ML19322B571

Resolution of Acceptance of Electromatic Relief Valves IRV-67 (RC-66) from Dresser Industrial Valve & Instrument Division

ML19322B571
Person / Time
Site:	Oconee
Issue date:	01/15/1974
From:	Thielsh H AFFILIATION NOT ASSIGNED
To:
Shared Package
ML19322B568	List: ML19322B566 ML19322B571 ML19322B574
References
1143, NUDOCS 7912040598
Download: ML19322B571 (27)

Text

_.

HELMUT THIELSCF"

• s.

METALLUR21C AL EN2fNEER' G

9 I

RESOLUTION OF ACCEPTANCE OF ELECTROMATIC RELIEF VALVES IRV-67 (RC-66)

FROM DRESSER INDUSTRIAL VALVE AND INSTRUMENT DIVISION UNITS 1, 2 AND 3 OCONEE NUCLEAR POWER STATION DUKE POWER COMPANY

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1 (jn HelmuT Thielsch January 15, 1974 Report No. 1143 T912040 % g

s INTRODUCTION In Units 1, 2 and 3, one Dresser pilot-operated electromatic relief valve No. RV-67 (RC-66) each is in-stalled.

One additional relief valve of the'same type has been purchased as a spare valve.

Photographs of the spare relief valve are shown in Figs. 1 and 2 The valve is a 2)" size.

The valve is installed in the reactor coolant piping system No. 50 It is i

designated as a Class A piping system.

However, a 2)"

diameter gate valve is installed immediately prior to the Dresser relief valve.

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The documentation applicable to each valve, and identified by the Units (1, 2 or 3) in which they are installed, is included in Appendices A to C.

The docu-montation applicable to the spare valve is included in Appendix D.

The valve is subject to service conditions involv-ing 2500 psi and 670 F.

The valves are normally subject to a system pres-sure of 2155 psi from the pressurizer tanks.

The valve shells were tested by the manufacturer at 9000 psi for five minutes.*

The valve seats were subse-

.b quently tested with saturated steam at 2300 psig.

After erection, the piping systems in which the valves are installed are tested hydrostctically at a pressure of 3125 psi.

However, since this valve was preset to open, it was isolated by isolation valve RC-4 VALVE DESIGN To confirm the compliance of the design with the re-quirements of Section III of the ASME Boiler and Pressur e

Vessel Code, detailed stress calculations'were perfor med by Dresser.

They are included in Appendix F.

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• Additional hydrostatic test are included in Appendix Ecomments on the re

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With respect to the top flange to the lower base joint, the following comment's apply.

" Referring to Page 1 of the calculations (Appendix F), the minimum wall thickness and maximum inside diameter used are the minimum section of that entire wall and exist specifically at the guiding diam-eter of the lower base as noted on Draw-ing 318330 (Figs. 3 and 4), Lower Base.

All other calculations also use this minimum section.

This question was pre-viously presented and it was decided to use this minimum section to show the max-imum amount of conservatism possible.

"With respect to cyclic analysis, this has been performed on Pages 11 and 12 of the attached calculations.

By applying' the maximum stress concentration factor of four, the analysis was performed with acceptable results."

WELD ASSEMBLY The valves are assembled by welding previously machined Type 316 stainless steel components.

The weld assembly is shown in Fig. 3 One of the welds involved represents a circumferential butt type weld identified by the letter "A" between the fit nge and lower base sections.

It represents a " sleeve-type" of butt joint where one member also serves as a back-up for l

the other member.

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• Letter by Mr. T.

R. Bordelon of Dresser Industries dated January 10, 1974.

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i The flanged member of the body is generally seated tightly against the lower base member as detailed in Fig. 4.

As this represents a " socket-type" of weld joint, the tight seating can be subject to questioning since Section ANSI B31.7 shows in Fig. 1-727.4.4 (c), a gap in the root of socket joints of approximately 1/16",

Fig. 5 Similar requirements are shown in other piping and pressure vessel codes.

These, however, generally refer to fillet type of socket welds normally involving one light wall member such as a small diameter pipe (usually 23" or smaller nominal outside diameter).

In

' these socket fillet-type of weld j oints, illustrated in

.)

