GOST 14249-89 (E)

STATE STANDARD OF THE USSR

VESSELS AND APPARATUSES NORMS AND METHODS OF STRENGTH CALCULATION GOST 14249-89 (ST SEV 596-86, ST SEV 597-77, ST SEV 109-78, ST SEV 1040-88, ST SEV 1041-88! STATE COMMITTEE OF THE USSR FOR STANDARDS M"#$"% STATE STANDARD OF THE USSR

GOST 14249-89

VESSELS AND APPARATUSES N"&'# )* M+"*# ". S&+)/ C$")

(ST SEV 596-86, ST SEV 597-77, ST SEV 109-78, ST SEV 1040-88, ST SEV 1041-88!

D+ ". I)&"*$")

01301390

This Standard lays down the norms for and methods of calculating the strength of cylindrical shells, conical elements, end plates and covers of vessels and apparatus made of carbon and alloy steels which are used in the chemical industry, oil-refining, and related branches of industry where they operate in conditions of single action and multiple-action static loadings under internal excess pressure, vacuum, or external excess pressure, and under the effects of axial and transverse forces and bending moment s. It also lays down values for permissible stresses, Young's modulus of elasticity, and safety factors for the strength of welded seams. The norms and methods of calculating strength shall be applied whilst at the same time observing the !egulations for the structure and safe operation of vessels operating under pressure approved by the "SS! State #ining Indus try Inspectorate, and on the condition that deviations from geometrical shape and inaccuracy in the manufacture of the elements of vessels and apparatus that are designed do not exceed the tolerances laid down in norm-setting and technical documentation.

13 GENERAL REUIREMENTS

$.$. %e si gn te mp er at ur e $.$.$. The design temperature is to be used for determining the physical and mechanical characteristics of the material and the permissible stresses. $.$.&. The design temperature is to be determined on the basis of heat-engineering calculations or the results of tests. The maximum value for the temperature of the wall of a vessel or apparatus is to be taen as being the design temperatu re. If that temperature is less than &()*, a temperature of &()* is to be used as the design temperature when determining the permissible stresses. $.$.+. If it is not possible to mae heat calculations or tae measurements, and if the temperature of the walls rises to the temperature of the medium in contact with the wall during the time that it is in operational use, the design temperature is to be taen as being the maximum temperature of the medium but it is not to be less than &()*. If heating is by open flame, waste gases or electric heaters, the design temperature is to be taen as being eual to the temperature of the medium increased by &()* in the case of enclosed heating, and by ()* in the case of direct heating, unless more accurate data is available. $.&. ori ng, de si gn, and te st p re ss ur e $.&.$. The term woring tempe rature for a vessel or apparatus should be understoo d as meaning the maximum internal excess or external pressure arising during the normal course of the operating process, without taing into consideration hydrostatic pressure from the medium and without taing into account the permissible rise of pressure over a brief period when a safety valve or some other safety device is functioning. $.&.&. The design pressure in the woring conditions of elements of vessels and apparatus is to be understood as meaning the pressure that is used when maing calculations for their strength. /s a rule, the design pressure for the components of a vessel or apparatus is to be eual to or higher than the woring pressure. If the pressure in a vessel or apparatus increases by more than $(0 relative to the woring pressure when safety devices are functioning, the elements of the apparatus shall be designed for a pressure eual to 1(0 of the pressure when the valve or safety device is fully opened. 2or elements that separate spaces which are at differing pressur es 3e.g., in apparatus with heating 4acets5, the design pressure should be taen either as being each pressure separately or as the pressure which reuires the greatest wall thicness in the element that is being designed. If it is ensured that the pressures act simultaneously, it is permissible for calculations to be based on the difference between the pressures. The pressure difference is also to be used as the design pressure for those elements which separate a space that has an internal excess pressure from a space that has an absolute pressure less than atmospheric pressure. If there is no accurate data available on the difference between the absolute pressure and atmospheric pressure, the absolute pressure is to be taen as being 6ero. If a hydrostatic pressure amounting to 0 or more of the woring pressure acts on an element a vessel, the pressure design pressure shallorbeapparatus increasedshould by thatbeamount. $.&.+.of The term test in a vessel understood as meaning the pressure at which testing of the vessel or apparatus is to be carried out. $.&.7. The design pressure under test conditions for the elements of vessels and apparatus should be understood as meaning the pressure to which they are sub4ected during trial testing, including the hydrostatic pressure if it is 0 or more of the test pressure. $.+. %es ign fo rc es an d mo me nts The design forces and momen ts are to be taen as being the forces or moments acting for the relative state of loading 3e.g., during operational use, testing or installation5 which arise as the result of the effects of the intrinsic weight of pipe runs connected to the vessel or

apparatus, and of wind, snow and other loadings. The design forces and moments due to wind loadings and seismic effects are to be determined in accordance with 89ST &7:;. $.7. when maing calculations relating to the limiting loadings of vessels and apparatus operating under single-action? static loadings is to be determined by means of the following formulae@ for carbon and low-alloy steels

