ML20065Q196
| ML20065Q196 | |
| Person / Time | |
|---|---|
| Site: | Zimmer |
| Issue date: | 08/30/1982 |
| From: | Mcdonald C MCDONALD ENGINEERING ANALYSIS CO., INC. |
| To: | |
| Shared Package | |
| ML20065Q180 | List: |
| References | |
| ME-884, NUDOCS 8210260493 | |
| Download: ML20065Q196 (91) | |
Text
- _ _ _ .
l ME-884 REVISED 3/12/82 REVISED 8/30/82 5
SEISMIC - STRESS ANALYSIS OF HORIZONTAL PUMPS SIZE & TYPE: 8 X 10 X 14 CAP CUSTOMER: CINCINNATI GAS & ELECTRIC COMPANY PLANT: FIM H ZIMMER NUCLEAR POWER STATION -
CUSTOMER P. O. NO.: 2212 IS!!!SEEi$i!!"E S.O. NO.: 14210325/8
""^""""8 MANUFACTURED BY BINGHAM-WILLAMETTE CO.
PORTLAND, OREGON Analysis By O MCDONALD ENGINEERING ANALYSIS COMPANY, INC.
!!A 28M o!!$8Sie NE PDR
CERTIFICATION STATEMENT These Bingham-Willamette 8 x 10 x 14 CAP 1-stage RX Building Closed Cooling Water pumps have been analyzed in accordance with Sargent & Lundy Specification No. H-2185 including Supplement No. 3; the ASME B&PV Code, 1971 Edition through Summer 1973 Addendum,Section III, Class 3; and good practice in design analysis. AISC Code, 7th Edition is used for bolting.
The pump is adequate provided that the pump hold down bolts, upper tail bracket bolts, and frame to cover bolts are replaced by bolts of A-325 material, or equivalent and thc lower tail bracket bolts are replaced by 1/2" diameter bolts of A-325 material.
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(, / lc'(lJ7abc C. K. Mcdonald, Ph.D., P. E.
Alabama Registration No. 9586 August 21, 1981 Revised 5/1/82 - Revised nozzle loads, re-ran seismic analysis.
Revised 8/30/82 - Revised per S & L comments.
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TABLE OF CONTENTS O)
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- 1. INTRODUCTION 1
- 2.
SUMMARY
OF RESULTS 3 l 3. FREQUENCY ANALYSIS 4 3.1 Dynamic Model 4 3.2 Computer Analysis 7 3.3 Frequency Output 7
- 4. LOADING CRITERIA 15 4.1 Dynamic Loading 15 4.2 Nozzle Loads 15 4.3 Internal Pressure Loading 15 4.4 Shaft Torsional Loading 15 4.5 Other Pump Normal Loads 15 O/~'
4.6 Casting Factor 15
- 5. STRUCTURAL INTEGRITY ANALYSIS 17 5.1 Motor Bold Down Bolts 17 5.2 Pump Hold Down Bolts 20 5.3 Anchor Bolt Loads 20 5.4 Shaft Stress 21 5.5 Stresses in Support Frame 22 5.6 Thrurt Bearing Retainer Bolts 22 5.7 Tail Bracket Bolt Stress 23 j 5.8 Stuffing Box Cover Analysis 24 a
5.9 Nozzle Analysis 24 5.10 Suction and Discharge Flanges 26 O Continued.....
TABLE OF CONTENTS (Cont.)
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5.11 Bearing Housing to Stuffing Box Bolt Analysis 27 5.12 Pump Pedestal Stress 27 5.13 Pump Pedestal Weld Stress 28 5.14 Pump Foot Stress 28 5.15 Motor Support Stress 29
- 6. FUNCTIONAL CAPABILITY ANALYSIS 30 6.1 Flexible Coupling Analysis 30 6.2 Impeller Key Analysis 31 6.3 Impeller Clearance 31 6.4 chaft Mechanical Seal 32 6.5 Bearing Loads 33
( 7. MOTOR SEISMIC LOADS 35 G
Appendix A - Computer Output for Forces and Displacements Appendix B - Nomenclature and Formulas Appendix C - Frequencies and Mode Shapes Appendix D - New Departure Bearing Allowable Loads Appendix E - Accelerations Appendix F - Member Properties Appendix C - Masses Appendix H - Nozzle Loads Appendix I - Response Spectra Curves x_/ Appendix J - Flange Analysis
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- 1. INTRODUCTION h
- 1
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This report covers the seismic, stress, and deflection analysis of Bingham-Willamette 8 x 10 x 14 CAP l-stage RX Building Closed Cooling Water pumps. The analysis is directed toward proving both the structural integrity and functional capability of the pumps.
A dynamic model is developed and a computer frequency analysis is made to obtain the frequencies of the assembly, as required by the spec.
The pump assembly has frequencies below 67 Hertz, thus a dynamic analysis is made.
The nozzle loads are also imposed on the computer model of the assembly and the resulting loads and deflections are calculated. The total stresses /
loads are calculated and then compared to the allowables given in the i specification, or ASME Code. The deflections are compared to operating clearances or other limiting criteria.
The nozzles are analyzed for the maximum nozzle loads. The equivalent pressure caused by the nozzle bending moments are calculated in accordance with the ASME Code and imposed on the flanges.
This pump casing is of complex geometry and has been well verified for normal. operation by service experience and hydrostatic tests. The seismic and nozzle loads impose negligible stress in the casing except at nozzle penetrations and the Stuffing Box flange, which have been analyzed.
Only the worst case component is analyzed in detail in this report.
The worst case is selected by either enveloping the loads for all components l
and applying these loads to the component selected or doing a case by case .
study of the stresses in each component. In either caso, only the worst case (3
' calculations are included in the report.
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- 2.
SUMMARY
OF RESULTS A summary of the actual stresses, loads, and deflections is given herein.
The actual Emergency values are compared to the Normal allowables.
Components Actual Allowable Motor Hold Down Bolt Stress, PSI - Tensile 4,708 12,221
- Shear 9,487 10,000 Pump Hold Down Bolt Stress, PSI - Tensile 20,607 40,000
- Shear 22,742 33,000 Anchor Bolt Loads, Lbs. - Tensile 8,854 By Others
- Shear Y 15,205 By Others Shear Z 884 By Others Shaft Stress, PSI 10,484 17,500 Support Frame Stress, PSI 18,206 24,000 Thrust Bearing Retainer Bolt Stress, PSI 1,271 20,000 yh Upper Tail Bracket Bolt Stress, PSI - Tensile 18,911 38,985 V - Shear 6,884 15,000 Lower Tail Bracket Bolt Stress, PSI - Tensile 37,505 40,000
- Shear 2,694 15,000 Stuffing Box Cover Flange Stress, PSI 18,'144 21,000 Bolt Stress, PSI 17,214 25,000 Maximum Nozzle Stress, PSI - Suction 15,562 21,000
- Discharge 8,755 21,000 Discharge Flange Stress, PSI 14,347 21,000 Suction Flange Stress, PSI 16,172 21,000 Frame / Cover Bolt Stress PSI o 18,127 40,000 Pump Pedestal Stress, PSI 12,936 24,000 Pump Pedestal Weld Stress, PSI 19,733 21,000 Pump Foot Stress, PSI 11,933 21,000 Motor Support Stress, PSI 8,935 24,000 Continued......
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- 2.
SUMMARY
OF RESULTS (cont.)
