nasa technical nasa tm memorandum copy no
TRANSCRIPT
NASA TECHNICAL NASA TM X-71933
MEMORANDUM COPY NO.
. M74-20568
( NA S T-X-71 9 3 3 ) IZTEGRb FLAFGE DESIG5
SPROGRAM (NASA) 32 P HC 75 UclaSC 20 UnclasG3/ 3 2 34356.
2z INTEGRAL FLANGE DESIGN PROGRAM
By
John F. Wilson
March 1974
This informal documentation medium is used to provide accelerated or
special release of technical information to selected users. The contents
may not meet NASA formal editing and publication standards, may be re-
vised, or may be incorporated in another publication.
NATIONAL AERONAUTICS AND SPACE ADMINISTRATION
LANGLEY RESEARCH CENTER, HAMPTON, VIRGINIA 23665
1. Report No. 2. Government Accession No. 3. Recipient's Catalog No.
NASA TM X- 719334. Title and Subtitle 5. Report D te
Mlarch 19746. Performing Organizatioo Code
Integral Flange Design Program
7. Author(s) 8. Performing Organization Report No.
John F. Wilson 10. Work Unit No.
9. Performing Organization Name and Address
National Aeronautics and Space Administration 11. Contract or Grant No.
Langley Research CenterHampton, Virginia 23665 13. Type of Report and Period Covered
12. Sponsoring Agency Name and Address Technical Memorandum X
National Aeronautics and Space Administration 14. Sponsoring Agency Code
Washington, DC 20546
15. Supplementary Notes
Programmed for Use on Hewlett-Packard 9810A Calculator
16. Abstract
This paper describes an automated "interactive" flange design program utilizingan electronic desk top calculator. The design equations are from the ASMEBoiler and Pressure Vessel Code, Section VIII. The program calculates the
operating and seating stresses for circular flanges of the integral or optional
type subjected to internal pressure. The required input information isdocumented. The program provides an automated procedure for computing stresses
in selected flange geometries for comparison to the allowable code values.
17. Key Words (Suggested by Author(s)) (STAR category underlined) 18. Distribution Statement
flange designpressure vesselautomated design (interactive)stress analysisHP 9810A Calculator Unclassified - Unlimited
19. Security Classif. (of this report) 20. Security Classif. (of this page) 21. No. of Paes 22. Price*
Uncl assified Unclassified 3 $ ,7S-The National Technical Information Service, Springfield, Virginia 22151SAvailable fromSTIF/NASA Scientific and Technical Information Facility, P.O. Box 33, College Park, MD 20740
I
INTEGRAL FLANGE DESIGN PROGRAM
By
John F. Wilson
NASA
LANGLEY RESEARCH CENTER
HAMPTON, VIRGINIA
SUMMARY
The flange design methods in this program are applicable to circularflanges under internal pressure. The gaskets must be entirely withinthe bolt circle and the outer rims of the flanges must not touch underthe applied loading. This paper presents an automated design solutionto integral and optional type flanges using the methods in the 1971edition of the ASME Boiler and Pressure Vessel Code, Section VIII,Division I, Appendix II, pages 210-221 (reference 1).
The program calculates the stresses associated with a given geometryand prints the required flange thickness to assure that the workingstresses are within the allowed code values. It is the responsibilityof the designer to be sure the geometry conforms to code requirementssuch as maximum hub taper, maximum bolt spacing, number of bolts andsize of bolts, as well as allowable materials and material properties.
The program was written for use with the Hewlett-Packard Model 9810ACalculator and programmed using their operating manuals (reference 2).
2EQUIPMENT NEEDED TOTAL TOTAL
E PRINTER REGISTERS PROGRAM STEPS ROM'
O 9860A MARKED CARD READER 51 5 00 1 Mathematics
O 9861ATYPEWRITER O 111 5 1012 2 Printer ALPHA
O 9862APLOTTER 2036 3
DISPLAYSTEP USER INSTRUCTION x Z z
Before using calculator T
1 I Determine a flange material (ASME Code)
Z I Determine a bolting material (ASME Code)
3 Determine a flange Geometry (See P age_3 )
4 Determine Gasket Details (See Page 4 & 5 ..
1.5 -Determine Flange Facing Details (See page 6 )5a Determine Design Pressure and Temperature
Now go to Calculator
6 Press: End
7 Press: Load (Load Program)
8 Press: Clear
9 Press: End
10 Press: Continue
Using symbols and definitions (pages 7, 8, 9, 10) Input
information to calculator as requested.When no error
messages appear (See sample program output pages 12
& 13 ) design stress and flange thickness requirements
have been satisfied. Designer may still select a flangethickness to iterate to closest acceptable thickness
giving no error messages.