 R or Rp (.& Rm Rm A $( [σ ] = η ⋅ min e B B nт nв nд 

-

B

R p$.( A $( nп

  

3$5

for austenitic steels

R R R [σ ] = η ⋅ min p$.( B m B m A $( n  т nв nд

-

B

Rp$,( A $(nп

   3

3&5

CCCCCCCCCC ? If the vessels or apparatus operate under multiple-action static loadings but the number of cycles of loading due to pressure, constraints on thermal deformations, or other effects do not exceed $( +, such a loading is conventionally considered as being a single-action loading in calculations for strength. hen determining the number of cycles of loading, variation within the limit of $0 of the design load are not to be taen into account. The limiting creep stress is to be used for determining the permissible stresses in those cases where there is an absence of data regarding the rupture stress, or in connection with conditions of operational use when it is necessary to limit the amount of deformation 3displacement5. If no information is available concerning the nominal yield point when there is $0 residual elongation, the permissible stress for austenitic steel is to be determined using formula 3$5. 2or test conditions, the permissible stress is to be determined by means of the formula

[σ ] = η ⋅

R &( or R &( e p (.& nт

3+5

2or test conditions for vessels and apparatus made of austenitic steel, the permissible stress is to be determined by means of the formula

[σ ] = η ⋅

R &( or R &( p (.& p $.( nт

375

$.7.&. The safety factors for strength shall correspond to the values given in Table $. Table $ Doading conditions 9perating conditions Test conditions@ hydraulic testing pneumatic testing *onditionsduringinstallation

nE $. $.$ $.& $.$

Safety factors for strength nF nG &.7 $. -

-

-

nH $.( -

-

-

2or vessels and apparatus of 8roups + and 7 as given in the "SS! State #ining Industry Inspectorate's !egulations for the structure and safe operation of vessels operating under pressure, it is permissible to tae the safety factor for tensile strength nF as being eual to &.&. In a case where the permissible stress for austenitic steel is determined by means of formula 3$5, the strength safety factor nE at nominal yield point Rp0.2 for woring conditions is to be taen as being eual to $.+. 2or vessels and apparatus which function in conditions of creep with a design operating life of $( 7 up to & ×$( hours, the strength safety factor nG is to be $.. hen the design operating life is & ×$( hours, it is permissible to tae the strength factor nG as being eual to $.& if the heat creep resistance and long-term plasticity are monitored when the material is in operational use and the deviation of the creep rupture strength and creep from the mean value on the lower side does not exceed &(0. It is not reui red that calculations for the strength of cylindrical shells and conica l elements, convex and flat end plates for test conditions should be carried out if the design pressure in the test conditions would be less than the design pressure in woring conditions multiplied by

[σ ] &( $.+ [σ ] . $.7.+. The corrective coefficient to the permissible stresses 3 η5 shall be eual to one except in the case of steel castings, for which coefficient Η shall have the following valuesB (. - for castings sub4ect to individual testing by non-destructive methodsB (.: - for other castings. $.7.7. 2or steels that are widely used in the chemical, petrochemical and oil-refining machinery building, the permissible stresses for woring conditions when Η J $ shall correspond those steel givenplate in /ppendix $. $.7.. 2ortorolled manufactured in accordance with technical specifications for the two strength groups, it is allowable for the permissible stresses for the first group to be taen from Table  of /ppendix $. 2or rolled sheet steel of the second strength group 3steels KSt+ps, KStSsp, KStS8ps and (18&S5, the permissible stress taen from Table  of /ppendix $ is to be increased by ;0 - and by :0 for steel (18&. hen steels KStSpc, KStSsp and KSt+8ps of the second strength group are being used at a temperature higher than &()*, or steels (18&S and (18S of the second strength group at a temperature of more than +(()*, the same permissible stresses are to be taen as for steel of the first group. $.7.;. hen the temperature is &(()*, it is permissible to determine the permissible stress in accordance with clause $.7.$, using the guaranteed values of the mechanical characteristics in accordance with the Standards or technical specifications for the steel and taing into account the rolling thicnesses of steel plate. hen the temperatures are higher, it is permissible for the permissible stresses together with the rolling thicness and strength group of the steel which are taen into account to be determined in accordance with officially approved norm-setting and technical documentation. $.7.:. %esign mechanical characteristics which are necessary for determining the permissible stresses at increased temperatures for steels that are not given in /ppendix $ are to be determined after carrying out tests on a representative number of test specimens which will ensure that guaranteed values for the strength characterises are obtained. $.7.. 2or elements of vessels and apparatus which function in conditions of creep at design temperatures which vary over the whole of the period of operational use, it is permissible to use as the permissible stress an euivalent permissible stress =σ>eu calculated by means of the following formula.

