the operator adapter plate simulated the rigid operator body and housing. For the si.atic analysis the worst possible mass, C.G. location, and torque was used. Again for modal analysis, appropriate mass and C.G. locations s were used for the specific valve assembly.
| |
| The shaft and operator section was modeled such that disc loads would not be transmitted through the shaf t 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.
| |
| The physical properties of the various materials in the valve were taken from ASME Section III Appendix I, Table I-6.0, for a design temp-erature of 340 F. A l
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| potel engineers huntsville, alobama .
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| i l
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| Report No. PEI-TR-83-13 4 Page No. 16 l
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| 6.0 RESULTS OF VALVE FREQUENCY ANALYSIS A tuodal 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 86.2 Hz. The lowest fundamental frequency of the Limitorque assembly was found to be 85.5 Hz. The C motion of these modes are ch pacterized by a bending motion occurring in the operator adapter plate section. This represents a lower bound l- frequency of this mode due to the very conservative modeling assump-tions made in this area. There is no stiffness representation of the
| |
| [~
| |
| yoke on the operator housing which would add considerable stiffness to the operator adapter plate. In addition no friction coupling between the adapter plate and valve body was taken into account. The operator I loads were transmitted to the valve body only at bolting locations.
| |
| The first valve body natural frequencies occurred at 94.3 Hz for the I Bettis assembly and 97.0 Hz for the Limitorque assembly. This motion was characterized by a torsional mode coupled with a valve neck weak axis bending motion (parallel to pipe).
| |
| I Participation factors for a few key resonances are given in Table 1.
| |
| These participation factors are calculated for each excitation direc-tion and indicate participation or activity of each mode in that direc-I tion. For a static analytical approach, as in this case, the partici-pation factors serve only to provide ' insight into the character of the modes. .
| |
| Total frequency analysis for both valve assemblies are given in the appropriate section of Appendix D which lists pertinent ANSYS print-outs.
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| .I l.
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| potel engineers huntsville, olabomo
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| e i
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| Report No. PEI-TR-83-13 [
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| Page No. 17 i I 7.0 RESULTS OF VALVE STRESS ANALYSIS ,
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| The mathematical model of Section 5.0 was subjected to the following l
| |
| g load cases:
| |
| o Load Case 1: Internal valve pressure of 285 psig with
| |
| . a differential disc pressure of 65 psig 1 ,. >
| |
| o Load Case 2: Seating torque applied to shaft 135,000 in.-lb o Load Case 3: X direction dynamic acceleration 1.0 g o Load Case 4: Y direction dynamic acceleration 1.0 g u
| |
| o Load Case 5: Z direction dynamic acceleration 1.0 g l
| |
| The results from these five individually calculated load cases were conservatively summed as shown in Section 4.4; i.e., dynamic load stresses were combined by SRSS and then combined with gravitational and operational stresses by absolute summation. This was achieved by I using ANSYS - post processing subroutine POST 27 which allows multiplica-tion by scale factors, summations of several load cases by SRSS, abso-lute-sum, or algebraic sua methods. Proper scale factors were used to I bring the g values of load cases 3 through 5 to design environment levels (see Section 3.0) before loads were combined. ,
| |
| 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 flag stresses over the threshold value. This data printout is given in Appendix E. Static analysis input and typical stress printout are I given in Appendix C.
| |
| r By use of ANSYS POST 23, principal stresses were calculated at nodal 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 dynsmic plus operational loading conditions.
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| t h4 patel engineers huntsville, olabomo
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| .s- -
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| Report No. PEI-TR-83-13 Page No. 18
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| *l ll l
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| I
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| ~
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| j N
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| , op%
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| dd I
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| i '
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| 1 BODY SECTION CUT Z=1.0 24 INCH VALVE SMAX ANSYS
| |
| ,P Figure 3.
| |
| - Valve Body i Max Stress Plot z = 1 Section Cut LO p -
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| potel engineers I huntsville, alobomo
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| +. - .
