o ATOMIC ENERGY COMMISSION - IAEA

BARC/1992/E/004

03

n

I

THE STRESS ANALYSIS OF MODERATOR PUMP CASING OF RAPP-3, 4 AND K.AIGA-1,2/».«•

D. S. Chawla. B. K. Dutta and H. S. KushwahaReactor Engineering Division

1992

BARC/1992/E/004

g GOVERNMENT OF INDIAo ATOMIC ENERGY COMMISSION

<

THE STRESS ANALYSIS OF MODERATOR PUMP

CASING OF RAPP-3, 4 AND KAIGA-1, 2

byD.S. Chawla, B.K. Outta, H.S. Kushwaha

Reactor Engineering Division

BHABHA ATOMIC RESEARCH CENTREBOMBAY, INDIA

1992

BARC/1992/E/B04

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10 Title and subtitle : The stress analysis of moderatorpump casing of RAPP-3,4 and KAIGA-1,2

11 Collation :

13 Project No. t

20 Personal author(s) :

67 P., 12 tabs., 18 figs.

D.P. Chawlai B.K. DuttaiH.S. Kushwaha

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» Reactor Engineering Division,Bhabha Atomic Research Centre,Bombay

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InformationAtomic Research

60 Abstract : In the PHWR far circulation of moderator (heavywater), the centrifugal pumps are used. These pumps are safetyclass 2 components. In each of the units of RAPP-3,4 andKAIGa-1,2, there are five such moderator pumps. The piping loadsacting at different nozzles of the pump casing were found to beseveral times more than the values quoted in API Standard 610.Hence it was required tD qualify these pumps units as per ASMESection III NC. The detailed stress analysis of pump casing iscarried out using finite element technique. The threedimensional finite element model of pu«p casing is prepared dueto geometrical and loading complexities. Analysis has beencarried out for each of the five pump casings with theircorresponding load̂ .. The analysis showed that the stresses inall the pump casings is less than allowable stress intensityvalue of the material as per alternate rules given in ASMESection III NC-3200 (1977).

70 Keywords/Descriptors : RAJASTHAN-1 REACTOR; RAJASTHAN-2 REACTOR;MODERATORS} HEAVY WATER; PUMPS) STRESSES); STRESS ANALYSIS;FINITE ELEMENT METHOD; NOZZLES; N CODES; THREE-DIMENSIONALCALCULATIONS;

Additional Descriptors :-

CASING; KAIGA-1 REACTOR; KAIBA-2 REACTOR

71 Class No. : INIS Subject Category: E3400; E2200

99 Supplementary elements :

THE STRESS ANALYSIS OF MODERATOR POMP CASING

OF RAPP-3f4 AND KAIGA-1,2

BY

D.S.Chawla, B.K.Dutta, H.S.Kushwaha

Keactor Engineering DivisionBhabha Atomic Research CentreTrombay, BOMDAY - 400 085

1.0 INTRODUCTION:

In the Pressurised Heavy Water Reactor, the heavy water isused as moderator. With the increase in temperature of heavywater, its moderating property deteriorates. To maintain therequired temperature of moderator in the calandria, it iscirculated and cooled in heatexchanger. To have the circulationof moderator, the centrifugal pumps are used. These pumps arccalled moderator pumps. There are five such moderator pumps ineach of the units of RAPP-3,4 and KAIGA-1,2. These pumps arcsafety class 2 componenLs. The piping loads acting at differentnozzles of the pump casing are found to be several times morethan the values quoted in API standard 61011]. To reduce theloads various piping layout were tried. Taking in toconsideration the locations of various reactor components and itscompactness, a final layout was chosen. For this layout also thepiping loads on different nozzles of pump casing are more thanthe values specified in API standard 610. Hence it is required toqualify these pump units as per ASMC Section III NC12]. It wasdecided to carry out the detail stress anslysis using a 3-Dfinite element model due to its geometrical and loadingcomplexitiesl3]. The present report describes the finite elementmodel, the loads, the procedure for the stress analysis and theresults.