Fig. 5, the pipe member may heat up more rapidly and thus expand to a somewhat greater extent than the adjacent heavier mass of base metal whenever hot gas or steam flows suddenly through the pipe.

Frequent temperature cycling may, in time, result in cracking across the fillet weld.

The susceptibility to cracking depends upon factors such as temperature shock, the number of temperature cycles, principally the heating cycles, the length of the leg be-low the fillet weld, the size of the fillet weld, the ma-terials, etc.

The socket type leg in the Dresser pressure relief valve design, shown at "B" in Fig. 4, depending upon ma-chining; may vary from nearly 0" to approximately 1/8".

's

-5 It will probably average 1/16".

Because of the mass of metal involving the flange and the cage, this section, even with a leg measuring 1/8" will not be subject to uneven heating or thermal fatigue.

This applies even if the valve is exposed to severe' temperature cycling.

The large metal mass, including the cage will equalize the metal temperatures in the flange and lower base sec-tions at the weld location.

The tight sealing at "C"

and the 1/16" average socket length at "B" thus will be of no significance.

Furthermore, this valve can be readily isolated by the isolation valves located between the pressure relief

)

valves and the ' pressurizer tanks.

Operation of the iso-lation valves was successfully tested in accordance with test procedure TP-230/10, " Test of Power Operator Relief Valve Isolation Valve".

The electromatic pressure relief valve was opened at operating pressure and temperature and the isolation valve closed.

The extensive experience with valve and component failures in fossil fuel, nuclear and chemical plants, also supports the conclusions that the specific weld joint design applicable to this Dresser valve in the operating conditions involved, should not result in failure.

e Th'e performance of this particular Dresser design has also been confirmed by the entirely satisfactory ser-vice of 99 valves machined from ASTM A182 forgings. These valves are operated in commercial plants at pressures as high as 2230 psi and temperatures as high as 1000 F.

In addition, 14 of these valves to date have been installed in nuclear power plants.

Even when a socket weld of a more conventional long socket leg design has failed because of tight " bottom" po-sitioning, the occasional failure encountered in fossil fuel power plants or chemical plants have almost always occurred as localized cracking over part of the joint cir-

}

cumference rather than involving a complete system.

The rare instances of failure generally involved a light wall pipe section welded into a heavy wall member.

These con-ditions would not apply to the Dresser valve design.

RADIOGRAPHIC EXAMINATION To verify that the " modified socket" was less than 1/8", the valve was radiographed by multiple exposures as detailed in the shooting sketch shown in Fig. 6 Prints of several of the exposures are shown in Figs.

7 to 10 They ',dicate that the socket leg is likely to be approximate 1;./16" and may even be less.

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CONCLUSIONS On the basis of the following criteria, the 2500 lb.

class Dress uonsolidated Electromatic Pressure Relief Valves Type 2 }-31533VX-30 (25)x2-XMYI-US126, as detailed on Dresser Drawing No. Cp-1549 and 418463 are considered acceptable:

(1)

The wall thicknesses shown in Appendix E and the evaluations included in Appendix E confirm complic.nce with the require-ments of Section III 1971 Edition of the ASME Boiler and Pressure Vessel Code.

(2)

The socket type weld joint with a socket leg length of less than 1/8" is not sub-ject to significant localized stress levels even under the most severe con-ditions of thermal cycling to which this valve might be subjected.

(3 )

A detailed metallographic examination of a mock-up section identical in size and design to the actual valves and welded under conditions identical to the proce-dures applicable to the original valves has confirmed that tha welds are not sub-ject to microfissuring.

The d joint

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design also does not provide

a. enhanced susceptibility for cracking at the toe of the socket.

(Report No. 1158).

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(4)

The valve, and weld assembly conditions, as detailed on Dresser Sketch No. 418463, have been verified by supplementary final radiography.

(5)

The accep'cability of the flange and lower body materials have been confirmed by Dresser who is responsible for the veri-fication of the supplier's mill test cer-tificates and ultrasonic and liquid pene-trant inspection reports.

(6)

The soundness of the weld assembled flanged body was further confirmed by Dresser by a

)

hydrostatic pressure test of the "shell" performed at a pressure of 9000 psig for 5 minutes, which involves more than three times the maximum working pressure.