[σ ]$ $A m

=σ>eu J

 n T  [σ ]  m  ∑ i  $    $ To  [σ ] i  

,

35

where = σ>i J =σ>$B =σ>&B ... = σ>n - is the permissible stress for the design period of operatio nal use at temperatures ti 3i J l, & ...5B Ti - is the duration of the stages of operational use of the elements at wall temperatures corresponding to ti 3i J l, & ...5, hrsB n

∑ Ti To = $ - is the total design operating life, hrsB т - is an exponent in euations for the creep limit of steel 3it is recommended that m J  should be used for high-temperature alloy steels5. It is recommended that the stages of operational use at different temperatures should be taen in temperature steps of ) and $()*. $.7.1. 2or vessels and apparatus which function with multiple-action loadings, the permissible amplitude of stresses is to be determined in accordance with 89ST &1. $.7.$(. 2or elements of vessels and apparatus which are not calculated using limiting loadings 3e.g., flange connections5 the permissible stresses shall be determined in accordance with the relative officially approved norm-setting and technical documentation. $.7.$$. %esign values for the yield point, tensile strength and coefficient of linear expansion are given in /ppendices & and +. $.7.$&. hen maing calculations for the stability of apparatus using low critical stresses within the limits of elasticity, the safety factor for stability 3nL5 should be taen as being@ for woring conditions - &.7B for testing and installation conditions - $. $.. %es ign va lues of the modul us of l ongi tudi nal e las tici ty $..$. The design values for the modulus of longitudinal elasticity M for carbon and alloy steels according to temperature shall correspond to those given in /ppendix 7. $.;. Sa fe ty fa ct ors of we lds hen maing calculations for the strength of welded elements of vessels and apparatus, a safety factor for the strength of the welded connections should be introduced@ ϕN - for a longitudinal seam in a cylindrical or conical shellB ϕE - for a circular seam in a cylindrical or conical shellB ϕO - for the welded seams of a stiffening ringB ϕa - for a transverse welded seam for a reinforcing ringB ϕ, ϕP, ϕQ - for the welded seams of convex and flat end plates and covers 3depending on their position5. The numerical values of these factors shall correspond to the values given in /ppendix . 2or seamless elements of vessels and apparatus ϕ J $. $.:. /dditi ons t o des ign th icn ess es of c ons truc tion ele ment s $.:.$. hen designing vessels and apparatus it is necessary to tae into account an additive correction c to the design thicnesses of the elements of the vessels and apparatus. The construction thicness of an element of a vessel or apparatus shall be determined in accordance with the formula s ≥ sp+c, where sp - is the design thicness of the wall of the element of the vessel or apparatus. The addition to the design thicness should be determined from the formula

3;5

c J c$ R c& R c+.