2.0 DESCRIPTION OF MODERATOR PUMP CASING:

The arrangement of complete pump-motor unit is shown infigure 1. The pump is supported by a stool at the bottom. Themotor and its stool are placed on top of the pump casing. Theposition of pump is such that its suction nozzle is vertical anddownward, whereas discharge nozzle is horizontal. The heavy watermoderator enters the pump casing in vertical direction from the

bottom and ia forced through discharge nozzle by a radialimpeller.

The pump casing is double volute casing. Figure 2,3 and 4show defferent sectional views of the pump casing. The geometryof pump casing varies at different angular sections. A spiralsplitter divides the volute in two parts. Figure 5 shows thevariation in the geometry of volute at different sections.

The geometry of pump stool is shown in figure 6 and 7. Thestool consists of top annular plate, bottom annular plate and twolegs. Both the legs are identical in shape and Bize. Bottomannular plate is slightly bigger than top annular plate. The pumpcasing is installed on top annular plate. The bottom annularplate is fixed to the ground. Above figures 2 to 7 are taken fromreference!4].

The material of pump casing is SA 351 CF3M type 316. Thedifferent mechanical properties of the casing material are listedin table 1.

3.0 FINITE ELEMENT MODEL OF CASING:

Due to lack of symmetricity, it is found essential toprepare a 3-D model of the pump casing. The model includes 3364nodes and 2426, eight-noded brick and six-noded prism elements.Incompatible modes in the shape functions have been considered in3-D elements to improve their bending properties. The casing ismodelled by dividing the whole configuration in to 39 differenttwo dimensional sections radially. The finite element mesh oneach section is prepared and checked thoroughly by plotting. Thetwo dimensional plots of the mesh for different sections areshown in figures 8a to 8m. The location of these sections areshown in figure 2. The three dimensional model, which has beenprepared by using two dimensional cross sectional mesh, is alsochecked by plotting. Fine mesh is taken where ever the highstress gradient is expected, while away from these locations, themesh is little coarse. The three dimensional model is shown infigures 9a to 9c as viewed from different angles. Figures 10a to10c show the model of pump casing after removing hidden lines.

To avoid the ,uncertainity in boundary conditions at thebottom of the casing, the pump stool is also modelled. The topannular plate of the stool is modelled using 158 eight-nodedbrick and six-noded prism elements. The legs of the stool aremodelled, by using 112, thin plate and shell bending elements and150 nodes. The bottom annular plate of the stool is fixed to theground. So it is decided not to model the bottom plate andinstead the bottom of the legs can be assumed to be fixed. Figure11 shows the three dimensional finite element model of the stool.The plot after removing the hidden lines is shown in figure 12.

The complete finite element model of moderator pump casingalong with the stool contains 3740 nodes; The complete model is

shown in figure 13 to 14.

4.0 LOADINGS:

Following loads are considered for the stress analysis ofpump casing.

(i) The internal pressure of Heavy water in the pump casing willvary from suction nozzle to discharge nozzle. But for the presentanalysis the pressure is assumed to be constant. The value ofinternal pressure is considered as 0.14 Kg/mm*.

(ii) The piping loads acting on discharge nozzle of pump casingfor different pumps and also design loads as supplied by NPC arcShown in table II. The static loads are combined with SSE loadsas per NB-3650(1977)[2].

(iii) The piping loads acting on suction nozzle of pump casingfor all the five pumps and also design loads as supplied by NPCare shown in table III. The static loads are combined with SSEloads as per NB-3650<L977)I 21.

<iv) The loads due to pump motor and motor stool coming on thetop of the pump casing are shown in table IV [51. There are twosets of loads depending upon the choice of the signs of SSE loadsas per NB-3650!1977).