Components Actual Allowable Flexible Coupling Misalignment, Radians .019 .025 Impeller Key Stress, PSI 2,531 9,000 Impeller Clearance, Inches .007 .009 Esaring Loads, Lbs. - Thrust 2,559 57,500
- Radial 1,941 28,480 Motor Accelerations, G's - X 1.80 -
-Y .84 -
-Z .86 -
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- 3. FREQUENCY ANALYSIS A dynamic model is prepared and a computer frequency analysis is made to determine the assembly frequencies as required by the specification.
A detailed discussion of the dynamic model and computer analysis is given below.
3.1 Dynamic Model The dynamic model which was developed for the frequency analysis is shown in Figure 2, page 5. The joint numbers (enclosed in circles) and member numbers are included to facilitate the computer input. Several assumptions were made in developing the model. These assumptions were made such that the model would be more flexible than the actual assembly.
t/)' s Thus, the frequencies predicted by the model will be lower than the actual
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frequencies. Some of these assumptions are:
- 1. The bedplate is assumed to be supported only at the. foundation bolts. This is true for upward forces but for douward forces the bedplate channel flanges are continuously supported.
- 2. The effects of grouting have been completely neglected. The neglect
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of this grouting reduces the calculated frequencies and increases the calculated stresses, thus it can be seen from the response spectra curve that this approach is conservative.
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shaf t is assumed to be pinned at the radial pump bearing (joint 22) and at V both motor bearings (joints 35 and 46).
Masses are lumped at joints i ' accordance with good practice in seismic analysis.
Most of the mass of the pump is lumped at joints 13 and 19. Joint 13 is the intarsection point of the centerlines of the nozzles.
The pump and motor bearings are modeled by equivalent hollow beam sections.
Members 33 thru 36, 43 thru 54, 65, and 66 represent the motor support and casings.'
Members 24 thru 27, 29, and 30 represent the pump pedestal.
The calculation of the member properties is given in detail in App. F. Members 15 thru 21, 37, 39, 40, and 42 represent the cross members under'the hedplate which are welded integrally to the bedplate.
The relationship between the STRUDL local and global coordinate systems is shown below: -
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3.2 Computer Analysis 0
U The cor:puter analysis for the frequencies is performed by use of the computer code ICES-STRUDL operating on an IBM 370/1'58 computer. This code was developed at the Massachusetts Institute of Technology, Civil Engineering Department. Users manuals may be obtained from M.I.T. ' The code has been well verified for frequency calculations.
' Tkeseverihicationchecktsare)
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contained in a set of course notes for a class in Dynamit. Seir>nic. Analysis
- which 5as taught at-the University of Alabama in Birmingham.' [These verifi-cation checks may be inspected at the offices of Mcdonald Engineering Analysis. Company.
The detailed input data sh'eets are given on pages 9 through 14 and are believed (o be self explanatory. The motor and pump shaft vary in cross section an'd'are input accordingly. -
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'The analysis'is made for the three orthogonal' directions simultaneously.
Thus,thamodel~isassigned:ISdegreesoffreedom[(threepermass).
3.3 Frequency Output The computer output for the frequencies is given in Appendix C. The lowest modes and their directions are:
Direction '
Lowest Mode Y ,
24.5 Hertz X ,
30.5 Hertz Z 40.7 Hertz Note that the X mode is close to the operating speed of the pump. However, as notjed previously, the neglect of grouting and assuming support only at the anchor bolts causes the calculated frequencies to be low.
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',' The X mode is a combined bending of the pump pedestals and flexing of the pump baseplate. Grouting will have no effect upon the bending of the pedestals but it will have a significant effect upon the flexing of the baseplate because the cross channels are integrally welded _
to the baseplate and then grouted, thus forming a very rigid base The same applies to the lowest Z mode.
The lowest Y mode will be significantly affected by the grouting because it is timost totally due to the flexing of the base plate.
- The coupling used on this pump assembly is a Double Flex type that is designed to prevent transfer of moments, other than torque, between pump and motor. Thus, the end releases on me.abers 58 and 59 -
(coupling) are included to correctly model the coupling.
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15-3 4. LOADING CRITERIA 4.1 Dynamic Loading The dynamic loadings applied are those given in the specification and are shown on page 14. - The lateral dynamic loadings are applied in both lateral directions. The two lateral cases are then combined by the SRSS method, with the vertical seismic. Normal Operating plus Max. Nozzle loads are added directly to the
- dynamic loads. See Loadings 1, 2, and 5 on page 14 for detailed input.
4.2 Nozzle Loads The nozzle loads are given in App < ndix H. See page 16 for detailed g computer input. 4.3 Internal Pressure Loading The internal pressure lesign conditions are 150 psig at 150 F. 4.4 Shaft Torsional Loading The motor horsepower is 100 at 1775 R.P.M. Thus, the torque is: T = 63000(100) = 3,550 in-lbs. 1775 4.5 Other Pump Normal Loads The pump is subjected to a 600 lb. axial and a 300 lb. radial load on the impeller during Normal Operation. This load is included in Load Case 4, page 16. The deadweight loads are given in Loading 3, page 16. () 4.6 Casting Factor
> A casting factor of .8 is used for pressure components.
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- 5. STRUCTURAL INTEGRlTY ANALYSIS b
O The detailed stress analysis of the pump, supports, and motor hold down bolts is contained in this section. One loading condition is considered. The Normal Operating plus Maximum Nozzle plus SSE loads (Emergency Case) is limiting since it is held to the Normal Allowables. Thus, it is the only case given. A computer analysis of the pump is contained in Appendix A. Some of the pertinent stresses are obtained directly from the computer output. Not al? of the important stresses could be conveniently obtained from the computer analysis. 'Ibus, some of the stresses are hand calculated. 5.1 Motor Hold Down Bolts ' i % A sketch of the motor is shown below: ((O/ Y . 1 - Operating Torque
, >- _I -
ex 10" l
- [l i II Y l, 8"- ,m 8" l c c - ,
,6.12" _ .,6.'12"_l rg- q 5/8" bolts G
The stress due to operating torque is: r s S = 3550 = 491 psi 2(16)(.226) The total stresses are obtained from the forces given by the computer output and the operating torque. The maximum loads on the bolts are listed below, see Appendix A, members 43 through 46. Tensile, Lbs. Shear, Lbs. Y Z Loading 1 651 1,415 541 Loading 2 347 42 125 Loading 5 502 1.005 632 SRSS 892 1,736 841 Loading 4 61 34 369 Totals 953 1,770 1,210 i The tensile stress due to the above loads is: 81 = P, = 953 = 4,217 psi (For 5/8" bolts, Ab = 0.226) A .226 S = 4217 + 491 = 4,708 psi total The shearing stress is: V = R = 17702 + 12102 ' = 9,487 psi A .226 The allowable stresses for A-307 bolts are 10,000 psi shear and 12,821 psi tensile per the 7th Ed. AISC Code, including the effects of shear upon the tensile allowable. NOTE: Ft = 28,000 - 1.69487 ) = 12,821 psi tensile allowable O
B . 18" _ 16" l
- 2 - 7/8n dia. bolts See view below l
.l
!00 o V
\ g Pedes.tal-I i j /8" 5 bol*
/
I i fl i il Tail Bracket / ~_5.25" lF 1/2" bolts See Sect. 5.7, pg. 23 l77/8" bolts'
#10 Taper Pin g' y
n 4.75",t l
-,- 5b -
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l 5.2 Pump Hold Down Bolts A sketch of the pump hold down bolts is given on page 19 . The loads in the upper end of the pedestal are the bolt loads and are obtained from Appendix A for members 24 and 25. The maximum tensile loads are in member 24.