(7)

Verification of these test results and com-pliance with the requirements of Section III of the ASME Boiler and Pressure Vessel Code was done by the Babcock and Wilcox Company.

(8)

Confirmation was provided by Dresser that weld failures have not occurred in the electromatic pressure relief valves of identical " modified socket" weld joint de-sign and tight seating.

These valves have 1

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T) been produced for over five years and operate in service environments con-sidered equivalent to, or more severe than the conditions applicable to the specific operations of the gaseous waste disposal piping systems of Units 1, 2 and 3 at the Oconee Nuclear Power Station.

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APPENDIX E STATEMENT BY DRESSER ON 9000 psig HYDROSTATIC TEST f

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APPENDIX E (1)

)

Statement by Mr. T. R. Bordelon of the Dresser In-dustrial Valve and Instrument Division on the effects of hydrostatic testing at 9000 psig.

"In analyzing hydrostatic test requirements, some confusion does exist with regards to what is the requirement of ASME Code Section III, 1968 Edition.

Since this valve body is mounted with a 2500 lb. inlet flange, the body should also be structurally equivalent.

This is the reason for establishing a 9000 psig hydrostatic test as defined by ANSI B16.5 for Type 316 stainless steel material.

"To further evaluate the problem, we find that when outlet loads, etc. are converted into some equivalent pressure, this equiva-lent pressure plus normal operating pres-sure do produce higher body stresses.

The increased hydrostatic test pressure does 3

produce a more realistic stress pattern 1

to account for these increased stresses.

"To further substantiate that the hydrostatic test does not produce excessive stress, an analysis " Bolted Flange and Neck Analysis" is provided on the following page which indi-cates that with a 9000 psig hydro, stresses are within allowable limits."

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APPENDIX E (2 )

LRESSER INbu37 nI AL UALVE T, INS TRU9E.':T DIVISION 90L1ED FLANUE AND ccCM ANALYSIS INPUT CATA

' 3 (2-1/2 31533Ux-30)

COLE =

10 5',4 5' 2 75' 7 75 3 1*25' 5'

5' A 8 dd C TH 60 G1

=

NB BA SA Sd = 3 S' 693* 35000 35000

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3 06' 0937' 3.'

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d Gd GM uY =

P EML.~. EM L.

EN DT ENDV =

• 9000 O.

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PRINTOUT 5 5440000E+00 AB =

P FD =

9 0000000E'03 1 1477042E'05 WM1

=

3 27915472+00 AMI

=

1 967160 9E*0 5 MD =

MT =

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1 1400 588E*05 M3 =

MO =

1 5805083E+05 1 3909107E'00 T

=

1 4500000E*00 Z

=

y=

2 4340994E+00 U=

2 57482835'00 E=

6 0594657E-01 0=

1 8234051E+00 L=

1 8816939E'Ol OPERATING CONDITIONS SH = 0 26970E*05

<.3 5 % = So,ooo # e too l:

SR = 0 67^49E'03 ST e 0 77792E'04 a.0513P18d'03

% 7.R =

1 1575377E-01 A ?.2 =

1 544052tE'05 4 =

3 6208021E+05 MO

=

GASKET SEATING CONDITION SH = 0 15394E+05 T)

SR = 0 1540 6E'04 ST = 0 17821h+05 9

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APPENDIX F o

0 CALCULATIONS PREPARED BY DRESSER ON ELECTROMATIC PRESSURE RELIEF VALVES o

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The stress analysis of 2 " 31533VX-30 valve body per NB-3647 i

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..follows.

The structural strength of the valve was found to

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be adequate.

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.H A structural 9eometrY of the valve main body is idealized as

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shown in Sheet 1.

Design parameters of stud, gasket, and

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valve body are given in Sheet 2.

Dynamic stress in valve wall

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(hub) due to disc motion is conputed in Sheet 3.

Stresses in (Q '[,6 flange and valve body at operating conditions under p r 1.0 ksi

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are calculated in Sheets 4 & 5.

Joint reactions at va'.ve top

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flange specified by B & W are given in Sheet 6.