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| . - . . .2, Report No. PEI-TR-83-13 f g Page No. 19 i:
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| I 1 $MRX ANSYS 6 BODY SECTION CUT Z=3.0 24 INCH VALVE Figure 4.
| |
| Valve Body Max Stress Plot
| |
| '- z = 3 Section Cut I0 -
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| I Report No. PEI-TR-83-13 "
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| Page No. 20 l I p\
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| hD f I
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| so p ,r , y / I-n +
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| 1 I
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| 24 INCH VALVE SMRX ANS15 8001 SECTION CUT Z=S.0 L
| |
| f
| |
| .1 .
| |
| j Figure 5.
| |
| Valve Body
| |
| ! Max Stress Plot z = 5 Section cut L
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| ,i O -
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| l
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| .l Report No. PEl-TR-83-13 Page No. 21 !
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| 1-x S3DY SECTION LJT Z=6.5 24 INCH VALVE SMAX ANSYS Figure 6.
| |
| 1 i
| |
| Valve Body Max Stress Plot z = 6.5 Section cut I
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| i l
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| potel engineers
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| ( huntsville, clobomo "
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| !I . * ,
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| Report No. PEI-TR-83-13 Page No. 22 F w ~
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| t t
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| N r
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| %y
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| \
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| lO s X
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| ~#
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| j.
| |
| Sa8' ""5 "
| |
| * w :. i.c. .sn ..se sono casinaties etus secantiac I
| |
| 9 Figure 7.
| |
| Adapter Plate
| |
| : l. Max Stress Plot g
| |
| potel engineers huntsville, olobama i
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| i l~- Report No. PEI-TR-83-13 l- Page No. 23 !
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| l l
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| . L.
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| , ,a I'O I n
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| ~ ,
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| g 3g tesCn VAvg 4.15 6080 CemetsflTIM PLUS SPtRATIC
| |
| #8I WI I t
| |
| Figure 8.
| |
| Disc Max Stress Plot O-potel engineers huntsvik, olabomo
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| _,-,,------,---,,,-w, . - - - . - - - - -,rr, -
| |
| | |
| . . , . . . . . , - ~
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| hl I;
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| Report No. PEI-TR-83-13 Page No. 24 [
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| ,1
| |
| .l
| |
| !l These figures also show maximum stress plots for the disc and adapter k i plate for the loading condition. These plots were made using ANSYS -
| |
| l' POST 25, the same type post processing routine as POST 23 except that. it 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 bolting, are detailed in Appendix B. ~
| |
| The max-imum stressed element was flagged by POST 27 and a detailed stress analysis is contained in this Appendix. l The maximum stresses for all valve components were compared to the allowable stress values of Section 4.5. Table 4 gives the maximum
| |
| " stress in all sections of the valve due to the dynamic loading 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) and the quadrilateral shell eleneents (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 compared to only the ASME "S" allowable stress. The stress levels were found to be well within the allowed limits.
| |
| ,I The drive shaf t stresses were also compared with their allowables and found to be within their limits.
| |
| Cover plate stresses were also compared with the ASME design and Level A allowable stress values. This resulted in a stress ratio well within range. The stress value calculated for the cover plate bolting was also compared to its "S" value and was found acceptable. These calculations can be found in Appendix B.
| |
| g Table 5 lists the load reactions at the support points. For better L understanding of - nodal locations refer to valve body'section of Appen-
| |
| !, dix A. The forces shown in these tables represent the net reaction at l
| |
| 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 8 found in Appendix E.
| |
| L I The section modulus and area at the plane normal to the flow passage through the region c.t the valve body crotch is greater than 110 percent of that for the piping connected to the valve l.. body inlet and outlet nozzles. Also, the allowable stress for 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 gi listed in Appendix B.
| |
| potel engineers hunNvWe, ciabama 4
| |
| -e,av .wc-,-- ..w..-.--, ar.--, , -,,-,--,-,re,,-,,,,-,m-.,,-_ ..,,.~,,-,--.----,<.-p- ------yy-, . - , ,,.c .,-y
| |
| | |
| ~'
| |
| - - - 'm - % ---- -- -
| |
| - ' at l
| |
| ] Table 4.
| |
| Susumary of-Allowable Stresses
| |
| . IDCATION MATERIAL ALLOWABLE STRESS STRESS ELEMENT STRESS
| |
| . (psi) VALUE RATIO l' (PER ASME SECTION (psi) .