(v) At the top of pump casing eight bolts are provided forconnecting the motor stool, stuffing box and pump casing. Atorque of 10 Kg-m 13] produced by the bolts is considered in theanalysis. Above torque is equal to the load of 2272.72 Kg perbolt.

5.0 NISA - A FINITE ELEMENT COMPUTER PACKAGE:

The finite element computer package NISA [61, NumericallyIntegrated elements for System Analysis, is used in the presentanalysis. Salient features of the computer package 'NISA' are:

(i) analysis of one dimensional, two dimensional and threedimensional finite element models.(ii) linear and nonlinear analysis.(iii) static and dynamic analysis.(iv) heat transfer analysis(v) restart capability(vi) multi-point constraints facility(vii) elastic, elastoplastic, creep material models(viii) buckling analysis(ix) big element library(x) preprocessing facility<xi) postprocessing facility

6.0 ANALYSIS AND RESULT:

The three dimensional stress analysis of pump casing modelis carried out using finite element technique. The analysis iscarried out for each of the five pumps separately and also forthe design loads. The analysis is done for two different casesfor each pump. The loads corresponding to these cases are shownin Table V and VI. Load at top of pump casing due to pump motorand motor stool (as shown in -table IV) is different in two cases.Case 1 considers the first; load sot; whereas case 2 includes thesecond set of loads from L.ible IV. In addition to these loads,the stress induced due to seismic incrtial forces in pump casingbody was computed separately. These stresses were found to benegligible in comparision to the stresses due to other tabulatedforces.

The maximum stress intensities in different regions of thepump casing for each of the pump are shown in Table VII to XI.The same for the design loads is shown in Table XII. Figure 16ato 16m shows the stress intensity contours at section 1 to 13 ofpump casing for case 1 design loads. Figure 17 shows theisometric view of pump stool legs with different plate componentmarked as A to H. The stress intensity contours for these platesare shown in figure 18a to 18h. It can be seen that the stressintensities in all the regions of the pump casing for each pumpare well below the allowable stress intensity given in NC-3200(1977). The allowable membrane stress <Sm) of the material is12.0 Kg/mma . The maximum stress intensity considered at anylocation in all five pumps is found to be 8.9 Kg/mma. The maximumstress intensity due to design loads is found to be 9.9 Kg/mmx inthe stool, which is less than the allowable membrane stressintensity (Sm) value of the material. Hence no attempt has beenmade to classify the stresses as per ASME Boiler and Pressurevessel code.

7.0 DISCUSSION:

The three dimensional stress analysis of moderator pumpcasing of RAPP-3,4 and KAIGA-1,2 is carried out using finitoelement technique. Design has been justified as per alternaterules given in NC-3200(1977). The stresses in all the regions ofpump casing for all the pumps is less than allowable stressintensity value of the material.

ACKNOWLEDGEMENT:

The contribution of Shri S.K.Saxena and A.Chakraborti ofNPCIL 235MWe is acknowledged.

REFERENCES:

1. Centrifugal pumps for general refinery service, API Standard610, 7th Edition, 1989, American petroleum institute, Washington.

2. American Society of Mechanical Engineers, Section III

3. Qualifying the moderator pump motor units for RAPP-3,4 andKAIGA-1,2 for structural integrity as per ASME, Section III NCand as per Seismic input for KAIGA-1,2, NPCIL letter No. RAPP-3.4/32112/91/B/1301, dated February 7, 1991.

4. Drawing no. 0CP10062 (PUMP CASE) and 1CP10121 (PUMP SUPPORT)of Bharat pumps and compressor!! ltd., Naini, Allahabad.

5. A. Neelwarne, R.S.Soni, H.S.Kushwaha, External forces andmoments at the top of pump casing, RED internal communication.

6. A finite element compute package - NISA (NumericallyIntegrated elements for System Analysis), Engineering MechanicsResearch Corporation, Michigan, U.S.A.