Equivalent r :. y ',..... total pressure is computed in Sheet 7.

Stresses in the valve f

,' ' ' at operating conditions are calculated in Sheet 7.

Stresses

'due to gasket seating are given in Sheet 8.

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The maximum stress intensity in the valve is 22.00 ksi which

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' occurs in va~1ve wall at operating conditicn s.

The allowable M.:- M, '

limit ic 24.3 kai (= 1.SSm),

The dynamic stress in valve wall

'g' generated by disc closing action is negligible.

The stress

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intensities in base flange at both operating and gasket seating

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conditions are less than 11. kai which is well below the allow-able limit of 24.3 ksi.

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'An additional investigation was made on valve body by considering

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the wall as a cylindrical shell.

The calculations are given in T

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Sheets 9 & 10.

The maximum peak stress intensity is 15,10 ksi 6.

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which is even less than Sm (= 16.2 ksi).

Therefore, the valve i

wall satisfies all stress categories.

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The fatigue analysis was performed per NB-3222.4 (e) t>f the ASME 1

-I Code Section III.

The calculations are given in pages 11 and 12.

" Through conservative evaluat. ion, the cumulative fatigue usage factor is 0.287 which is well below tha allowable limit of upity.

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APPENDIX F (5) 1 OPE r'AT IM G coM DtTi otJ s.

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.. h,=. 4- (7.7s - s.5); $.,, ;. '

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...,. p. _..

,p...

i.

m

i $ 125 4,2 C.J = l. 375

.. _.:. 4....:.:-

i

~

..Ii i

.e

. I. !;.

,y

. g = o.7as (3.o6') - o.785;( 2 7s2)i :.

l g

. = 1. ss - c. g = j. 4 i K.......

.l

... j.-

'i.-

4 i :- 5 i MT: 3. 4 '2 ', - h'.

i i

j-h = 4..7 7s -_2 ( zci s + 3.o6)J T

i i.

4

),.;

=f (7 75 - 2.9os) = 2.422" j-i-

..t a,...._.

p. '..,q,,,.

...,,t,.*,,,

,, 8, H ::4 12.16 - 7.ss = s.4.t k. -

/,

M = 12.-[. -k 4

,,j h a = j (7.75 - 1.o 6) - 2.34S i

i 9

e-

'r

.H,=21.s p 3.4 2 412q = 3 s, o u: k-

,j O..

i i

s l.

DP,EZ'!!. P,,,3o-6 2 2 5 2 - o l

t' i

g;;{ 5/73 s

i N

l P W.I 9/'14 v nua

-l rca ocer. evo.

oV ANDAN>[ b C O Af3CC S m ais esa a

_TO C t" M A CKCD rrt A Ciso ps t s2ece.sre, TOOL NO.

2 t sC4 -

ECCePI AL5 ' * "' O ~.Ci?

t AescL a s 1 t

W.O.* NO.

_TO CC U :CD ON PART NO.

DWG NO.

-s

. j.i SKETCH e

Ij 9

(4) TJl AtJGE STRESSES' udDGR untT OAQltJc

~- a*. as* ic R.

APPENDIX F (6) 10 = A = t o. s

.......%.T = 154 I

g 4 g = 2. 5 4

..] 1 ~ _U.=_26 7 1,,

t

~

s

..:1 Y: 2 43 i

u

~ ~ M.. '~ s 1

~ ~f =.g.s5 ' : ' '

I l.

s

..r

$. = $, = o. 5 ',

t. -.

9 o9 1

F: 0.

q

v. = o. s s

.c

..c s.

J = \\.,

4 -]. ', ) g.,,,,.

l

?.y...,.

i D

9 do = /E4 : / 4.s(.s)': k 2. 25 = 1:

T~ ~ '

50

,o

.e =.noq s,

o.6o 6 15 E.

u

't-

... -g,

.. o.c

~ :

.g=~U j Ao 2.s = 7 67 (15)(.5').=.I. 8 2.

,ec -

..f.

~

'E

e:-

L = t'e + 1

~

+ t* :3125(/6o6)41" i 12. s 2

-T d

-+

1.33

t.e 2.

= 2.o 2 ' ( 4.? = I E, F?