| |
| III, TABLES I-7.1 l THROUCH I-7.3) i Valve Body SA 516 17500 4089 106 0.23 CR.70
| |
| :o
| |
| ; Disc SA 516 17500 6930 244 0.40 .@
| |
| CR.70 $
| |
| I
| |
| . m"
| |
| ! Drive Shaft SA 564 34550 27263 267
| |
| * 0.79 $@
| |
| Type 630 **
| |
| I - H-1045 FM
| |
| * 'r -
| |
| Operator Adapter Plate SA 516 GR.70 17500 5891 296 0.34 W 4
| |
| i Y
| |
| ] Adapter Plate SA 193 25000 172150, N/A 0.19* C ,
| |
| Bolts CR.87 8884T '
| |
| 1 Ope rator/ Adapter SR 193 25000 155660 N/A 0.61*
| |
| i Bolts - ( Limitorque ) CR.B7 19076T i
| |
| ; Operator / Adapter SA 193 25000 161410 N/A 0.57*
| |
| Bolts (Bettis) CR.B7 18276T Cover Plate SA 516 (1.5)(17500) 21052 N/A 0.92 :
| |
| GR. 70 =26250 Cover Plate Bolts SA 193 25000 70000 N/A 0.0l* '
| |
| CR.87 N 102T i
| |
| *Per ASME, Section III, Appendix XVII, Subsubarticle 2460.
| |
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| l ,
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| E V
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| Report No. PEI-TR-83-13 s- Page No. 26 t
| |
| Table 5. j.
| |
| Net Reaction Forces at Boundary Nodes FX(LB) FY(LB) FZ(LB)
| |
| . NODE SHEAR SHEAR NORMAL 19 2940 1195 933 20 488 981 723 21 453 591 374 22 267 394 245 23 235 305 240 24 256 317 286 25 466 316 289
| |
| , 26 521 271 217 29 454 259 156 30 359 274 265 31 239 284 284 32 178 30 2 239 i 33 141 362 25 4 34 258 542 378
| |
| : 35 339 980 736 36 1431 1002 776 184 5329 2743 2835 185 5666 6894 3950 188 10454 9919 5375
| |
| -l 189 11390 4206 5273 135 3666 1460 1830 t 136 560 1439 1122 137 567 864 522 138 30 9 453 378 139 222 332 406 140 264 330 448 141 484 268 440 142 541 287 271 145 468 275 238 146 370 221 416 147 250 297 440 148 175 329 415 149 199 433 398 l'; 150 371 806 545 151 319 1416 1078 152 1623 1402 1569 412 10358 1373 3743 413 10678 4316 4272
| |
| - 416 11254 6528 4957 417 14875 3402 5704 y t''s l' \)
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| i . . _ _ .
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| l i
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| Report No. PEI-TR-83-13 Page No. 27 l)
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| \ ;
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| i
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| :l 8.0 DEFLECTIONS OF MAJOR COMPONENTS ,i -
| |
| I Maximum deflections of major valve components resulting from the appli-l, 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 susmaation 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 axis 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
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| il c l
| |
| L l
| |
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| ~ . _ _ . - . _ _ _
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| 4 Report No. PEI-TR-83-13 Page No. 28 l .
| |
| | |
| ==9.0 REFERENCES==
| |
| | |
| I
| |
| [
| |
| : 1. Clow Engineered Products Division data transmitted ;
| |
| included the following items: i 1
| |
| Drawing Number Title D-0704 24" Lug Stop Valve Assembly
| |
| -D-0705A 24" Lug Stop Valve Assembly -
| |
| B-3954 Machining 24" Wafer Valve B-3955 24" Disc and Seal Assembly
| |
| . B-3951 Disc and Ear Assembly (24")
| |
| B-3920 Lugged Body Plate i-B-3948 Drive Shaft (Limitorque)
| |
| B-3949 Operator Adapter Plate (Bettis)
| |
| B-3959 Seat Ring B-3958 Disc B-3952 L.H. Disc Ear i
| |
| B-3953 R.H. Dise Ear B-3967 Cover Plate B-3950 Drive Shaft (Bettis)
| |
| B-3947 Operator Adapter Plate (Limitorque) l 9
| |
| .3 2. General operator definition: G. H. Bettis drawing SPC-9151 Revision C of a Base II NT820-SR4-S operator; ^
| |
| Limitorque Valve Controls drawing 02-442-0498-2 with center of gravity report 1734.
| |
| : 3. Telecon; Allen Davidson, PEI, to' Jim Krueger, Clow j_ Corporation, discussing operational loads and thermal B gradients, C.G. information for operators with accescories furnished.
| |
| : 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 Company".
| |
| l
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| \ .