~
Axial, Ibs. Bending, in-lbs. Shear, lbs. Y Z Loading 1 84 2,074 764 570
, Loading 2 104 2,338 842 725 Loading 5 736 15,183 298 501 SRSS 748 15,501 1,175 1,050 Loading 4 6,936 24,859 7,169 1,603 Totals , 7,684 40,360 8,344 2,653 The tensile stress is:
, ~ . d-/ S = P + M + T 2Ab 4.75Ab 2(18 + 16)Ab
= 7684. + 40360 + 3550 = 20,607 Psi 2(.6013) 4.75(.6013) 2(34)(.6013)
The shear stress is: V = R = 83442 + 26532 ~ = 22,742 psi ATP .385 The allowable stress for A-325 bolts is 40,000 psi for tensile. The allowable stress for the cold drawn steel dowel pins is .33(100,000) - 33,000 psi. 5.3 Anchor Bolt Loads The loads in the anchor bolts are given by members 2, 22, 23, 28, 38, and 41 in Appendix A. p. V
l l Tensile, lbs. Shear, lbs. Y . Z Member 38 Member 23 Loading 1, Seismic X 671 1,449 37-Loading 2, Seismic Y 971 1,529 44 Loading 5, Seismic Z 570 1,692 346
. SRSS 1,311 2,702 351 Loading 4, Nozzle + Impeller _
7,543 12,503 533 Totals 8,854 15,205 884 These bolts are furnished by others and must be able to withstand the above . loads.
- 5.4 Shaft Stress ,
I The maximum shaft stress occurs in member 55. The loads from App. A are: Axial Bending Y Z
. Loading 1 68 889 58 Loading 2 80 1,154 65 Loading 5 5'1 150 2,249 SRSS 117 1,464 2251 l Loading 3 0 0 751 Loading 4 600 3,468 0 Totals 717 4,932 3,002 The tensile stress is:
St=P + M = 717 + [4932 2 + 3n022'
- 8,924 psi A Z 2.76 .647 The shear stress is:
O V =
]}-
J
= Tr Ix
=
3550(.9375) 1.21
= 2,751 psi The combined stress per the maximum shearing stress theory is:
t - --
-e- -+-,--w <----vr--w--v -----w -----*-----rrm-w-----------+---+-v--------*---ww m-- - - + -<ee---te-wr,e---. we
r S = d(2(2751))2 + (8924)2 ' = '10,484 Psi h(m_/ The allowable stress for the A-276-410 shaft is 17,500 psi. , 5.5 Stresses in Support Frame The maximum stresses occur in member 11, see App. A for loads. Axial, lbs. Bending, in-lbs. Y Z Loading 1 437 136 8,139 Loading 2 495 130 7,906 Loading 5 963 127 _11,804 SRSS 1,168 227 24,580 Loading 3 229 76 5,441 Loading 4 5,116 344 _ 68,581 c ,. Totals 6,513 647 98,602 O
\~# The stress is: (note on page F-2 that the effects of 12t of the bedplate have been included in S$ calculation)
S = P_ + h + h A Zy Zz
. 6513 + 647 + 98602 =
18,206 psi 3.42 1.23 6.25 the allowable for A-36 steel is 24,000 psi. 5.6 Thrust Bearing Retainer Bolts The thrust load imposed by the shaft and impeller is resisted by 4 - _ diameter bolts. The axial load given in Section 5.4 imposes thrust in these, bolts. l The stress is: S =
]>
= 717 - 1271 psi tensile A 4(.141)
O The allowable stress is 20,000 psi for the A-307 bolts, per the AISC Code, 7th Ed.
5.7 Tail Bracket Bolt Stress
-fh O The loads in the tail bracket are given by member 29, Appendix A.
Axial, lbs. Shear, lbs. Bending, in-lbs. Y Z Y Z
. Loading 1 ,
130 76 284 .4,199 1,132 Loading 2 80 53 339 5,013 787 Loading 5 831 541 49 726 8,009 SRSS 845 549 445 6,579 8,127 Loading 4 4,957 1,062 921 13,637 15,725 Totals 5,802 1,611 1,366 20,216 23,852 (a) Upper Bolt Stress (One 5/8" bolt, see page 19) The ; ensile stresc is: (For 5/8" bolts, Ab = .3068) S = P_
= 5802 = 18,911 psi The shear s ress i :
V = R = 16112 + 13662 = 6,884 psi A .3068 The allowables for A-325 bolts are 15,000 psi shear. and 38,985 psi tensile. . (b) Lower Bolts (4 - 1/2" bolts, see page 19) f S = P + My + Mz 4Ab 2(5.25)Ab 2(3)Ab
=
5802 + 20216 + 23852
- 37,505 Psi tensile 4(.190 _2 (5. 25) (.196') 2(3)(.196 )
V = R = 16112 + 13662 = 2,694 Psi shear A 4(.196) The allowable stresses for A-325 bolts are 40,000 psi tensile and 15','000 psi-shear per the AISC Code. O O
-24 .
5.8 Stuffing Box Cover Analysis O The loads on the stuffing box cover are given by member 31 at joint 13, Appendix A. Axial Bending
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Y Z Loading 1 509 4,658 3,409 Loading 2 598 5,818 3,775 Loading 5 157 802 23,010 SRSS 801 7,496 23,565 Loading 3 130 177 6,147 Loading 4
- 462 16,344 82,999 Totals 1,393 24,017 112,711 The resultant moment is:
M = 240172 + 1127112 - 115,241 in-lbs.
.. The flange analysis, including the effects of external loads per the fm ASME Code Paragraph ND-3647.1 is included in Appendix J.
5.9 Nozzle Analysis
- 1. Discharge Nozzles The discharge nozzle-casing intersection is closely approximated as a tee.
The methods of ASME Code ND-3652 are used to perform the analysis. The tee is contoured similar to a welding tee but it is not exactly the same as a welding tee. Thus, to be conservative, the stress intensification factor used for this analysis will be the average between the factor for a welding tee and the factor O
-25 * -
for a fabricated tee. The nomenclature is that of the ASME Code. (y For a welding tee: h = 4.4(.58) = .284 i = .9 - 2.08 9.0 (.284)Z/3 For a fabricated tee: . h = .58 = .064 i =
.9 = 5.62 9.0 (.064)2/3 Average Stress Intensification Factor: , ,
iavg = 2.08 + 5.62 = 3.85 2 Z = 3.1416(4.0)2(.58) = 29.15 in.3 The total bending moment resolved at the nozzle / casing junction is: Mxt = Mx + 22.125Fz = 1300 (12) + 22.125(1050) = 38,8311n-lb s. Myt
- My =
3000 (12) = 36,000 in-lbs. Mzt " Mz + 22.125Fx = 2000 (12) + 22.125(1825 ) - 64,378 in-lbs. MR " Mxt +M yt +M zt = 388312 + 360002 + 643782 = 83,3S7 in-lbs. Equation (8) of ND-3652.1 gives: 125(9.25) + .75(3.85)(83357 -1 = 8,755 psi < 1.5(.8)(17500) = 21,000 psi 4(.58) 29.15 SA-216 WCB
- 2. Suction Nozzle The suction nozzle is treated as a nozzle in a flat plate, Cases 10 and 20 of Roark's Formulas for Stress and Strain, Fourth Edition. The parameters are:
ro = 6" = b a = 9" t = .75" The stress coefficients are obtained from pages 241 and 242 of Roark. They are: Sg =
.60 Sp - .22 The loads are:
Mxt = Mx = 4612'(12) = 55,344 in-lbs. Myt " My + 6Fz = 8219 (12) + 6(1459) = 107,382 in-lbs. Mzt " Mz + 6Fy = 2486(12) + 6(1915) = 41,322 in-lbs.