7

..h..._ '.

.t.

. s Mo

PS T

38 ~...,.

f g' e -

h..s' gg 4.5

- +.

=-

r

-Q L,20 B, 4p 4-

. I.n,

l

.t

. 8,9 8 (.s')(4.5)

4. (.s)

I'.2 L 2.

3 t

J. Lq -t_2.2 5_= a;o 4' t

i

'!.lI. -

f

-.1-3

.kst

4. -..i S g' = -( i. 3 3 t e + t ) H. --_.= T. 3 3 0 12 5 5.. ~(. 6 o 69 t '

Lt*B g'g-3co.(ggg 13,E9 (3.125*) d. 5

.t'-.

s.

tso l9

= o. \\ (;>2 kst 3

1:

.l*..;. -

.... ~..

VM S

- 2 Se, = w.43 ( 3 8 5 2

Tn.

.p -

t-e2 s,' (4..s.)

1.4 5 (.16 2) = 2.t o. 2 55-

'O t '

= L Eb.5 Vst 1..

Y..: . *l2

.l.

i;.

.p,

.. 2 -

J t

t dress ER ' E,o-6n 5 2 - o I.

4r!4 Rh3 j

a nna p,.., i o /- o

APPROM3L.) [DY l

• a ij67. No.

veseen casosass e -* sci eas TOOL NO Fft ACT t3 N S t#Se TO GE M' RKED CECINALS

~.007 A

ANGLES

?! i W.C" IMO."*

TD CC UtCD ON PArtT P10.

uwG. NO.

S A

V,-

SKETCH a

i.

,/

4*

i 9'.. :

.s..

APPENDIX F (7)

.t.-

....i.....,.._i 4......

- Jo 1.1 i RE/ CTio rd s AT VA LVE..FL A tM E

.i- ! *:....

... q..

v.-

a

t...:

. D mm

~Dl b( )R

. k d{

I.'j O '_'6 ghL t.

gl g

e a:.

)v g

e.:it

..t...

4 x

..q

, - - -mh r Fs i

q.

A s..Q._f p

V' y.

V, t

!,m

".i..

c.

I F/..

l ir

(

v__. /

j*

.(

).

'.. ~

1 s

i u

.i. v..

g.

.~

2.

i us.

,,..g

.n

.,y

.s

.......,3,.....

.4..

v.. ' :....,. :...;:..;......l,..

i.

., _.,....,.....i...

M

c..

....t_

M = 't o o o ET-4..

c.!a.E f

.e N, : /

1;, gt.

8

.c

.t M.4=

5'oo FT-#

. ". -,7 34., =, l o o FT-s

(. ' C '

I

..s.

.i..

.u..

a..

.:...... Fx a....

.. l o.o

'r

.i-r

.l f

1

.Fg = 150 t i

..,. p.. i -

p2= 1754

.r

.a...

.i....

...a 4

.s e.

....t

..u

.I y

s,

-r-2

.\\.

s

\\

e,

\\

.t n

I i

s 974. P/73

. Dr! ESSE.% ~6o - 6 2 :5 2'- o~

g.

s:

lg W MWH

j eca grs.f. No.

i LW AN$A,f D TOL CCADeCF S

'estess ms ' a s>te:rus TOOL.NO.

yo cc unno<co r'tA C f f 0N a 1 %f34 j

GCCIMP..S auam

- t.L'v ?

- O 1s w.o. no.

To cc usco on wany no.

DWG. NO.

d

'e SKETCH i

= = = =. assE lco'.isu:.w.Tivat.( c.ese, ige tpx 4 g2 I

j APPENDlX F (8)

Auge g 4 p 2

q M = M,.

.4 r.4 3 = 1 ooo + t o o = 1 i o o. p-*

= t\\ L 2.

I,.-e.

i F,"= F x + F 2 = z 25

• t o;o = 3 2 5 'M =. 3 25 k. i

.t.

H =.5co it-4 =.G,. L - h g

L,

- c o ;i

,4

.j_...

D a",i u Pg = 150, =.15 K __

s a

7 i

3

. )

1:

Tf:

i.