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| l C -
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| potel engineers j
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| ,, huntsvik, olobomo
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| i REVISION A i';
| |
| APPENDICES '
| |
| APPENDIX A MATHEMATICAL MODEL APPENDIX B APPENDIX OF CALCULATIONS APPENDIX C ANSYS STATIC ANALYSIS A Im APPENDIX D ANSYS MODAL ANALYSIS A r APPENDIX E ANSYS POST 27 LOAD COMBINATIONS APPENDIX F ANSYS POST 23 VALVE BODY NODAL STRESS AND
| |
| . NODAL DISPLACEMENT DATA l-APPENDIX G ANSYS POST 25 VALVE DISC AND ADAPTER PLATE NODAL STRESSES AND DISPLAC K S
| |
| ~
| |
| I These Appendices have been prepared by M,8/d M N. A. Davidson l Approved by
| |
| ,, Robert Parker a
| |
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| |
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| |
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| APPENDIX A MATHEMATICAL MODEL l
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| - potel engineers l
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| ' huntsville, olabamo '
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| l ANSYS MODEL CODING INFORMATION FOR ELEMENT DATA
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| COMPONENT ELEMENT TYPE MATERIAL I TYPE I TABLE Valve Body 3-D Solid 1 1 1
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| - Neck Transition 10 Node 1 2 2 Element Solid Disc Shell 1 3 3 Shaft 3-D Beam 2 4 4 l Adapter Plate Shell 5 5 5 ,
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| Dise Ears Shell 1 6 6 Body to Plate 3-D Beam 1 8 8 Bolts i) % Seat Ring 3-D Beam 3 9 9 Massless Rigid 3-D Beam 4 10 10 Links Torque Spring Spring 1 11 11 I
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| Operator Center Translational 1 12 12 of Gravity Mass 1
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| AND ANSYS INTERPRETATION 69
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| I FIGURE All. DRIVE SHAFT PLOT lk 012-ii..
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| ], APPENDIX OF CALCULATIONS ti e
| |
| i n
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| I O
| |
| I D
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| l 7
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| h
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| 4 4 i
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| j OPERATOR ADAPTER PLATE BOLTING CALCULATIONS l
| |
| l potel engineers
| |
| - huntsville, oloboma BI l
| |
| l lim
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| y -
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| t Q .
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| d CALCULATIONS FOR LIMITORQUE OPERATOR BOLTING 1
| |
| -O patel engineers j huntsville, clabomo B t.
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| F
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| ,e v, 8 M ficle Z't" Lim ToneuE OPEM[Anarrst S.Arg. SoLT. s. .!ui) iuu.._EtJ.o L,' .
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| Patel Engineers Huntsville, plohame .
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| page mo. .a3 ._
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| 4
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| OPERATOR IC* 1948 - l b. !
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| DETERMINATION OF WORST CASE OPERATOR ADAPTER PLATE AND EVALUATION OF ADAPTER PLATE BOLTING O
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| 1 potel engineers huntsville, clabamo B3&
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| O The ANSYS analysis which follows presents the determination of the worst case adapter plate used in the hybrid valve model for the static analysis.
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| Both Bettis and Limitorque operator plate models were subjected to the 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.
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| The Bettis plate showed highest stress level of 6727 psi, while the Limitorque showed highest stress of 2873. 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.