MR
= 1073822 + 41322 2 ' = 115,058 in-lbs. Resultant Bending 0'V R - =N19152 + 1459 2 ' = 2,407 lbs. Resultant Shear F = 4,868 lbs. Axial Force The stresses are:
Si = SM M + 8F =
. 60(115,058J + .22(4868) = 15,540 psi g t 9(.75)2 (. 75) 2 Bending V =
Mx "
+ R = 55344 + 2407 2 6.283(6)(.75) 2(3.14) rot 6.283rot 2(3.142) (6) Z(. 75)
= 411 psi shear The combined stress per the maximum shearing stress theory is:
28 S = h(2V) 2 + 37
=N(2(411'))2 + (15540)2 ' = 15,562 psi The allowable stress for SA-216 WCB is 1.5(.8)(17500) = 21,000 psi including the casting factor.
bV 5.10 Suction and Discharge Flanges These flanges are analyzed per ND-3647.1. (a) Discharge Flange This flange is an 8" 300 psig ANSI. The external loads are: P = 2,250 lbs. M = 12 13002 + 20002'= 28,624 in-lbs. The analysis is given on page J-2 and the flange is adequate. (b) Suction Flange This flange is a 10" 300 psig ANSI. The external loads are: P = 4,868 lbs. M = 12 82192 + 24862' = 103,041 in-lbs. O The analysis is shown on page J-3 and the flange is adequate.
5.11 Bearing Housing to Stuffing Box Bolt Analysis B The housing is fastened to the stuffing box cover by 6 - 3/4" diameter bolts on a 9.875" belt circle. The forces and moments acting on the bolts are essentially the same as those given in Section 5.8. Thus, the tensile
~
stresses in the bolts are: (For 3/4" bolts Ab = .442) S = P_ + 4M A NCAb
=
13'93' + 4(115241 ). = 18,127 psi 6( .442 ) 6(9.875)( .442-) The allowable stress for A-325 bolts is 40,000 psi per AISC Code, 7th Edition. 5.12 Pump Pedestal Stress The pump pedestal loads are given by members 24 and 25, see App. A. s Axial, Ibs. Shear, lbs. Bending, in-lbs.
'Y Z Y Z Loading 1 111 764 570 11,122 13,623 Loading 2 107 842 726 14,148 1,4,960 Loading 5 '833 298 513 10,003 19,760 SRSS 847 1,175 1,056 20,589 28,282 Loading 3 631 66 218 4,257 2,740 Loading 4 6,936 7,169 2,127 41,481 143,631 Totals 8,414 8,410 3,401 66,327 174,653 The pedestals are shown on page F-3. The stress is:
S = P, + M_y, + h A Zy Zz
= 8414 + 66327 + 174653 = 12,936 psi 9.74 8.49 41 The allowable for A-36 is 24,000 psi.
1 5.13 Pump Pedestal Weld Stress O The pump pedestal shown on page F-3 is welded all around to the baseplate by Is" fillet welds. The properties are given on page F-9. The weld, stress is: V1
= P,_ + h + }fg = 8414 + 66327 + 174653 = 19,659 psi Aw Zy Zz 5.31 5.84 26 V2 =
R_ = Y 41.02 + 34012 = 1,708 psi
- A 5.31 V =fV 1 2+V2 2 = Y196592 + 17082 . 19,733 psi ,
The allowable stress is at least 21,000 psi, 5.14 Pump Foot Stress The pump foot is as: shown below: I l -h 8 I Il l 1 i 0 - l I I _ i i 7 l t_ Vy P N V2 The loads on tae pedestal are obtained from Section 5.2 except deadweight is added to the load P. The properties are given on page F-5, Segment 1 of members 26 and 27. The stress is (P = 7684 (p. 20) + 675 dwt. = 8,359 lbs.). S = h + 4V y + g A Sy Sz
= 2653 + 4(8344 ) + 4(8359 ) = 11,933 psi 12.25 14.2 3.57 The allowable stress for the SA-216 WCB is 1.5(.8)(17500) = 21,000 psi.
l l 5.15 Motor Support Stress C \ The motor supports are represented by members 33 through 36, see Appendix A for loads. Axial, lbs. Bending, in-lbs. Y Z Loading 1 836 4,996 2,054 Loading 2- - 345 1,828 431 Loading 5 660 5,874 1,803 SRSS 1,120 7,925 2,767
; Loading 3 223 2,128 243 Loading 4 125 3,473 1,414 Totals 1,468 13,526 4,424 The stress is:
, S = P + M, A = 2.22 in.2, Z = I 72 in.3
^
S = 1468 + y135262 + 44242 = 8,935 psi 2.22 1.72 The allowable stress for A-36 is 24,000 psi. O
- 6. FUNCTIONAL CAPABILITY ANALYSIS 0
O The detailed functional analysis (deflection, rotaticas, etc.) is contained in this section. The following leading condition is considered: Normal Operating loads + Maximum Nozzle loads + SSE loads (Emergency case). The computer analysis is contained in Appendix A. 6.1 Flexible Coupling Analysis The coupling is adequate for the normal torsional loads. The seismic and nozzle loads do not impose any additional torsion in the shaft. However, the seismic and nozzle loads do cause bending in the pump and motor shaft, which in turn causes coupling misalignment as shown below: . Coupling 7 Motor Shaft N 1h' Max. Pump Shaft ;g The maximum misalignment must not exceed lb degree (.025 radian). This misalign-ment can be obtained from the computer output as the vector sum of joint 33 or 34 (worst case), rotations Y and Z. These rotations are tabulated below, see App. A. (Joint 34) _ Y Z Loading Case 1 .00013 .00044 Loading Case 2 .00016 .00006 Loading Case 5 .00002 .00165 SRSS .00021 .00171 Loading Case 4 .00421 .-01688
;O '
Totals .00442 .01859
Resultant = .019 radian 6.2 Impeller Key Analysis The torque that the shaft key must transmit is practically the same for all loading conditions. This is 3,550 in-lbs. operating torque (p.15 ). The shearing forces on the key are as shown: R E
-l- (
R .50" _ 3" _ m 1.87" _ R = 3550(2) = 3,797 lbs. 1.87 The shearing stress in the key is: ( V = 3797 = 2,531 psi
3(.5)
The yield stress is 30,000 psi for the A-276 Tp 316 material. Thus, the allowable stress is: Fy = .3(30,000) = 9,000 psi 6.3 Impeller Clearance The relative deflection between the impeller and pump casing is found by taking the difference of. the deflections of joints 13 and 21. See Appendix A l for output data. l
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l O
Joint 21 Faulted
) Y Z (O Loading 1 .00037 .00663 Loading 2 .00042 .00846 ,
Loading 5 .00201 .00106 SRSS .00209 .01080 Loading 3 .00186 .00008 Loading 4 .00084 .02105 Totals .00479 .03193 Joint 13 Loading 1 .00026 .00535 Loading 2 .