Table I Properties of the pump casing material

Material

Tensile strength

Yield strength

Allowable membrane stress(Sm)

Young's modulus

Poison's ratio

SA 351 CF3M TYPE 316

49.30 Kg/mma

21.14 Kg/mm2-

12.0 Kg/mmz

19400 Kg/mm*

0.3

Table II Loads due to piping at discharge nozzle of the pumpcasing with respect to local axis.

PumpNO.

1

2

3

4

5

DesignLoads

DW+PU+THOBE (±.)SSE (±.)

DW+PR+THOBE (±)SSE <±>

DW+PR+THOBE <±>SSE (±)

DW+PR+THODE (±)SSE (±)

DW+PR+THOBE (±)SSE (±)

DW+PR+THOBH (£)SSE (±)

Fx(Kg)

3671117

1031016

81110

2041020

7371626

7371626

Fy(Kg)

262133

-1911117

2184062

-1994164

2602947

2602947

Vz(Ky)

714164

-365125193

-375135209

-21094146

-1756196

-175Gl96

Mx- (Kg-m)

-2042031

62711

-213040

-731727

3093047

3093047

My(Kg-m)

3082844

31891141

18586135

9566

- 103

-3884368

-3884368

Mz(Kg-m)

1591727

-47610

-3732844

-252742

4111829

4111829

Not.f»: Local axis for above loads is shown in figure 15.

Table III Loads due to piping at suction nozzle of the pumpcasing with respect to local axis.

PumpNO.

1

2

3

4

5

DesignLoads

DW+PR+THOBE (t)SSE (±)

DW+PR+THOBE (±)SSE <±)

DW+PR+THOBE <1>SSE (±.)

DW+PR+THOBE (±)SSE it)

DW+PR+THOBE (±)SSE (±)

DW+PR+THOBE (±.)SSE <±.)

Fx(Kg)

-3601419

-1720104130

231074105

-1720104130

-3681419

-1720104130

Fy(Kg)

-7202640

-711106171

-9235662

711106171

7282640

-711106171

Fz(Kg)

2240132209

-3630248346

3.8542871

-3630248346

2240132209

-3630248346

Mx(Kg-m)

-4392846

-525282

8.667

525282

4392846

-525282

My(Kg-m)

-108072114

-1560113159

-2.34500804

-1560113159

-108072114

-1560113159

Mz(Kg-m)

-1661118

4464471

-9714651

-4464471

1661118

4464471

Note: Local axis for above loads is shown in figure 15.

Table IV Loads at the top of pump casing due to pump motor andstool with respect to local axis.

Fx(Kg)

Fy(Kg)

Fz(Kg)

Mx(Kg-m)

My(Kg-m)

Mz(Kg-m)

DEAD WEIGHTSSE (±)

0.0 0.0 -2241.0 0.0 0.0 0.01425.0 1425.0 576.0 1916.0 1916.0 0.0

Note: Local axis for above loads is shown in figure 15.

Table V Various loads acting on the pump casing considered in theanalysis for the case 1 loading w. r. to local axis.

PumpNo,

1.

2.

3.

4.

5.

Location

ABC

ABC

ABC

A0C

ABC

Design ALoads B

C

Fx(Kg)

3B4-387

-1425

1191850-1425

262415-1425

232-1850-1425

763-387-1425

763-1850-1425

Fy(Kg>

59-768-1425

-208-882-1425

280-985

-1425

-2f>3082

-1425

307768

-1425

307-882

-1425

Fz(Kg)

1352449

-2817

-558-3976-2817

-584874.8-2817

-356-3976-2817

-2712449

-2817

-271-3976-2817

Mx(Kg-m)

-235-485-1916

73-134-1916

-6915.6-1916

-100134

-1916

356485

-1916

356-134

-1916

My(Kg-m)

352-1194-1916

459-1719-1916

320-806.34

-1916

198-1719-1916

-456-1194-1916

-456-1719-1916

Mz(Kg-m)

186-184

0

-57517

0

-4171022

0

-67-517

0

440184

0

440517

0

Note 1.A-Discharge Nozzle, B-Suction Nozzle, C~Top of pump casing2. Case 1 loading also includes internal pressure and bolt

loads at top of pump casing.. 3. Local axes for the above loads is shown in figure 15.