3
INTEGRAL FLANGE GEOMETRY
GO=
L= R = - G1 B1 =R= I -
ITK
C;1/16
NO. BOLTS
NOM. BOLT DIA =
4
PRESSURE VESSEL CONSTRUCTION
FACINGS AND GASKETS
(Reference 3)
Suggestions as to the choice of facing and type of gasket to suitparticular applications and service conditions are not covered in thisManual. Pressure, temperature, thermal shock, cyclic operation and thefluid handled are all factors to be considered. All sections of theAmerican National Standard Code for Pressure Piping (ANSI B31) containrules for flange facings and gaskets and these serve as valuable guides.Reference should also be made to American National Standard ANSI B16.5,covering "Steel Pipe Flanges and Flanged Fittings". This Standard pro-vides facing dimensions for flanges in the 150 lb. through 2500 lb.classes in sizes through 24" and also refers to gasketing. Similardata for sizes 12" through 36" in classes 150, 300, 400, 600 and 900 lb.is given in the Manufacturers Standardization Society's Standard PracticeMSS SP-44.
Flange facings may be classified as (1) those sealed by pressureon the gasket from bolt loading and (2) those sealed by self equalizinggaskets that function by internal fluid pressure. The first groupincludes raised and flat faces where the gasket is restrained only byloading. The gasket is confined in a recess when Male and Female,Tongue and Groove, and Ring Joint are used. Such facings providegreater unit pressure and offer more protection against blow-out.
Raised Face Gaskets for raised faces may extend to the inneredge of the bolt holes for centering control. The O.D. of the raisedface may extend to the same point at the option of the designer, butbecause of machining tolerances, it is advisable to keep it smaller.The gasket O.D. for design purposes is equal to the O.D. of the raisedface. Spiral Wound gaskets work best when the O.D. of the gasket isslightly smaller than the O.D. of the raised face. They should beprovided with a compression and centering guide to insure proper loca-tion.
The gasket need not cover the entire width of the raised face asthis requires additional bolt load. For certain corrosive services,locating the gasket 1/8" from the flange I.D. helps protect the flangeface.
Male and Female In this type of joint the O.D. of the gasketis the same as that of the male face. The femalefacing is madelarger than the male face to receive the gasket and provide interlock.
5
Tongue and Groove For this type of facing the width of thegasket is made equal to the width of the tongue, which, for clearancepurposes, is narrower than the groove. The joint proportions areshown in Figure Ic, page 6. The detail shows a "nubbin". This isused to reduce the effective seating width of the gasket.
Ring Joint Suggested minimum edge distances are shown in Figure 1 g.For reasons of economy and sound design, it is recommended that groovesfor ring type joints conform with ANSI or MSS Standards whenever possible.ANSI B16.5 and B16.20 cover sizes through 24" and MSS SP-44 covers sizes26" through 36". In larger sizes the configuration and proportions ofthe groove should follow those established by these Standards.
It should be noted that neither Standard refers to rounded-bottomgrooves. Unless otherwise specified, flat bottom grooves should be- pro-vided. While either oval or octagonal rings may be used with flat bottomgrooves, the octagonal type is preferred.
Self Equalizing Types The self equalizing type of gasket, such asO-Ring, Delta-Ring and Lens-Type, are useful for high pressure applications.These gaskets and the special flange facings required for them are shownin Figure 1 e, page 6. Joints of this kind have the distinct advantage ofnot requiring mechanical loading for gasket seating. Since the gasketreaction can be considered negligible, the total bolting is only thatnecessary to retain the hydrostatic end force.
A great deal of research and experimental work has been done inconnection with joints of this type. No attempt is made here to coverthe subject in detail. Where metal O-Rings are required, they shouldhave a plating of soft metal (copper, for example) and be used with16 AA maximum surface finishes.