AdSFoP.M THE REA<.TioMS FROM TOP Ft A' 3

.. M = 1 B. 2. + 355 M.0 5) =' 16.14 * - k.

t E

ty F =, 1 5 k.

.._... i f.-

...l..

3

. y'f, g g gi

]:)

t~.{

..=g g +4e =r406 0

..4 (. t s3 1

i

• 1L' ( 3.00 J -r

,, s-

"' P.

w /' "

"li (', '

.u

=

2,2(, 4. o.2 = 2. 2 8 ksi

, $ g-in t.3.e t,

/

l

. q., ;

...i 3

2 P = 2. s - 2.s s = s. 3 s ysi. ;.

9 m.

p

.o

,._._.z... g..,. _.......

~ '. i-W'iEM'. STRESS 14 HUB DUE To' My = 6 g

I Y.

.,:' - k

.g,#, % Q

. -..,.l j '

..

P h.

7.,. ; -

. y

~'

... _ i 2

' 'T ' ' '

' ~, 4 (5;S 4 4. 241 ) ~~~~~ '*$.Y ~ ~" '

r.

4

'j.

.e i

,4.,Y.(L. 9 - d.24'M ~

2 3 '2., = c. 2 5 2 ksi

~

.r 2 ( 2.*)

~

e

' ). ;.. ' :. 1. '.

s..

i. :

r SIR.E"-SES Ut4 DER des 1G4 OPERATiedC=

C.odetT t on l'5 Sg = 4 A4 (s,33) + o. 25 2 = 2.'2. 0 0 2 tu Se = :o. ) 6"2. C.S.53) = 0412 kst (con s= mTive)

F S.= l,7/,9(5. 3% ) = 10..O 2. kSt T

~

s 0

1 I

i t.

DP. ESSER 3o-62252-0 s.

I

' o wns Mf_ B/13

a v DECCRIPTION.

DATE STANDARD TCL NCCS

., APEROVEO HY

, 02 GCPT.NO.

Utttts

$ese$wett

• BC f tt9 TOOL NO.

F*f1 ACTIONS 2 1#$4 DCCt9ALS

. 1 Jio?

T3 DE MARKEO ANOLCs 2t' W.O. NO...

. TO CE USEO ON PArtT NO.

DWG NO.

O, s

SKETCH a

' * ~ * * * " " '

.c J

. O AskG.T SE AT ttM

' " ^ ", ? 'I APPENDIX F (9) },

~~

~-

g l

4-j, W% = 7r bG "f = IT (. oWI ) ( 3,o 6) (,4. 5 ) = 4'. oS k

.s.

A m = s..O 5 = o,tsa..

1..

a 2(>. 3

.. I,...

- i: -..

A i = 12.7 4 (2.5) = g,2 i,. s 7b D IP T' D

@@U)Y917@

1

3..

~'

jl([. U d j )) j p', N,

j.....

q..

W

_1. 2 1 + S. M'. ( 2 6.'3 ) = 8 8. 7 k 2

...-.. t.,

i t

.bA

= 9 8. ~7 ( 7. ~75 - 3. o 6 )- =. 2. o S. - K'..i l

~

g

.y-t

'"..4 6:

.f W 2o 8 = q,8 o.ksi

.e f.

% = L j,'- B i

=

21,22

.... _.. l

,.;, i '

~.,

t..

i 2.:.

a s e ->

c: _. - -

< 2. O x..i = n. 9. v.

2 x.u,

-y

.i i.

j..

S3 = 2*43 MO - 1 M(,883N 11[5 -b3 -MU %

4. a..

u.: t.....

-:.;.s.........::.

. g.*.

/.s._:.

s

.i..s.

.t.

y.

s.

u.

3..

.c a,,.,

..+.:

~.,

.-...... -...f..,..-..... n,

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5..

, g.

n

. i......;,

3...

.p

.... e

,..r... ;.

7 i

.:.....,.n.

s.

• g.

.

.... y.,

,.,-;. 4.

. :.L..

s. gs

.]

s u

.t

.>..-e..

4 :., i.

a..

l 5

4.

..... i

..g g

I..s i

...._.....1,..-

.3..