.00028 .00680 Loading 5 .00195 .00085 SRSS .00199 .00869
(._) Loading 3 .00084 .00008 Loading 4 .00040 .01600 Totals .00323 .02477 Difference (Joint 21 - 13) .00156 .00716 The total vector deflection is: D = g[(.00156)2 + (.00716 )2 =
.007" The available clearance between impeller and casing is .009" (minimum).
Thus, the clearance is not exceeded and the impeller does not make contact _ vith the casing. 6.4 Shaft Mechanical Seals The Jeflection of the shaf t at the mechanical seal is approximately
~
('} one-half that of the impeller, or .004". Experience indicates that the construction of this seal is such that leakage vill not occur due to this small amount of shaft deflecticn.
i 1 l I l 6.5 Bearing Loads l u A sketch of the pump shaft is shown below. l 300 lbs. Radial Impeller + Shaft Thrust Brg. Coupling + Shaft 600 lbs.W,= 65 g lbs* Radial ;; Brg. ;; ; W = 50 lbs. Axial
/77777 177777
-_ 11.56" _l_ 6.19" _l_ 7.63" The accelerations of the impeller (Joint 21) and coupling (Joint 33) are obtained from Appendix E. The loads are assumed worst case for beating loads.
Joint 21 - Impeller (units are in/sec.2, or in/sec 2/386 = g's) Ax = 402 + 472 + 303 = 1177 = 3.05g Ay = 29 + 33 + 491 = 553 = 1.43g Az = 452 + 587 + 76 - 1115 = 2.89g Joint 33 - Coupling Ax = 401 + 472 + 302 = 1175 = 3.04g Ay = 218 + 190 + 2268 = 2676 = 6.93g Ag = 476 + 572 + 92 = 1140 = 2.95g (a) Radial Bearing-Fy = (300 + 65(2.43))(17.75/6.19) + 50(7.93 )(7. 63/6.19) = 1802 lbs. Fz = 65( 2.89)(17.75/6.19) + 50(2.95 ) (7. 63/6.19) = 720 lbs. The resultant load is: 2 2 F = 1,941 lbs.
= k1802 + 720 The allowable load for the ND-3313 or equal hearing is 28,480 lbs. ,
see Appendix D. /s3 NJ
(b) Thrust Bearing Fy = 50(7.93)(13.82/6.19) + (300 + 6' 2.43))(11.56/6.19) - 1,740 lbs. . 1 Fz = 50(2.95)(13.82/6.19) + 65(2.89)(11.56/6.19) = 680 lbs. I F = 1,868 lbs.
=f17402 + 6302 The thrust load is: ,
600 + 65(3.05) + 50(3,04) = 950 lbs. The total load is (see ND Catalog 2C-110): P = 1.37Q868 ) = 2,559 lbs. The allowable load for the ND-45313 or equal bearing is 57,500 lbs.
=
0
.-1 O
- 7. MOTOR SEISMIC LOADS The motor seismic loads are given in Appendix E for Joint 36.
Ax = 5672 + 292 + 3972- = 693 in./sec.2 = 1.80g Ay = d 103 2 + 522'+ 3032 = 324 in./sec.2 = .84g Az = 862 + 3152 + 622 - 332 in./sec.2 =
.868 The motor coupling is a Double Flex and is designed to prevent loads, other than torsion, from being transmitted between the pump and motor, i
O i . i (O l j
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APPENDIX B - NOMENCLATURE AND F0101ULA2 v S = Tensile Stress ; N = Number of bolts ; C= Bolt Circle V = Shearing Stress ;Ab = area of one bolt, in.2 S ,x = The maximum combined stress, combined by the maximum shear stress theory. S = b A bending stress, usually equal to M/Z; M = moment, Z = Section Modulus R = A shearing force Y = The vertical direction X = Lateral Direction in the plane (parallel to shaft) V = T/J, shaft shearing stress where T = torque and J = 2Z = torsional modulus Fy = Allowable shearing stress for bolts: peg Q Fy = 10,000 psi for A-307 bolts per the Code and NF-3281 & Appendix XVII of the ASME Section III Codel Fy = 12,320 psi for A-325 bolts per above reference Fy = 15,000 psi for A-449 bolts por above reference ' Fg = Allowable tensile stress for combined loading per the AISC Code and also per App'endix XVII-2461.3 of the ASME Section III Code. per gg ,% m, Fg = 20,000 psi for A-307 bolts per above reference. F t
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APPENDIX D - NEW DEPARTURE BEARING ALLOWABLE LOADS l - sJ The allowable loads for Delco New Departure bearings subjected to short term seismic plus nozzle imposed loads are established in accordance with the
~
method outlined below. New Departure Catalog 2C-110, pages 58 to 62, gives: 4 Average Life, L = 3800 RR RE / RR =
.866'(4190) = 3628 lbs. ND-313
=
.866(8460) = 7326 lbs. ND-45313 RE
= Allowable Equivalent Radial Load, Lbs.
Since the maximum duration of an earthquake is no more than one minute, it is conservative to set the life, L, to be equal to one hour. Thus, solving for the maximum allowable seismic load: RE
=
RR(3800) = 3628 (7.85) = 28,480 lbs. ND-313 r
. ((,,'
= 57,500 lbs. ND-45313 7326(7.85)
O e
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I O
e APPENDIX E = ACCELERATIONS E~
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gp5 2,9 y i n} S = 'Z. ( ), t11) i ,7 Y Sg.= 2 O Z.V) = Z, M '2 T_.g = 7 (i.85) = 3,70 Z .s = 3 ,7 5 + 2.crif O ,5 f : 10, 3 2 s s,
- Y l i >1e A -A 3 Z(,2 47) = , y14 Y 5 = 2.(, z.3 3)= , gc m_
h= in 9 T-v = Z8 /"4( See p g F~g) g (Y1mb s '2_ll. ( 7_ 5 1 (-W'l i 5/g" i c i9.s" v I I 9 %. ) 9 'ig . 3/s" f LATE'
- t
\
v
- 13. is" s e 6.
y f 16.44 S e6. z q sesy l o L. G. 41" s ea f 4.5" ses z 2.52 5e 6 3
pL z
$EGl 9.74- '"-
(,375) (6 tf I +0 y I 4 13,15) = h- ~ a(c.9i)L375)(c.s7)*= z,3 i#. le: 37s0m59+ rz, t O 2 9l 1n . c.15 2.(.379)(C. 41)(3.M - /, 6 $ " 5: 9.74-
.15 0.ui)(i.c,zf.+ i3.is(.ps.)(/.5B)*
Z C. 575.)(c4M+ T.3= 3 8 7_. 4 5 - s.99iw.
= y. / , i n , 3 = +41 .83 O s e e 7_ ,
(,375)(it. S +LI,5 + IL). W) = '7. 2 9 , b A. = s., Y 1C %5.)(.T75)(5.2.2f. : i z7,5
~f-a = .325 ( lo,l#I)3 4 iz S s= l MS = 2 3,5 Il
_ S, LiI I - z,L.37s)(y s)(L1s] - /. o+ u 3 _- 7.24 i 1 = z C.37s)(%5)34 ,7g(q,5)(j,zf )'# ,o, gg,usjc j.04f l 3 IL O = / 4, 9 id. 6 i4,9 = 4.,3 / in? 3 = 3 46
1 F-5 D Sec, 3 z pr. = L. 5, s)(z. se + 2, Ge + J.3 3) = 4 83 Ig= . 37 5 (.7.]39 + .15 (z,59X3 sc)2 = qg ,ny 4
% -= N S _ = f o. lo I !.