6
*TYPICAL FLANGE FACINGS-Fig. 1(Reference 3)
a. FACING DETAILSRaised Face e. Self
Equalizing Relief
O-Ring
Groove -TER Wb. Smooth FinishMAle AndFemale
Groove- T.FRWCold Water Finish
Elastomer Metallic
Delta Ring D
C.Tongue AndGroove
Lens Type Sphercl Radlus
n a Bevel... old WaterFinish
d. f 9.Lap Joint Tongue And Ring Joint
Groove
I.D. LA
With Seatingange Design", Bulletin 741
*From T. ylor Forge "Modern Flange Design", Bulletin 741
INTEGRAL FLANGE DESIGN
NOTATION SYMBOLS AND DEFINITIONS
ALL SYMBOLS ARE SHOWN IN THE ORDER THEY APPEAR IN THE PROGRAM
The definitions are those given in Appendix II of the 1971 ASME Boiler andPressure Vessel Code, Section VIII, Division I.
B = Effective gasket or joint contact- WM2 = Minimum required bolt loadsurface seating width, inches. for gasket seating, pounds,
EB1TGYB=bo, when bo : inch
P = Design pressure, pounds perB=_I , when bo>-k inch square inch.
2HP = Total-joint-contact surface
bo=basic gasket seating width, compression load, pounds,inches, see Table UA-49.2, -27TBGMPpage 14.
Y = Gasket or joint-contact-surface H = Total hydros atic end force,seating load, pounds per square pounds,TG P.inch, Table UA-49.1, page 15.
M = Gasket factor, Table UA-49.1 WMl = Required bolt load forpage 15. operating conditions, pounds,
EHP+H
G = Diameter at location of gasket SA = Allowable bolt stress atload reaction. atmospheric temperature,
pounds per square inch. Selectwhen bQ ' 1/4 inches, G = from ASME Code for requiredmean diameter of gasket material.contact face, inches.
SB = Allowable bolt stress at designwhen bo: 1/4 inches, G = temperature, pounds per squareoutside diameter of gasket inch. Select from ASME Codecontact face less 28, inches. for required materials.
AM = Total required cross-sectionalarea of bolts taken as thegreater of AM1 or AM2, squareinches,
8
AMI = Total cross-sectional area HG = Gasket Load (difference between
of bolts at toot of thread flange design bolt load and
or section of least diameter total hydrostatic end force),under stress required for the pounds, = W-H 3Hpoperating conditions, squareinches, =(WlMl) HT = Difference between total hydro-
(ST) static end force and the hydro-static end force on area inside
AM2 = Total cross-sectional area of flange, pounds, MH-HD
bolts at root of thread or HGG = Possible gasket seating load duesection of least diameter to bolting, pounds, see UA-49,under stress required for paragraph (b) item (3), sub itemgasket seating, square (d), formula (4), sub iteminches, =(UM2)
-(SA ) R = Radial distance from bolt circle
to point of intersection of hubAB = Actual total cross-sectional and back of flange, inches, (in-area of bolts at root of tegral and hubbed flanges).
thread or section of leastdiameter under stress, square Gl = Thickness of hub at back of flange,inches. (Must be equal to inches.or greater than AM).
W = Flange design bolt load for C = Bolt-circle diameter, inches.
the operating conditions or HD1 = Radial distance from the boltgasket seating, as may apply, circle to the circle on which HDpounds, E.5(AM+AB)(SA) acts, inches, = R+.5(GI).
N(Min) = Minimum width, in inches, HG1 = Radial distance from gasket loadrequired for the basic gasket reaction to the bolt circle,seating width, based upon inches,=C-Gthe possible contact width of --the gasket. Has no meaningif Y=0,=(AB)(SA)/2Y7TG. HT1 = Radial distance from the bolt
circle on which HT acts, inchesB1 = Inside diameter of flange, r.5(R+(G1)+HG)
inches. When Bl is lessthan 20 Gl, it will be op- HGIG = Radial distance from gasket loadtional for the designer to reaction to the bolt circle,substitute BB for B1 in the inches,-C-Gformula for longitudinal hub 2stress, SH.