Table VI Various loads acting on the pump casingthe analysis for the case 2 loading w. r

considered in. to local axes.

Pump Location FxNo. (Kg)

1.

2.

3.

4.

5.

DesignLoads

ABC

ABC

ABC

ABC

ABC

ABC

384-3871425

11918501425

2624151425

232-18501425

763-3871425

763-1850L425

Fy

59-7681425

-208-8821 425

280-9851425

-2638821425

307768

1425

307-8821425

Fz(Kg)

1352449-2817

-558-3976-2017

-504074.8-2817

-356-3976-2817

-2712449

-2817

-271-3976-2017

Mx(Kg-m)

-235-4851916

73-1341916

-6915.61916

-100134

-1916

356485

1916

356-134L91G

My(Kg-m)

352-11941916

459-17191916

320-806.34

1916

198-1719-1916

-456-11941916

-456-17191916

Mz(Kg-m)

186-184

0

-575170

-4171022

0

-67-517

0

4401840

440517

0

Note 1. A=Discharge Nozzle,U=Suction Nozzle,C=Top of pump casing2. Case 2 loading also includes internal pressure and bolt

loads at top of pump casing.3. Local axes for above loads are shown in figure 15.

Table VII Maximum stress intensity (Kg/mma) in different regionsof pump casing 1

Location Cise 1 Case 2

Suction Nozzle 1.45 1.81

Discharge Nozzle 1.64 3.39

Top of Pump caning neat-bolts between casingand stuffing box 5.0 4.85

Splitter of casing volute 1.6 2.34

Pump Stool 8.33 5.09

Table VIII Maximum stress intensity (Kg/mm3) in different regionsof pump casing 2

Location Case 1 Case 2



Top of pump casing nearbolts between casingMild stuffing box 5.31 5.12Splitter of casing volute 1.15 2.71


10

Table TX Maximum BtrnaH intrMmity (Kg/mm1) in different regionsof pump casing 3



Discharge Nozzle 1. .68 3.46

Top of pump casing nearbolts between casing

and stuffing box 5.07 4.91

Splitter of casing vnlul.n 1.08 2.19


Table X Maximum stress intensity (Kg/mm*) in different regions ofpump casing 4




Top of pump caning nearbolts between casing

and stuffing box r>.2r> 5.07



11

Table XJ Maximum stress intensity (Kg/mm2-) in different regionsof pump casing 5




Top of pump casing nearbelts between casing




Table XII Maximum stress intensity (Kg/mm*) in different regionsof pump casing due to design loads

Case 1 Case 2



Top of pump casing nearbolts between casing


Splitter of casing voluLe 1.34 2.89


12

ZZTL

MOTOR

MOTOR STOOL

PUMP CASING

PUMP STOOL

ALL DIMENSIONS AkE IN mm

FIG.1 GENERAL ARRANGEMENT OF MODERATOR PUMP-MOTORUNIT

ALL DIMENSIONS A»E W

FIG. 2 CROSS-SECTIONAL VIEW OF MODERATOR PUMP CASING

FIG. 3 SECTIONAL VIEW OF PUMP CASING AT A - A

ALL DIMENSIONS ARE M M l .