.p _

e 3

..I r-

.. s D.

w T*

'..'.'i'

' DRELSER so-622 'Es2 -o M t_

8/'7 '.,

n

(*)OW dP APPROVED nY rea Ccet, wa.

CT AHRAftD *

g, C 8t A t* C.r 3 wasess st.:

tssce ore T.') DC M A f*x CD T ft ACTIC N S TOOL NO.

2 8/94 S E C48.t AL.3

. 2.077 AH at.t2 73 DC (fSCD ON 21" W.O. NO.

PART NO.

/

' DWG, NO.

SKETCH

.i l

j

=='a*~a

-ADettTioMAL CordStDERAT. ierJ :.+ -

i 7-APPENDIX l' (10)

_t J_..

VALVE VJALL WAS TREA~[ED As_'A hYt.itdoRic t

'1 SUBJECTED To THE LOAbihlG Co!JSERVATIVE l,

, Fottov)3. :

S i

.:...c.. ;~. I "

.t.-..

..... s..

.-i.

= 2 soo psi 3

M = ( 6.1 4 L.- k }9

. ;.._ _... p...

j.

I

....____'.r' I-d.

-- Q '4 F=.15 k ssE "T' I i

M=6.

~k g

r s /~'

/

.. J.q jC[

..3..-

9~

1

. A = 4 ( s.s'-4.5,7 = 9 2 5' L '.'..

i

,.1.

4 4-c.

j 3=1r.2 5 ~4*.9

.. w 14, go g y.

'i.

2.

g

.g ',

I=.f2. = '2 s4. 9 e.

4

...., g _ y.

=...

.... 2..,#..

.~r

.{

~-

u

.......s.: _ -.. 4. '.:.:<.a.... : '..it.

+.u

?.

.. e..

+

>..' i t

t>ue To p = 2 soo Psi.AT IM 5tDE SUR1: ACE

1. ' N :::.

0'e = 5. c S'

. S.S *- 4. S '

i'2. 6 es1

'(T2.11G=oTmt) a.:.....

2.'

s

^::

8

..i

,. <.3 C :

t.

a.

.M 3.

3.A,5 4-

,.:.~y-2

'),5 H

.. 6' _..=_.

546 ksi, ". !( LousrTuot w.L')-

t P, t

.i i

7, g g t_

3

.Q~r = - 2. 50

.... m,...., ;.

J--

w c-g, ks i -----( RADI AL.-) J ' --

2

.. ;,,. K.,.. ;..s

((.

._D O E

, y...,... y..... !

~[o.M =. l.6.14 * - k ' AT ouTSinE ; SURFACE 11

~

'.Q = Mc = -(6.i d.o (s.5V2 ) =

1. *l $ ks 1

~

,5.:

I

.. 24. 8

.n 1,.-

DO E To M o : 6. ~

, k

'A. T. OUT.51DE. SuRFAC E e

> p

. Te6 = 6, (5.5/2 ) =:

b.333 hst. ;

\\

n. -

A c{. (o

.s F!,

M f

D Hn

$ n n D

v l

.bJ11d"S j

i DRELSER, ~60- 6 2252-o ~

i FE, t._

2/"73 h

4

n. M

DTArd CA*.D T OLf M ANCC O fC.PPROVED OY

--c ocer, us, vsm e mes..si '.:s o*"

• T O O L. N D.

rn AC7 eons t rea p

DECIM ALD

= 447 T:') C E M A RX E D p,4ctgg 9.

W,o

,,o, TO CE USED ON PART NO.

r*

• G. N O.

lO kKETCH -

• ** a *' u n

.i

. 1 APPENDIX F (11)

. 4:..I 1.*

i

(

'puE To F = o. I s g AT SoTN! IWstoe. t'ouTsics 'sucu:

Aces p

o as i

.c.

.0%.

=.h

='1.25 r o. ot q 1..a st a _L._,

..i.

i

. s,

.t,..,..

u. _.. +., 1

, u..,. t

• l 7

.{

sy case.e.VATio% Tite MAXIt/.UK SKl4 STRESS INTEds!TY T.

oCCURED AT IN 51DE sOR. FACE CP.4AGt4tTucE.

f.~

i

$ = [m E + 2.s = 15..I a ksc ;..

4-4

.r

..,....t...........g w.