MD = Component of moment due toBB = B1+G0 for integral-type HD, inch-pounds,--(HD)(HD1)flanges when FC is equal to
or greater than 1. MG = Component of moment due toHG, inch-pounds, _(HG)(HG1)
HD Hydrostatic end force on areainside of flange, pounds, MT = Component of moment due to-7 B2p. HT, inch-pounds, _(HT)(HT1)
9
MO = Total moment acting upon the E = Factor for integral-typeflange for the operating flanges, =Fconditions, inch-pounds, (RU)-MD+MG+MT
D = Factor for integral- ypeMOG = Total moment acting upon flanges,-U (HO) (GO)
the flange for the gasket Vseating, inch-pounds, (HGG)(HGl) TK = Flange thickness, inches,
assumed value.A = Outside dia mter of flange or,
where slotted holes extend to ALF = Stress formula factor,the outside of the flange, the -(TK)(E)+1.diameter to the bottom of theslots, inches. BTA = Stress formula factor,
M (4/3)(TK)E+1.
K = Ratio of outside diameter offlange to inside diameter of GMA = Stress formula factor,flange, = A . =ALF (T).
DEL = Stress formula factor,T = Factor involving K, shape con- -(TK)/D.
stant. LMA = Stress formula factor,U = Factor involving K, shape con- -GMA+DEL.
stant.MM = MO
Z = Factor involving K, shape con- Bstant
MMG = MOGYS = Factor involving K, shape con- BT
stantBS = Bolt spacing, inches
GO = Thickness of hub at small end,inches SH = Calculated longitudinal stress
in hub, pounds per square inch,Gl/GO = Shape constant. (operating conditions),
--(FC)(MM)/(LMA)(G1) .HO = Factor = V(B1)(GO) , inches.
SR = Calculated radial stress inL = Hub length, inches flange, pounds per square inch,
(operating conditionsl,H/HO = Shape Constant. =(BTA)(MM)/(LMA)(TK) .
F = Factor for integral-type ST = Calculated tangential stressflanges, figure UA-51.2, in flange, pounds per squarepage 16. inch (operating onditions),
MM)(Y)/(TK)2d - Z(SR)V = Factor for integral-type
flanges, figure UA-51.3, SC = Combined stress greater ofpage 16 .5(SH+SR) or .5(SH+ST)
FC =:Hub stress-correction factor(for integral-type flanges).For values below limit of chartuse FC = 1. Figure UA-51.6,page 17.
SFO = Allowable design stress formaterial of flange, nozzleneck vessel or pipe wall, atdesign temperature (operatingconditions), pounds per squareinch. Select from ASME Codefor required material.
SHG = Calculated longitudinal stressin hub, pounds per squareinch, (gasket seating con-dition), =(FC) (MiG)/(LA)(G1)2.
SRG = Calculated radial stress inflange, pounds per squareinch, (gasket seating conditions),= (BTA)(MMG)(LMA)/(TK)2.
STG = Calculated tangential stress inflange, pounds per square inch,(gasket seating conditions),
=[(MG)(Y)/(TK) 2] - Z(SR).
SCG = Combined stress greater of.5,(SHG+SRG) or .5(SHG+STG).
SFA = Allowable design stress formaterial of flange, nozzleneck vessel or pipe wall, atatmospheric temperature(gasket seating), poundsper square inch. Select fromASME Code for required material.
11PROGRAM WELD PROGRAM PROGRAM
NECK FLANGE DESIGN
ROM'S ROM'S ROM'S
MATH PAC
PRINTER ALPHA FOPTIONS OPTIONS OPTIONS
EQUIPMENT 981 O0A H.P. EQUIPMENT EQUIPMENT
Calculator
SERIES
thpll HEWLETT-PACKARD CALCULATOR
PART NO. 9230-0052
U EK.DIG H NECK
P F: G R ! O U TP UTFIND HUB :-;TRESS
SDESIG O F '= CORRECTI FACTRF:IE LDING HC i CK 750
S1. 1250i 1, 600
H I-
I.1.556
1.975 ,M= 0 .0 HIl= 1.5560 SUME
. H T 1 =G. 2 I2.0280 ALF=
33. : 8880 *H G = 1. .1950.t , tiM 2 = 0 i 5 5 6 0 B T = 1 . 2
S205 01.6 04 623291.9825 0 260
bM- IiMG=8 6 0
HTM. 79F 9F. 1 2.. 2 3 .8S!- K-1-1:" .A,
..L... 1.2227 1 . .i
P-N4 ._ _, .16 , 2 EL= F r
BOLT1'-T RESS B9T M
2162 PEERAIN 1:2TRES!7 .S
T=
4E1NEM 0Ii* .