4.06
~2. L 37 5)( z.,58)(l 2d - , 6Z"
{. 4,83
.7 5( 2,5S[4- .7 5(.2,5g)(;77 f 4- 7.13(,y15)[5Z)*
13= IL ,C = 3 0 in N
~
3= W
- 1. Olo
= \ , LS (o t v1?
(Ylem b3 2h k ~L3 i ses 1 1 " x 1.~15" /+: 11. Ii
,n 4 3,57 i,?
1,='l(1,159 - iz 3,i3 5, 3 So in 4 5 l'f.1 '" ! h = 1.15Ct >t _,
- .5-I
! Set, 7_ 16.5" O,D. Y I 5" 1. D. A=_TT{ig,g_,I 2 zj= 57, L, = g ( ,, (,g 4 3z
- 13o0 inY h II5*oan\
h =1 = % 1X - s s y = Se : lift =/39 od S.26
F-L yg <a 2. 9 C y x 7 2 5' A = 2.is l y= 4. 5 9 S3 = 2,19 1 .g = , y'3 z Se = ,3 V3 th< m b 30 $ 32 S " O. D. x 7 " 1. D, k= %(f-Y) 11. ~7 1 3 = 7 (p V n
-g ), y V
Ly = T_.z , Q = 3 3 , ) 5 = $ = g5 _ ,o ,n} 1
- t. y Memk 3l 526 I SMvc h5 SG6 2 # MWh M
- 5es z et = s d = . 9 T7 12AS.
s,,, a = . fr 3 d- % a =. 5% 5cc R onitK 2 .S" k' / " lI # 4.s" ,,, 1 ' 4% ed. p g ge 14, CME Il A= zd Rt 2_L 977XysMd =. 4,4 '"1 - 7_.g : 4.5'(.5)(,all . 9 3 C,5Q) = E3- I - T
-3 4.5'(.5)(.977 + .13 C 59 z l'S' 4 ,,
)* 4
- D S'I" C5 '"
O L.s Tm+,u. sw u+ e i cs , m u t+ se3 2. 6, 2 A = S 8 in T 3
- r50 in 4 h = 46 inY 3
s g -=. 2.s i n 3. St= to iw .
F-7 m e , A .v 3 es t a L a To % lI m<mbs '~6 3 il 0'"3 3 - ' k
- Y S 'b 4 6 I;l t Esst,, on nr Pipe A- = 2, z/z. .Iy = G . o 3 I.3 : ~I.g - 3, o 'E inI 1, '! ? m?
S3 = 5:2. = Membs 4 3 T'o % 5/s" b o L-f5 - 75' inY
.o15' 1 = La = , o A: ut T_.3 = 3 s . , S , = . o t q , n '.
iwmbs (4 'l To 54 O mo ra z o" o,d x ;q_i." t 1.D. Ce s G 4 I = 15.5 I_.x : tsoo I:17 3 = 7 50 i n . 5 9 = Ss = 15 s n? M <m 6 55 5;.)^F-r 5=b.m 3 5% i 1. sw" 4 A =. 2 . s r x : 1.z.i 1 :3T. t =.. c o
- 1. El a y,sq n : 7_.y 0 1 3 z I g = 1. W 5 p 5t:
Sec 7. g,3 i 4 A ry)<w1b 56. /S h A- f= T-E' Tb 'N A . 6,I (f Iy = ((,"Z.7_ T_.3=T.e='Z II s,=5 4 =1.W h YMe mb 5~7 Sh A r= T Iy : Lt = f . o Z125"6 k = 3. 54 ly 2, o 3 53 = $t =- 94E in.
E-B O m m bs GS,59,60,p1 M cTo (L 5 h A F-T k C P (-j
- 2. I 7 5O , 5 A-me As m e mb 57 mambs G 'L , 6 3 , le Q Do.,mv me4ces 4o Get b eg. L o Sos membs LS 4 L4 1
1.f. S ARS A= 5 in z i 5 3 = 3. 3 3 3 = 6. 6 6 (C) T 1 . G 5' Sa = l- 'I ' " ~
/
m om b I k 10 7 2/ (1)( >) (.L = 7 " i
, i -
7" b = 46 -7 = 39 , 100 8 2.
- f ~/
b ' f 46 a t 1 n.s - e g, ,e
! - "h r -i - - I --
y - b' ._ [e
~ - [-- } -%
1E" > P = <19. 5 0 05) = u, z.s-
&o A e, y 5, m i t * * *1 h5 <-
h= t 3 4y 4)( $( ) g i e co(lq ,5) Q=-h G M == W O K=j s
. c I co V/ L *iMJ ge = Q T = h = Ll * = z y , ,o = ', 'fp
(,L-Ul*j G _-
F-8 l 1 Lm cy- na A.wlus - /W(+ 1 LRB Le Ar Bi sgm Wi l I A men Co, 4i Ava U-D - 16 o s q.% REU. 3 - PLIMP ASSEMBLY REV . O - Tn/& B/zpctcGr 6-3385I% H-SS44 RSV. 6- VoLore cnse t M-3315 2.ay, o- STu/=/=/us Box D- Il 294 Re V. 4- PUMP super D- (2cDo REV. o - PL=Das7x& pernic b- 12o 92 R G V- E- SA56 D - 12.s o 6 l2 e V . D- CDP BnsG . D-15s29 peu. A- I m p e c c ent i y g PE.B e.ETAL Ws4o
' ) I "9 k' a cal 2sYr 5.S+ /4 9 = 53/[.NW f I h44 s
- t
- j= 2 (7.7s3(7.7s1/2. = Z
y
* 's
.,,,....,..a ,,......,~c, 1
~
^
K, < 101 {2 D 35$ <- 7.h.rs')(Imsf+ ta.sM](f r2. Iww ' 33 6 \ X ' D E b ' 6 . 3 4- { p s.w Iyy = %M25f GA.Si+ 2 (7ayh.2Si > l69 (pb rt
$ (N
~7,25
~
O.
Q pEb30) x 6- M A-S SE $ ss(wfw) C o me o wewT Wi p+ . Lt,s m 70, ,,- (on Mele f) iNP-cheR. GS (lut . S I'*f) ,17 . Il C.c o p lia 6 So Cac 5A-r) .13 33 Pu m p 12.s o 83 i'9 C.asin3 660 1, 7 / /f ! Bec\ PLATE 330 * *b Moroe LO fo7wL 2SSS ' 30 mi i3, M=t/3(17.5e) '= f33 d5 m= z.16 10 'n ~ l9 , W = I/3(, t 7,56) = M/ 7 IYl-: / , 3 $' 1 o 'n 7 % , W = 33D dS YYl= 2, ) T v O
", k P P EMDIY k N OR.1, c. boAD.5 D l
^Y !