FIG. 4 SECTIONAL VIEW OF PUMP CASING AT B - B

_J

R16

RZQA

lie

R l l -

ALL UNENSIONS ARE IN dm

FIG. 5 GEOMETRY OF PUMP CASING VOLUTE AT DIFFERENTSECTIONS

• 610

fS

I

# 1900

FIG. 6 GEOMETRY OF PUH? STOOL

ALL OlMENSIONS ARE IN

•35

168

'I

s

PART NO. (a)PART NO. (b)

Li _ J

PART NO.lc)

PART NO. (d)

ALL DIMENSIONS ARE IN mm

FIG. 7 GEOMETRY OF DIFFERENT COMPONENTS OF PUMP STOOL

FIG. 6 a 2 -0 PLOT OF 3-D PUMP CASING MODEL AT SECTION 1-1

FIG.8b2-D PLOT OF 3-D PUMP CASING MODEL AT SECTION 2-2

FIG.8c 2-D PLOT OF 3-D PUMP CASING MODEL AT SECTION 3-3

FIG.Bd 2-D PLOT OF 3-0 PUMP CASING MODEL AT SECTION 4 -4

FIG.8e 2-D PLOT OF 3-D PUMP CASING MODEL AT SECTION 5-5

FiG.Bf 2-D PLOT OF 3-0 PUMP CASING MODEL AT SECTION 6-6

FlGiBg 2-D PLOT OF 3-D PUMP CASING MODEL AT SECTION 7-7

FIG.Bh 2-D PLOT OF 3-D PUMP CASING MODEL AT SECTION 8-8.

FIG.8 i 2-D PLOT OF 3-D PUMP CASING MODEL AT SECTION 9-9

FIG.8J 2-D PLOT OF 3-D PUMP CASING MODEL AT SECTION 10-10

FIG.8k 2-D PLOT OF 3-D PUMP CASING MODEL AT SECTION 11-11

FIG.81 2-D PLOT OF 3-D PUMP CASING MODEL AT SECTION 12-12

FIG .Bm 2-D PLOT OF 3-D PUMP CASING MODEL AT SECTION 13-13

FlG.9a 3-D FINITE ELEMENT MODEL OF MODERATOR PUMP CASING (VIEW-II)

FIG. 9 b 3-D FINITE ELEMENT MODEL OF MODERATOR PUMPCASING (VIEW-I)

I

UJ

>

z

Ia.o

£ao

UJ

a

FIG. 10 a 3-D MODEL OF PUMP CASING WITH HIODEN LINES ELIMINATED (VIEW-U

FIGlOb 3-D MODEL OF PUMP CASING WITH HIDDEN LINES ELIMINATED (VIEW-II)

FIG. 10c 3-D MODEL OF PUMP CASING WITH HIDDEN LINES ELIMINATED (VIEW-HI)

FIG. 11 3-D FINITE ELEMENT MODEL OF PUMP STOOL

FIG. 12 3-D MODEL OF PUMP STOOL WITH HIDDEN LINES ELIMINATED

FIG. 13 3-D FINITE ELEMENT MODEL OF PUMP CASING ANDPUMP STOOL

FIG. 14 3-D MODEL. OF PUMP CASING AND PUMP STOOLWITH HIDDEN LINES ELIMINATED

(iJ

^

1 .

1

i

(

1

p

X1

^ 2

- Y

(ii)

ir(•>

FIG. 15 DIRECTION OF LOCAL AXES WITH RESPECT TO WHICH LOADS ACTING ONilOISCHARGE NOZZLE ii) SUCTION NOZZLE l » ) T O P OF PUMP CASINGARE GIVEN IN THE TABLE II TO VI

LEGEND

-1 - 0.35

- 2 - 0,7

- 3 - I.049

- 4 - 1.400

FIG.16a STRESS INTENSITY (Kg/mm1) CONTOURS FOR SECTION 1-1OF PUMP CASING

LEGEND

- 1 - 0.4

- 2 - 0 .8

- 3 - | .200

- 4 - I .589

FIG.16b STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 2-2OF PUMP CASING

LEGEND

- I - 0.4

- 2 - 0.8

- 3 - 1.288

- 4 - 1.8

FIC.16C STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 3-3OF PUMP CASING.