RO= AREA H BLLTS= 9 .
22.04007 " .2 '39 796F O .
W HO = . .. 68 20 . 179:3
M6= n14904 O.4.000-
21 5 5054 1C21.8528
R-LT ! 32 LT. = 3' 7 V% 000,.000%3 7 8.3 6 F- .,
2 2 . 0 4 0I ., g S. .T =
G= H.O0 H GR:. 1"
N TK
436624.9147 -._ 40 l*I
- -59 5, 4:3
H--
: 219 .t82; =NTE L YL-; = ..4 9. -P O-, .. .C," ," .3 .
RO4T AREA BLT.= :?, 007 267
HB- 49i~F-
436 241: ., .9 i 47 4. E .;C
H =.: .. .
13
F:I R G Si::ET S T [t' , l OLT 1I ; =
a , B .. - i.. ;4
!. - 4 0 :i
4.-; T 3.. ...... . p.- F'. i I F A l
.Y. I ,. ' 'C" I
SF.-FI II
'ti.......... 49Ee 1--, . .- 41:
BE A
: :; I i- 1. 4 "i. : . i .
HLi-S. a 19 , 1 415i . 592200
I.520 0 ......
S 212:30.865 NEW r
DESi SA SRTiS-
FRCTDR
14
Table UA-49.2 SECTION VIII - DIVISION I PRESSURE VESSELS (Reference 1)
TABLE UA-49.2 EFFECTIVE GASKET WIDTH
FA(IG(, SKETCl BASIC GASKET SEATING WIDTII, bo
Exagg(rated COLUMN I COLUMN 11
NN N
1b* 4ZA 2 2
Id* 2 ; 4 max -2 4L max,
2 v + T ( w +-N---< N w + N w + 3N
1/64" Nubbin , . , 2 4 8
<3 - N N 3N1/64" Nubbin 2 4 8-2 4 8
43N 7N8 16
5*_--- N 3N
S4 8
6 8u
EFFECTIVE GASKET SEATING WIDTH,"b"
b = bo, when b. 5I in.
b = , when b. > , in.
LOCATION OF GASKET LOAD REACTION
G1-----h(' 2 G-- .hG " NOTE: The gasketO.D. Contact factors listed onlyFace-- Gasket ' apply to flanged
Face joints in which thegasket is containedentirely within theinner edges of thebolt holes
Forb, in. For bo < / it..
*Where serrations do not exceen 1/64 in. deptn and 1/32 in. width spacing, sketches lb and Idshall be used.
15
MANDATORY APPENDICES (Reference 1) Table UA-49.1
TABLE UA-49.1GASKET MATERIALS AND CONTACT FACINGS
Gasket Factors (m) for Operating Conditions and Minimum Design Seating Stress (y)NOTE: This table gives a list of many commonly used gasket mat'rials and contact facings with Refer to Table
suggested design values of m and y that have generally proved satisfactory in actual service whenusing effective gasket seating width b given in Table UA-49.2. The design values and other details UA-49.2given in this table are suggested only and are not mandatory.