., ~

......,.,. ~......:.,..,.

...i.

t

. f

,t o 9-,,

76 R pr.,1:

, f.-l g

.:. ; f 5

,q

)

Md 1 5] f j

o 4.

...:..,. i.

z

........ =.......

.u..

.......i..-..s,.....

. ] ;.

j.

i

)

. r...

...s.. s.

. a..,

,..,[

g i..

j. '

r'.' 'l,:c.r.-

'; [.,5,c, q.;.,

4-

.i

.r.......,.:.4 :}..,..... :..'*. :,._.

i.....

9, 1

.,u s

. i.

.e...........t..

t.

.t.

.s

.4 t

.a

.v y

s

{.

s,s g.

.. }. _

.u

..,..,i.

. s...

..r

, s..

r

...m

. i..

.t..

.. ~.w.....;...'

r..

- }

f.

e s

c i

. -8

.o.

....... \\

~

DRESSER,30-62252-o frft W to mm w n n ' --

,, DCSCRtWlON g

DA,Tg ______N 17 l{l.[2Qf _____

.y am r c m ' c = - --,.

GT AN D AC,D 'TO'.

4CC5 s

l

?A,.APPHOVrOt1Y

~ /l r A crer een, m ais e.se ist sc r,se 7001 NO.

FR A CT13,4 s 2 1,34 c eceMr.a.9 2 427 re4otts 21 W.O. N O.

6 t

-..' _TO DE M A RK CO PARTr40 DWG. NO.

l!

• TO DE USCO ON

' = * * *i" = i SKETCH

-l

.....:_.... q.i

. < u..

a i

..e

.... a,

....i...

+.....!

. '. 2-U!

~ !THE VALVE IS SUGd E'CT.ED T:o'~iVJ6"CYCD C. LA AD IidGS : '

~

. c.

. k :.?...1..

.... _v.

...e.

.; p..: i c

..Q. N.

i. 40 STAtTUP - SHUT,Dowd cycts (2,0 cyctEQ e

.. _.. _ PRE ssu RE. :.. Q

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J:........_

y

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t.

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ad,_

a.

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...OF. REACT lords, SHo@d od

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O

.,4.o.

o

.:M.

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p

. v...,.

~._..,

a. :... _. 3.,,... ;.

. n :. n. c.y.r...

c.,

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~

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n. _..

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s. _,., e..... : u

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-e. n p(# ;f..;

', AueLiTODEs oF Peak Stress tuTeM'stTy ci: poo cycLtc LOADS EVALUATE 6 AS PoLLoW5, E^

-!.i-P 1,.." - [ ARE. CotJ5ERVATNEL.

s

.n..

... w...,

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,...o.

.., i

i

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m,_..,..

iir,sJ.p.i..._.e_... %) i

• 2 2. c o 2.(. 4...J. o ); =.. 9. 8.,.c o.8 ks i

.F...R. _. r _:c,e_ _

=

.... ;. n.. ;,... g F.

...1

. ;. 2.

~2..

7-g.. my e.. :

s4: = 2 2, o.o 2 -(2.5-2.185) + o. 6 6.M f (4.0) = n,m g3i

- r

.s.. a..

....:. s. 25 3 8;...t.

J

a.,.......; m.

m,.r.s.

w.

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1.....,........

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~

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g...:....,..,..n. c.:.w... <.o. _ _g.. ;..g.

g

p.;.g..........-.....

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m.

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o

. v, "THE VALVE is SOBdec. Eb :To ~24.o.cYc'es o#- (b)i 'AMD To

~

T

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3o,oc o C.ycLE$ o f..dS'o.)-i." PER.'. PAT ( c,0 E. c.O RV E Fm L-F2.,

h:

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. TH.E ALLouJ AB LE 14 OM BEqs oF cy cLE ARE T

.-e t...y.........

u.

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m.: i

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a. 7..q, =

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> p s.=. z o c o.-e y : u s s

..,.i :. +.n,:.:.

._.%. :- n 4_;.

.. m s.----.

.w,M..y : +......w.;.

.... -: _..... :,.........-...n,

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~

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p. p;..

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'3

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s

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p

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o

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.to

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