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| seniENI AL 2
| |
| .29t000E+00 4
| |
| ER- =
| |
| li .
| |
| ALI*a = .650000E-05 730000E-03 3, DENS e g
| |
| NUEY a .300000
| |
| , NATERIAL 3 ,
| |
| 4 i
| |
| * EA = .203000E*00 .
| |
| ALPA = 650000E-05 =
| |
| DENS a 730000E-0 3 hURY = .300000 +
| |
| e -o s4*. y' ,
| |
| } seATERIAL 4
| |
| +
| |
| 9 (p
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| =LPs =
| |
| . .29 000E*00 650000E-05 6 DENS = 0.
| |
| NUXY = .300000 i 8AIENIAL 5
| |
| . ts = .299000E*00 ALPX = .650000E-05 DtNS = .013000E-03 +
| |
| NUNY = .300000
| |
| ***** COUPLED UtG. OF Fit. OEFlestil0se5 ICAND pg *****
| |
| %ET D.O.F. feUNH(N COUPLED N00E5 ,
| |
| $ 8 Ul d I 552 2 U2 2 # Sl3
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| {
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| 3 UI 2 ? 556 i 4 UE 2 4 585 5 UT 2 S 516 j 6 497 2 6 SIF F ul 2 i %IN
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| * 39 un 2 576 396 ,
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| et uv 2 576 396 41 es? 2 576 3v6 41 COUPLE 0 bEis AUClaL $1opAbt stoutptMENTS t0e H THAUU6H E CAND DATA $9ePut cps 39.799 d Coset s 30844060 mise 0RT= 40898000 TOTAL = 08144068 minuts, AVAILabLf= 09147778 4
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| 9ete illLL= INIENNAL PRtb$Up[ LQAU 9 . -
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| TALHE WAkIAesLE LOLUMNS hAnt LOAD SitP RLY . . . . .... -I RDIS 2-3 itpPtRAtukt NEY . . . .... O RTEm> e-6 humesEW OF IftRATION$. . . . . I NITTEN T-4 5tht55 PRINTOUT FNt00ENCy . . 2 $sPRINI 80-12 ilME At Efeu OF LOAD STEP. . . 9. Yleet 13-24 litN pkte CF POST LLEM. O*fa l IFE0 49-51 (CadO mg litet 8 kl 0 0F Post N00AL 0*I A I IF ho $2-Se (Cnep pl '
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| *S 119 % 28%.00 46 lia 5 205.00 4F let -5 205.00 es $22 5 285.09 49 153 S 285.00 Se 554 S 295.00 St ISS % 285.00 SJ 156 S 2s5.00 S3 157 % 285.00 S4 15e 5 285.00 55 159 5 285.00 56 Ive 5 205.00 SF 198 '5 285.00 Sb 192 S 285.00 59 193 '5 285.00 60 194 5 285.00 68 195 % 205.00 1 62 196 5 285.00 , ,
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| 63 227 1 285.00 ,
| |
| 64 230 1 295.00 i I
| |
| 6% 231 205.00 66 234 1 245.00 4 .
| |
| 67 23S I -65.009 >!
| |
| 68 236 1 -65.000 .
| |
| 6W 237 8 -65.000 '
| |
| 70 238 I -65.000 FI 239 8 -45.000
| |
| . 72 240 1 -45.000 F3 241 1 -65.049 t' 74 242 1 -65.000 .
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| O 75 243 1 -65.000 6
| |
| 4 36 Ti 244 245 1
| |
| 1
| |
| -65.000
| |
| -65.000 78 246 I -65.000 ;
| |
| 79 247 1 -65.000 80 24s I ~45.000 bl 249 I -45.000 82 250 1 -65.099 83 255 1 -65.000
| |
| * 84 252 1 -65.000 .
| |
| PS 253 1 -45.000 86 254 I -45.000 DF 255 I -65.000 to 256 8 -65.000 l 69 2S7 1 -65.000 90 258 1 -65.099 L h
| |
| es* *
| |
| * LO AD SIPeM AHf - 4* pl5PLACEMtNis a F0kCE5 99 PWL SStMt s *** i OCT AL STORAtif Wt0Uluf MENf 5 P.09 L THNOU6M P C AWla RJAI A lhPSIT (Pa eg.gh%
| |
| LONLa 0014JI67 a.5mopyn 00000000 TOTAL = 0014JI67 MLMouy AvalLAeL(= 00407F74 .