MinGasket design Sketches Use Use
Gasket material factor seating and facingm stress notes sketch column
Y
Self-Energizing Types 0O Rings, Metallic, Elastomer other gasket typesconsidered as self-sealing
Elastomers without fabric or a high percentage ofasbestos fiber:Below 75 Shore Durometer 0.50 075 or higher Shore Durometer 1.00 200
,/ thick 2.00 1600Asbestos with a suitablebinde: io. thick 2.75 3700
the operating conditions /4 thick 3.50 6500
Elastomers with cotton fabric insertion 1.25 400 1(a,b, c,d)4,5
3-ply 2.25 2200
Elastomers with asbestos fabric inser-tion, with or without wire reinforce- 2-ply 2.50 2900ment
I-ply 2.75 3700
Vegetable fiber 1.75 1100
Carbon 2.50 2900Spiral-wouad metal, asbestos file. Stainless or 3.00 4500
Monel I (a, b)
Cor.ugaed metal, da- Soft aluminum 2.50 2900besto- inserted Soft copper or brass 2.75 3700
or IIron or soft steel 3.00 4500Corrugated metal, lack- I Monel or 4-6% chrome 3.25 5500
eted asbestos filled Stainless steels 3.50 6500
Soft aluminum 2.75 3700Soft copper or brass 3.00 4 00
C..rrugated metal Iron or soft steel 3.25 5500 1 (a, b, c,d)Monel or 4-6% chrome 3.50 6500Stainless steels 3.75 7600
Soft aluminum 3.25 5500 __Soft copper or brass 3.50 6500
Flat metal lacketed as- Iron or soft steel 3.75 7600 la, lb, Ic*,bestos filled Monei 3.50 8000 1 d*, 2*
4-6% chrome 3.75 9000Stainless steels 3.75 9000
Soft aluminum 3.25 5500Soft copper or brass 3.50 6500 1 (a, b,c, d)
krooved meta, Iron or soft steel 5.75 7600 9 3:Monei or 4-6% chrome 3.75 9000 23Stainless steels 4.25 10100
Soft aluminum 4.00 8800Soft copper or brass 4.75 13000 I(a, o, c, d)
w,,id fiat met.. Iron or soft steel 5.50 18000 2a, 5Monel or 4-6% chrome 6.00 21800 2,3,4,5Stainless steels 6.50 26000 IIron or soft steel 5.50 18000
ding joint Monel or 4-6% chrome 6.00 21800 6Stainless steels 6.50 26000
aThe suriace of u gasket having a lap should not be against the nubbin.
16
oeI - c
on
0.9 Q=9
A -
----- 7 1Ti-
0.8- 0.807- T7-rt
sI I I I I-
-Hi 1 0.°
0.8-t : - - : : : : : .
1 1.5 2 25 3 3.5 4 45
, I/s
FIG. UA-41.2 VALUES OF F (Integral flange factors) (Reference 1)
Figs& UA-51.3-UA-51.5 SECTION VillI DIVISION I PRESSURE VESSELS (Reference I)
0.6 . . . . . . .. s 0
05 0.5
Z-z I- ha rBy,
200
0025
15 2 2.5 3 3.5 4 4.5 5
s,/9o
FIG. UA-1.3 V ALUES OF V (Integral flange factors))
Figs UA-SI.3-UA-SI.5 SECTION VIII - DIVISIDN I PRESSURE VESSELS (Reference ] )
o5 :=,Plr-tt--+C I io.1 rl~7105
- - -i., "
0.1 , -" :.
I~ , , t:
o! l3 N II I .:C-LL i 1: Il ll ' o0
I. 1. .535 4 .
S,/.YoFIG. UA451.3 VALUES OF V (integrl flange factor)
17'
25
20= I (Minimum)
f= / For hubs ofun/form thickness(gt/o= )15 F= / For loose hubhbed f/nges
10
66 v ,
f5 ... . 5F
4II I I
3 3
2.5 O I I 2.5
2 2
oo1.5 e 1.5
1 1or /A
FIG. UA-61.6 VALUES OF f (Hub stress correction factor) (Reference 1)
liESI GN OFiiELD i N ECK
F'L I G ..F I :
FLANGES 18
PROGRAH
0000-FMT-- 42 56--FM iT -- 42 0112 --XT---23
0001--FIMT -- 42 157--FMT---42 0113-- 6 --- 60002--PHT---415 058--XFR---67 0114--GTO---440003---PHT--t5 0059--SFL ----5 4 0115-- 1 ---81
8 00 i4---PNT ---45 0060--FMT---42 0116-- 8 --- 1l0E5-- D --- 3 61--TP---41 17-- 6 1 -- --- 06
00E06-- E --- 6 862--PHT---45 8118-- 4 ---84
0 7--YT0---40 E8063--XTO --- 23 0119--- CNT ---. 47
oo0 8-- i [--- 65 0064-- 2 --- 2 0120--CHT---471009-- G --- 15 0065--FMT---42 0121-- UP---27