o DISMJige l zt'/s" l X sucr= i, bo# u MooEL LO hw C Ase hs Lsowec & w+ ,3 6 = ha +FYs = l ees + 4e6s = 6(o93 Les P 45 3: F3g + pgs n'. 2 Z 5 0 + /9/ $ = 4/65 F=F33 3 -t Fg3 = / c50.+- /459 : 2507 E5 M X = Mya 4 M y3 + n,tts Fed 1"- b
=(/ 300 + +6/z)(it) + 2r IIS C./ 050 ) = 94 / 7 N
32 Nd+M g g3 + q,in g -
= (3o0o + B2/9) 00 4 9.12s(/459) = / 4 7 94[3 ,
Yt 1= M a a + Mgs 2.2.. i ts Fx g
+ 9. I t s F3s +
= (.zooo 4- 2+B40t) + 9.1zs(f et/5) + 2.z.1zs(1ses) = /I, / n-ws e 85
SARGENT&LUNDY
'M ENOINEEMO
~
"' * / H-2185 Supp. 3, 11-24-81 1
s N-2 !t
/ATTACHMENTC L _ Sheet 1 ,
Supp.3 l Pipe Loads on RBCCW Pump Nozzles l (WR0lPA,B,C,D) (F in Ibs., M in ft. Ibs.) i Suction Allowables SRSS FAg 1,820 4,868 F 2,000 1,915 B (YJ F 1,620 1,459 C% A ( X) ,5,600 4,612 M 5,200 8,219 B (YJ (O M 5,000 2,486 c 3) F R ' M 5,700 9,746 R Discharge
- F Ad 1,800 2,250 F 1,620 1,825 B (,%)
F 1,440 1,050 C (,h M , ,000 A (Y} 4,500 M Bh , 1,300 M 4,000 , 2,000 Ch F ' ' R M 4,600 3,832 R
- Discharge Loads Revised
}'~ o M P.
M L cu2NT CINCINNATI CAS & ELECTRIC COP.PANY Pi;OECT ZIMMER - 1 JC3 NO. 4130-3.5 gg10{;,g gI,Jg CECGN DY T 7<t,A t*,TE 01 R i
' T* W 'M M CNECXED CY'l L-pA C',TE us.or S.EET 3 OF +
( any. we. DATS fW811ALS
~
. m crs .
200 l00 50 33 20 10 - 2.0 1.0
. ~
20.0 "i i i e iiis iisa un on un u" aa i i i i aii i io. u w i." i o on iu. . ,. . .
. 20.0 15.0 15.0 10.0
-1010 8.0 8.0 - i e i
' i.
l l 6.0 6.0 - 4.0
- 4.0 -
3.0 3.0 d
>I \.'.i 2.0 2.0 _ .
1.5 fh 1.5
.\ \ -
> 1.0
. 1.0 - p. i ,
\ , f ./- I 3 i I .i!' ,' O.8
/ " l '\ ' / I 0.8 Nii l - i e ;
- a. -
/
/ \l J I' O.6 0.6
- 1 Vf i l.
$z
. i 1
E ( 0.4 $ ! k 0.4 . l
~
- 0.3 O.3-_ _
_~ 0.2 0.2 _
' O.15 0.15 '
1 -
~ i 0.10 0.10 - !
e i,, H -
' ' ' ' ' ' l- ' ' ' ' '
I i'" 0.08 O.08
, i i t ii-
'.L - I ! l I I ! I I i i# I t t i l a l l 1 i '- .
! I I I L _
~
' O.05 0 .1 J "'>r d3 b i'.4I.:"d>"l'!lI'
'" ' '~"
6iI'I
.01' ' ' ' ! ' . '0".04"I"".
0.05 .6 .6 1. 2
.COS .2 .
n n REACTOR BUILDING-ELEVATICN: 50 ., 570,'
'. MS & EW RBCCW PU.'.P RESPONSC SPECTRA !!OP.!ZQ3bp'2'* <- CAI'21T'
.t.-
ENVELOPE OF UPSET A$D EMERGE: ICY CCNDITICNS REFERENCE FILE NO. EMD-024252 - -
- - , --e.,, - - , , . , , - - , - - - - , . - - , _ , , , , . ,
e... ' 1-2. CINCINNATI GAS T. ELECTRIC CC.V ANY
- I
,_. wyg7 !
\
pp mDr-ma M,q 0 ru-a. m,, FRCUZCT ZI.v::ER - 1 . x3 NO. 4130-15 h 'd ' CF.SGN DYS~Th DATE 02 - t U 7 L : r C4MME CHZCXED GYL%%e4 CATE 2.-neeSHIET 4 OF 4- ! 3 8 V. MO. DATE IWl7taL3 s m ers . 200 100 50 33 20 ' 10 2.0 1.0
. 20.0 ;;" i i a i iiei aio "" "- ou " " " " i e i i a e "" "" "" "" i"' '"i * ' i' .' 20.0 15.0 15.0 . 10.0 -
13.0
' l '
8.0 - i i 8.0 6.0 .
, \ ' ' . 6.0
)~L . ;
4.0 i \ 4.0 3.0 E
)' '
3.0 2
\ l
. 2.0 _
( . 2.0 1.5 h ' '
; 1.5
~
\ :
1.0 / 1 1.0 _ y . , , .. \\ . . . . -
/' I I I '
I i \' fi i 0.8 a 0.8 , e ; i i i , gi... j 1 0.6 I \ I' O.6 I \ f, l \1-- 0.4 x 0.4 _
- h:',,
O.3 0.3
~
0.2 - 02
~
3 0.15 _ -f 0.15 0.10 - _ O.10 i t i . i e
? 7
' ' i i
i'. O.08 0.08 - t i i i ii i l i j i ! .. l I l t l ll i ' I i l i-
~' "' ' ' ' ' ' ' ' ' ' ' ' '""' ' ' ' h' O.05 0'05
.COS .01 .02 .04 ' ' ' "". 0 6.1'''".3 .2 -
4'" ."6 '.u'!'. 1 v y' . 570' ;
/z. REACTOR DUII. DING-ELEVATION: 50a , VERTICAL i RBCCW PU:1P RESPOt!SE SPECTRA ENVELOPE OF UPSET AMD 1. !ERGENCY CONDITIO::S - 11, NID 2% DN! PING REFERE:CE FILE F10. E"D-024252
h, 4 J i
' APPENDIX J- - ' FLANGE ANALYSIS 4-
) (a) Stuffing Box'
. *fN i 1 i
i
- g.
Cl OU,*;C. ,- T eil.'"4
- . l*f Kya - ( C ..C.C . QCpC (*. .*!9. . . w .C,*gp .Qft..f.*N M fI.p,Y]tp s . C \,
i
; F t
- A = **.. . 5 5 = **.5
. i = 5./.. 9' N = 1 ^. DB = '
,i (1 v z .1 4 . %. Q E.e .
= . E =.. 4 I= 9 . 4 E.*.
2 f.s } : . ,' sC a (*h E .' 7 5 f 2 S V = '49999 O = }9h
..; - .. .. e.. . as .
p - ., w:.co. r ..C.v c -
*e .e. .
. .s C....i--14i i p .- . .. .=.
I
. (*.C.
C Q p " T. [j.*4 ', C.;*". C C C. .C. ; , C C.; ? 1 I 1-4 r .S.c. Tl.p.t. A.t , . rie,s . ..,s% . t.,s.. .:. l ."sh. U.it. sa CTgwCC.,ov ? o.*p s.te. T i .N. *. n.'. r/',.1 v- q.. .*. 4 } (p(y,*, t w . C w t. ' . . . QbQ.T yt . ' . _
"t CCC,
~
. e C.f K ,1., %. . . e... s (.y',e.*,
4
'eAh. .lF0-C h." t. A t . .
C.T. q .
" c C. C. , , Cw"T" o.L.Q v /t. s.aQ(y(p e '
-'cH&so)/2 o is7 21000 *
- f. C w U. . .n.C, *T' ) / .". 09.7O v/ v o 4. (*,I I#N. -
B'.I' T c. ' :: .rc.':'.