LEGEND

1 -

2 -

4—

0.4

0.8

1 .239

1 .8

FIG.16d STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 4 - 4OF PUMP CASING

LEGEND

- 1 - 0 .4

-2- 0.85

- 3 - ! .299

- 4 - 1.8

FIG.16e STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 5-5OF PUMP CASING

LEGEND

1 -

2 -

3 -

4 -

0 .3

0 .6

0 . 9

1 .200

FIG.i6f STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 6-6OF PUMP CASING

LEGEND

t -

2 -

3 -

4 -

0.35

0.7

1 .048

1 .400

F l d 6 g STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 7-7OF PUMP CASING

LEGEND

- I - 0.3

- 2 - 0.65

- 3 - 1.048

- 4 - 1.45

FIG.16h STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 8-8OF PUMP CASING

LEGEND

1 -

2 -

3 -

4 -

0 .

0 .

1 .

1 .

35

7

200

9

FIG. 16 i STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 9-9OF PUMP CASING

LEGEND

! -

2-

3-

4-

0

0

1

2

.4

.8

.200

•

FIG. 16 j STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 10-10OF PUMP CASING

FIG.16k STRESS INTENSUTY (Kg/mm2) CONTOURS FOR SECTION 11-11OF PUMP CASING

FK3.161 STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 12-12: OF PUMP CASING

F»G.16m STRESS INTENSITY (Kg/mm2) CONTOURS FOR SECTION 13-13OF PUMP CASING

FIG. 17 ISOMETRIC VIEW OF PUMP STOOL LEGS

TOP

MIDDLE

LEGEND

- I - I .

- 2 - 2.

- 3 - 3.

-A- 4.

BOTTOM

FIG.IBa STRESS INTENSITY (Kg/mrf) CONTOURS IN PUMPSTOOL LEGS (PLATEA)

TOP

MIDDLE

LEGEND

- 1 - 2.5

- 2 - 3.

- 3 - 3.5

-4 - 4.

J L

BOTTOM

J L -

FIG.18b STRESS INTENSITY (Kg/mm2) CONTOURS IN PUMPSTOOL LEGS (PLATE B)

TOP

MIDDLE

LEGEND

- 1 - 0.5

- 2 - 1.

-3 - 1.5

-4 - 2.

BOTTOM

FIG. 18 c STRESS INTENSITY (Kg/mirf) CONTOURS IN PUMPSTOOL LEGS (PLATE C)

TOP

MIDDLE

LEGEND

- I - !.

-2- 2.

-3- 3.

-4- 3.5

BOTTOM

FIG.18d STRESS INTENSITY (Kg/mm2) CONTOURS IN PUMPSTOOL LEGS (PLATE 0 )

MIDDLE

LEGEND

- I - 1.5

- 2 - 3.

- 3 - 5.

- 4 - 6.5

- 5 - 8.

BOTTOM

FIG. 18e STRESS INTENSITY (Kg/mm2) CONTOURS IN PUMPSTOOL LEGS (PLATE E)

A 4

TOP

MIDDLE

LEGEND

- I - 1.

-2 - 1.7

-3- 2.589

-4- 3.5

-5- 4.5

BOTTOM

FIG. 18 f STRESS INTENSITY (Kg/mm2) CONTOURS IN PUMPSTOOL LEGS (PLATE F)

TOP

MIDDLE

LEGEND

- 1 - i .

- 2 - 2 .

- 3 - 3.

- 4 - 4.

BOTTOM

FIG.ISg STRESS INTENSITY (Kg/mm2) CONTOURS IN PUMPSTOOL LEGS (PLATE G)

T0P

MIDDLE

LEGEND

- I - 2.199

- 2 - 2.

- 3 - 3.

-4- 5.

BOTTOM

FIG. 18 h STRESS INTENSITY IKg/mnft CONTOURS IN PUMP STOOLLEGS (PLATE H)

Published by : M. R. Balakrishnan Head, Library & Information Services DivisionBhabha Atomic Research Centre Bombay 400 085

o ATOMIC ENERGY COMMISSION - IAEA

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