| |
| MANIMUM silFFhts5 a .26* 8 8t M e l4 AT tLthENI Je2 hlNIMUM %1lfFNt55 e 69 7d 8 80t
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| * 0 7 AI (LtMENT 309 g - '-Ne .-eo- --eg=,
| |
| | |
| I OLI AL SigNabt ht uulkt Mt NI% ' 04 IllMihI 9 0N4UL AllDN LPs tie.srj tunts telejles namoNye 04udee00 IntALs 4444386F utwop, AvalLAntes esteFF7h
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| *** tLtMthf %Ilf fmtss FuhmuL ATIon Timis
| |
| ' ITPE NUnhtM STit TOTAL LP Avt CP 1 226 4% 20%.les .wes 2 m we 4.5Je 567 3 de 63 m.4wl 370 4 ft 4 .gae .tig 5 26 63 14.435 402 6
| |
| * 63 8.16d .27b e * * .2WJ .072 9 26 4 1 084 072 '
| |
| le le 4 4e# .448 11 # I4 . ele .See 12 4 24 .084 .elt il%E AT Ebb 0F ELEMENT Siste hE55 FORMULail0N LP e 774.5$2 MAAIMU4 In-CORE wavt FRONI ALLOWLO FDR RLGUE5ftp MLMONY tille 269 i
| |
| OCIAL STORA6E kt0UlpthEN15 tor Wave FRONT MATRia 50Lullog CPe 433.157 8
| |
| CORLs 00143167 nCh0RY 90064470 TOTAL = 002272ST MEMONv AvalLAMLEm 00507770 i e I
| |
| sMalMuH th-CONE WAVE FRONT GEGUAll0N55 USE0s 229
| |
| *** MATRIE 50Luil0N TimEh .
| |
| RE AD IN ELEMENT SilFFNE55Lb CP= 6.720 NODAL C00NO. THANSFORMAfton cpm .090
| |
| ()MAld!N INI ANGOL AMil Ai!04 CP= 451 392 o
| |
| Os Ilkt AT EhD OF MAINIR TRI?h&dLARITATION CP e 43J.194 ilnE AT STadi OF WACK sod %)lTUTIoh CP= 433.250 *TLP" 1 ITERailbMe I t
| |
| DCTAL STORAbE RLuul>EMENig 904 SACK SUM 5Tlluftph CP= 436.656 CONEm 00143167 MLmuMYe 8000F027 TOTAL = 00lS221e MLMORy AvallahLEe 80107770
| |
| *** ELEm. STRESS C ALC. flats .
| |
| TYPL NUMBER SilF TOTAL LP Av[ CP 1 246 45 te.tes .048 2 e w* 8.32J .l65 J to 63 8 300 .the
| |
| * 14 4 .23* .Stw
| |
| % 26 63 1.506 .458 6 4 43 .tif .444 9 * * .00* .t2l w 26 4 .466 .022 10 le 4 .368 .017 11 4 le .0lt 009 It i 21 .018 . ell ese hoOAL FowCL CALC. I B ML %
| |
| ITFL NUMutM Sil$ IOTAL LD AVE CP 4 426 4% 4.64# .42l 2 a we 0.00# 0.000 b
| |
| 9 -
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| - (~A L m)
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| J to h3 468- .019 4 It 4 .314 .009
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| % d6 hh eude .020 h
| |
| * 63 .Onw .020 8 4 4 .0JS .010 9 26 4 .24d 009 le le 4 .09d .009 Il 2 le .See .003
| |
| , it i 21 .00J .003 d'
| |
| ee. STEP l ITLR I CumPLETE. T IME s 0. rDI5* I MitMPs O Ciru. filR.= 1 Cpm ogw.452 OLIAL STORAbt kEQUIREMENTS !OR $iRL$$ ANU F0 HCL CALLULATinNS COHta 00143244 ufMORY* 0000f020 TOTAL = 0035226S MLMON, AVAILAHLEe 00307770 M3AIMUN CLhiWAL MEMORY USED a 0144060 M1XIMUM AUEILIAnf MEMORY USLDs 0064070 MINIMUM TOTAL MLMORY USED = 02272SF MaulMUM AUAILIAkf AvalLAULt = 0101170 496947 woROS wel1 TEN 04 eLOCNS I ANO 2
| |
| ., 223080 WO405 wRIffEN ON DLOCN 3 .
| |
| ! 8 lue4 ACTIVE DEbnEES 0* FRELOON 119.5 R.M.S. WAVEFRONT .
| |
| MATRlx $0Lui!ON i!ME ESTIMmIElCDC6600I m. 2be.74 SEC0h0s. ,
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| j (4 c', Posi DATA welliEN ON FILL TAFEl2
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| * O RtDUCLO DISPLACLMENi$ wRlitLN 04 FILL TAPE 13 RLSTARI DATA WRITTEN ON FsLE TAPE 3 t
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| IRI ANsutARIrE0 a4Inlx WRITTEN 04 FILt r APl i t NE W IliLEm 1040pE 135000 IM.LU.