. -w 1 (.).tco "* eor.>r ,
m i C /."+1 . *l" : )IC. . C. ,*p.r . . C -w C;C ** C. . C.C., T . r)C T*tA' 1*
- O'Jr4 .cc 4
1 5 ."Alr? . TT. e.t r. uts.C 0.; T --g "'" r C., . CU t*** 3. 4 * . *. g ,(s.e
. . " h)C,1 -
s - - t Q
.< QT.i T. C'. C. DC-C.; C. . C .*. "'* /.,9. c. .
. in e',(
' [ N g f.C htT
- Css. 2.,T C C '.,s2, C." /t Og")*J . s1(ye .e
( C s . J. C C .t .t .*, s
- n. .*.=4.
. .-p*. . (} = ,1 (,,.~,e .
( C. u. a..C T .\ .p #>
- t. ' K.5. .*. f. . f hi.y'<
"1 *
*c, e. . , ,' .
O.
. i.9 "l'" C w ""-Q :" C C. -
'"I '.s .
i Ci.fge C C. ' 6 C C .S... *t h ' C.,*:" O. m :T C.; e t
;/ =
s g . /t c. T - . "/ .4 C o cwv,er/. *7 s . '.7
- .. 2."O. rga i (* * *** .. ". tl u at3 . / **..f..* e
- e* - . .O
. v. = - =. . . %.- o. s A. t, / 1 a.. s = . ==wQ3c=o, w + s } C = e Oe*+ . . .
- O. *- C =wt,ot n .
C = 1
. i. / P
**. wSO. = .
' J. / W.Q,
= f".)
4 1 1 ! l j a C q.a .C c. . C = C. C. .
- : S .. T . i o.C.,
I 4 e
- u,o.i e c -
4 v.v(.e.. . . . e w i. = - .
.o. f.~- c e . c.., . .
. . , 3p .. o. . .. -
.,r. A s
- t. .- s
,..~.;.O C F.,.i .T L*10 : t- S pwCC . C. .a t. C~ C.
?^ p j C. . C. . = "..S.g"...O
. O C ..*t = .v =Q.C 3
Cl c.a.se .C w.rie,:"Att A , wc ! a*O- "* v? ? =.I.<W.C C.. t t L 4..f"e .g ~4
.==*E
. . .y 1 WY = 4
. . K.
+ 1 C.1 QNc4.C .. s t 7. -A wwi r.C . 4.* sw
- c. .*. : n c.
M t {
- s
.e...
wg " - cc.Ao - vv .i...e.*
-= - -
s .< ow..
. . + e.
4 b\ ' C of e .-'W ..$%. . + . Y h $ e. .e . . .e - %
- v e- - s. ; . u * .* = .s;4n %T , ar .94s- ,~.5 s.c- i
{ :. 4 <,-4ee-
, . - 4.-- ,-.n-. --- -w,,.-.y.-g,ye.7-,3 ,,,,73y.-,-,-,-w.,.m,-,,,-..,,-,r+, ,--,,,..w-.-
,.y,-,,.+.v- ,,--.-,-,.,,-,,r.,,.me--,-,-,-*,,,e,-,,ww-rwwen
J-2 (b) Discharge Flange Analysis bT slaNGE INPUT DATA (SEE ASME CODE FOR NOMENCLATURE) 4= 15 B=3 C = 13 N = 12 DB = .875 G = o.?l289302 AB = .419 T= 1.5625 G1 = 1.125 00 = .59 M=3 Y= 10000 P= 150 MOM = 28624 F = 2250 TEMP = 150 SMALL B = .353553391 OPERbTING STRESSES, PSI
.4CTUAL ALLOWABLE LONGITUDINAL HUB STRESS, SH 5656 21000 RADIAL STRESS, SR 4326 21000 TANGENTIAL STRESS, ST 3101 21000 (SH+SR)/2 4991 21000 (SH+ST)/2 4379 21000 BOLT STRESS 7014 25000 BOLT UP STRESSES. PSI -
ACTUAL ALLOWABLE LONGITUDINAL HUB STRESS, SH 14347 21000 RADIAL STRESS, SR 12077 14000 TANGENTIAL STRESS, ST 8658 14000
"~NSH+1R)/2 13212 14000
(/km SH'ST)/2 11503 14000 90LT STRESS 21887 25000 CL4NGE SHAPE CONSTANTS X= 1.075 T= 1.55446061 Z= 1.79503106 U = 3.57874728 Y = 3.25666670 V- .24459278
- = .335125009 SMALL F = 1.26839011 G1/G0 = 1.93o65" H/HO = .464238345 CLANGE STRESS FACTORS SMALL D = 10.6027893 SMALL E = .3376o7052 L (CR LAMBDA) = 1.39078923 EOUIVALENT PRESSURES' e
*E = 178.9 PCD = 328.9 LANGE MOMENT ARMS. INCHES HD= 1.0375 HG= 1.54?55339 HT = 0.0217767
- LANGE LOADS. POUNDS
,M1 = 95269 WM2 = 110048 s
I :1.4.0E MCFENTS, !N-LSS
" 5 = ' .:no t MO = 152n7 MT = 17881 MD-MG-MT = 65174
J-3 (c) Suction Flange Analysis i
,LANGE INcVT DATA (SEE AM.E CCOE FOR NOMENCLATURE)
A= 17.5 9= 10 C= 15.25 N= 16 DB = 1 0= 12.0429432 AB = .551 T= 1.8125 G1 = 1.31 GO = .53 . M=? Y = 10000 P= 150 MGM = 103041 F = 4 sos TEMP = 150 SMALL B = .353553391 OPERATING STRESSES. PSI ACTUAL ALLOWABLE LONGITUDINAL HUB STRESS, SH 9140 21000 RADIAL STRESS, SR 5352 21000 TANGENTIAL STRESS, ST 4138 21000 ( SH+:?R ) /2 6771 21000 (SH+ST)/2 6164 21000 BOLT STRESS 7733 25000 BOLT UP STRESSES, PSI ACTUAL ALLOWASLE LONGITUDINAL HUB STRESS, SH 16172 21000 RADIAL STRESS, SR 11475 14000 TANGENTIAL STRESS. ST 8871 14000 [ish-SR)/2 - 13824 14000 L iSH+3T)/2 12522 14000 BOLT STRESS 15165 25000 FLANGE SHAFE CONSTANTS K= 1.75 T= 1.60463733 Z= 1.o6060697 U = 4.00224229 Y = 3.64204801 V= .1971*41*1 F= .91544237 SMALL .c = 1.5122'017 G1/GO = 2.258620 H/HO = .51003424o FLANGE STRESS FACTORS SMALL D = 16.4429314 3 MAL *_ E = .3385c4014 L (CR LAMBDA) = 1.36777074 EQUIVALENT PRESSURES PE = 343.1 ocD = 4*?.1 FLANGE MOMENT ARMS, INCHES HD= 1.47 HG= 1.6035523? HT = 2.1142767 FLANGE LOADS, PCUNDC-lM1 = 68182 WM2 = t32645 , y CLANGE MOPENTS, 'N-L25 10 = 270 FO = ;,e* ** = ?' e9 C ~Q-MT = 132424
t ! I T AllACHMENT l l 1 P 1 1 1 1
)
l l l i i l l
. _ . _ , , . . . , - - - . . . - _ _}}