0010-- iN --- 73 0066--FMT1-----42 122-- 2 ---- 020011--PNT --- 45 8067-- M --- 78123-- X --- 360012-- o ----;'1 O168--SFL --- 54 0124-- 1 --- 50013-- F ----16 0069---FMiT -- 42 0125-- X --- 36800 4--CLR---20 j-1070--STP---41 126.--XEY-- -3000! -- PNT---45 071 -- PNT --- 45 0127--FMT --- 42
n 16--PHT---45 8072--XTO---23 0128--FMT---420017--IIN -- -- 31 0.73-- 3 --- 3 8129--- H ----74801.:-- E --- 68 874--FT ---- 42 0130-- i --- 5E:0019-- L --- 72 0075--FMT---42 0131--SFL---540020-- D --- 63 876-- G --- 15 1I32--FiMT---42
0021-- I --- 65 0077--SFL---54 I133--PNT---450022-- N --- 73 0078--FMT---42 0 134--XTO---230023-- G --- 15 0079--STP---41 0135-- 7 --- 070024--PHT --- 45- 801--PNT --- 45 1 36-- FR---670025--N----73 081--XTO---23 0 137-- 4 ---840026-- E --- 60 8082-- 4 --- 04 0138--,S---1210027.-- C --- 61 083--,FR---67 1 39--RUP---220028-- K --- .55 084-- 1 --- 01 0140-- i --- 560029--PNT---45 00O85--XFR---67 0141-- X --- 36e10031--PNT---45 0086-- -- 36 0142--XFR---67E031--PNT---45 0087-- 2 --- 02 0143-- 6 --- 06E032--PHT---45 088--XFR --- 67 0144-- X --- 36
0133--PNT---45 0089-- X ----36 - 0145-- 4 --- 04134--PNT --- 45 0190-- 4 --- 04 0146--DIV---350035-- F --- 6 091--RUP-----22 14 7 --- EY -- 30036-- L --- 72 0092-- . --- 56 0148--FM'T---4208037-- 8 --- 62 0093-- X --- 36 0149--FMT---420038-- N ----73 0194--XEY---30 0150-- H --- 74
039-- G ---!5 OEi95--FMT----42 0151--SFL-----540040-- E --- 60 0096--FMT--- 42 1 52--FMT---420041--YTO---40 0097--N--N---31 0153--PNT---450042--PNT---45 098-- Ml ----70- 0154--XTO---2381043--PNT----45 0099-- 2 --- 02 0155-- 8 --- 100i144--PNT --- 45 01001--SFL---54 0156--RUP---220045--PNT--- 45 0101--FMT---42 0157--XFR---670046--CLR---28 0102--PNT---45 0158-- 7 --- 0 7O047--CLR---20 0103--XT0O---23 0159-- + --- 3k0048--CLR---20 0114-- 5 ---- 5 E16E-- ,.EY----300E149 -- B --- 66 010.5- -FMT---42 0161--FMT . - 420050--SPL---54 0 106-- FMIiT ---- 42 01 62--FIT --- 42i0051i--FMT---42 E!07-- -- ---56 0163--IND ----31
805.2--;STPF---41 810 8 ---'-; FL. ---54 0164-- M ---0053--PHT --- 45 0109--FMT---42 0165 -- 1 --- 01!0 0!54--;::Ti--- -23 0 11 :l -- ST P- ----41 0166 '--;FL---540655 - - 1 --.-c 1 -N- --i:: -r-T .. .45 1 67--FMT-- -42
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CONCLUDING REMARKS
This computer aided design program presents an "interactive" procedurefor the engineer utilizing the electronic desk top calculator to obtainthe optimum circular, integral or optional type flanges under internalpressure. The design criteria meets the requirements of the 1971 ASMEPressure Vessel Code. This program provides the flexibility of comparingthe computed stresses for a selected flange thickness to the allowedcode value for a given geometry. Since the design equations for loose,non-circular and split flanges subject to internal and external pressureare similar to the integral and optional type flange, this program couldeasily be modified and adapted to those types of design, The othertypes of flanges in conjunction with different gasket and outer rimcontacts are not as easily programmed but the general outline andprocedure is valid.
REFERENCES
1. American Society of Mechanical Engineers:Boiler and Pressure Vessel Code, Section VIII,Division I, 1971, Appendix II, pages 210-221.
2. Hewlett-Packard 9810A Calculator,"Programming", "Printer Alpha ROM", and"Mathematics Block" Operating Manuals, 1971 Editions.
3. Taylor Forge DivisionGulf and Western Manufacturing CompanyModern Flange DesignBulletin 741, 1973 Edition