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| $1HESS PletNfoui F4touENCY . . t N"0 INT IO*l2 fl4E AT END OF LOAu STEP. . . 8. ilmE 13-24
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| ; ITER F910 OF POST ELEN. Data 1 IP ED 49-58 (CaNO MI t IILR FREO OF POST houAL 0*la i IF hD S2-54 (Cado Ma IItM F9EO OF POSI ALACT. phia 1 IP MD $5-57 (Cagu as i
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| ***** LOAD STER' OPTIONS ICARus L Amis MS ****.
| |
| VALUE WAkIAbLE LOLUae8si maeol LuaD STEP RET . . . . . ... -2 EUli 2-3 TLMPLMAiuML EtV . . ..... 8 ATEMP 4-6 hundER OF ITENATIbes5. . ... I haffER f-v SihE55 PHifeIOUT FRE0u(NCY .. 2 NPNthi 30-82 ilmt, AT Esau 0F LOAD STEP. .. 9. TIME 13-24 liEM FREO 0F POST ELEn. Data l ID ED 44-SI ICARD MD IIER Fkte OF POSI NODAL Dala l It hD S2-54 ICAND Mt litM Fkt C Of POST REACT. UntA I li kD SS-57 ICauD al ,
| |
| Ol5PL. PulhTOUT fe4LOUENCY .. 2 NDPRNi 70-12 ICAwo MS
| |
| , COONDINATE ACCELERATIONS 346.40 8. e.
| |
| 1 e
| |
| *** LOAufse6 CMa W S ***
| |
| e
| |
| ***** SPECIFIED PosCES ICAuD 08 *****
| |
| i $ s0.
| |
| e N00E DIRECTIuh WALuE I
| |
| P 1 330 Ma 0.
| |
| 2 tot Ms 8.
| |
| i i OCI AL 510RabE REcutREMENTS F0el esEW LOAD Ose OLO SilFF. Mavels CP= F24.bv0 j COMEu 101434d1 MEMONY= 0000F028 TOTAL = 00152142 ut M0fe w AvalLAlsLEe 80807770 e
| |
| i t set' At SIANI 0F WACE SudSIlluTION CP= F24.600 steps 3 litantION= 1 5
| |
| *** STEP 3 ITER I CoaPLETE. Ilset a 8. wD85 2 mILnP= 0 CePe. life.= 3 NLW TliLE8 Y UlkECil0M ACCEL
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| ese## LOAD STEP Oe'TI0ses ICARUS L Aeso MI **ese VALUE waplasLE COLUMN $
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| esAME d
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| LOAO STEP KET ........ -2 mul$ 2-3 ,
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| itMPENAIUht REY . . . .... O KTEMP 4-6 NUMdER OF ITENATIDses. . . . . I NITitR F-9 SIRt$$ PNihiOUT FRt00t#8LY . . 2 NPRINT 10-12
| |
| , f lME A T E hu 0F LOAD STEP. . . 9. TIME 13-24 i life SktQ OF POsi LLEM. DalA I IFED 49-53 (CARD M3 litR Fkte OF POST se00AL DABA 3 IF eep S2-$4 (CARD MI .
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| 4 IttR F Rtc OF POST EE ACT. pala 1 IF R0 SS-Si (CAND MI UtbPL. PRlhiOUT FRICOUEasCT . . 2 esDPesci 10-12 GCARO hl C00HUINATL ACCELERATIONS 0. 3e6.40 n. .
| |
| ese LOAulNG CHAhDES ***
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| 4 OCTAL STORAbE RE00lREesENTS FOR NEW LOA 0 Ops OLD STIFF. MAtoIR cpm 826.413 - . . = = . . .
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| APP.ENDIX
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| . D .
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| MODAL ANALYSIS 4
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| potel engineers huntsville, alob. omo .
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