3:5

hen maing the chec calculation, the addition is to be deducted from the values for the construction thicness of the wall. If the actual wall thicness is nown, it is permissible not to tae c& and c+ into account when carrying out the chec calculation. $.:.&. The 4ustification for all additions to the design thicness shall be given in the technical documentation. If there is two-sided contact with a corrosive andAor erosive medium, the addition c$ for compensation for corrosion andAor erosion shall be increased accordingly. The technological corrective addition c+ maes provision for compensation for the thinning of the wall of the element of the vessel or apparatus during technical processing - drawing, stamping, bending of pipes, etc. This addition should be taen into consideration when preparing the woring drawings according to the technical processes used. /dditions c& and c+ are to be taen into account in those cases where their sum exceeds 0 of the nominal thicness of the sheet steel. The addition c+ for the technological process used does not include rounding off of the design thicness to a standard sheet thicness. hen calculations are made for elliptical end plates that are manufactured using stamping, the technological addition c+ to compensate for thinning in the flanging 6one is not to be taen into account if its value is not greater than $0 of the design thicness of the plate. $.. *he ci ng f or f ati gue st re ngt h $..$. 2or vessels and apparatus which function under multiple-action loadings with the number of cycles of loading due to pressure, constriction of thermal deformations or other effects greater than $( + over the whole operating life, a chec should be made for fatigue strength in addition to the calculations that are made in accordance with this Standard. $..&. Kessels and apparatus which function with multiple-action loadings are to be checed for cyclical fatigue strength in accordance with 89ST &1. 23 CALCULATION OF CLINDRICAL SHELLS &.$. %esign diagrams *onditions for applicability of design formulae &.$.$ %esign diagrams for cylindrical shells are given in 2igs $-7. &.&. *ondi tion s for appl ica bil ity of de sign for mula e &.&.$. The design formulae are to apply when the ratio of the wall thicness to diameter is s−c D

≤ (.$

for shells and pipes when % ≥&(( mmB

s−c ≤ (. + D for pipes when %&(( mm.

S'"" $)*&$ #+#

a - shell with flange or flat end plateB b - shell with rigid bulheads 2ig. $

S'"" $)*&$ #+# % $")+ "& $")$ +)* +#

a - shell with flanged end platesB b - shell with end plates without flanges 2ig & S'"" #+# %  :$;+

2ig. + C)*&$ #+ &+)."&$+* % #..+))/ &)/#

2ig. 7 ote. 2igs. $-7 do not define the construction and are given only to show the design dimensions.

&.&.&. The design formulae given in clauses &.+.&, &.+.7-&.+.:, and &.7.& should be used on condition that the design temperature does not exceed the values at which creep of the materials is to be taen into accoun t, i.e. at those temperatures when the permissibl e stress is determined only by the yield point or tensile strength 3strength limit5. If no accurate data is available, it is permissible for the formulae to be used provided that the temperature of the wall of the shell does not exceed +()* when it is made of carbon steel, 7&()* when it is made of low-alloy steel, and &)* when it is made of austenitic steel.B &.&.+. 2or shells which are reinforced with stiffening rings, the following limitations shall be satisfied in addition to the reuirements of clauses &.&.$ and &.&.&@ the ratio of the height of the cross section to the diameter is to be@

h &

D

≤ (.&B

the design formulae should be used provided that the stiffening rings are positioned uniformlyB in those cases where the stiffe ning rings are not fitted unifo rmly, it is necessary to substitute the values b and l$ for that area on which the distance between two ad4acent stiffening rings is the maximumB if l&> l$, l& to be taen as the design length l . &.&.7. The design formulae for shells which function under the effect of an axial compressive force given in clause &.+.7 are to be used on condition that@ l or b D

≥ $.(.

In the absence of more accurate calculations, it is permissible to use formula 3&&5 for shells on which l or b D  $.(

&.+. Smo oth cyl in dri ca l s hel ls &.+.$. Shells which re lo!e! with n internl e"cess press#re &.+.$.$. The wall thicness should be calculated by means of the formula s ≥ sp+c,

35

pD

where sp J

&[σ ]ϕ p

−

p

.

315

&.+.$.&. The permissible internal excess pressure should be calculated from the formula &[σ ]ϕ p ( s − c )

=p> J

D + 3 s − c5 .

3$(5

&.+.$.+. hen a shell is made from plates of different thicnesses 4oined by longitudinal welded seams, calculation of the thicness of the shell is to be carried out for each plate taing into account the weanesses that exist in them. &.+.&. Shells which re lo!e! with n e"ternl press#re &.+.&.$. Thicness of the wall The thicness of the wall is to be determined approximately by means of formulae 3$$5 and 3$&5 and subseuently checed using formula 3$+5. s ≥ sp+c,

3$$5

 $,$ pD  ≅ m"& 2 D$0 −2 %  2[σ ]   where sp .

3$&5

*oefficient &2 should be found from the nomogram given in 2ig . Mxamples of the use of the nomogram for calculations are given in 2ig. ;.

N"'"/&' ."& $$")# ". #< %) + '# ". + +#$ ". $)*&$ #+# %$ .)$") )*+& ) ++&) &+##&+

F/3 5

Mxamples of the use of the nomogram 3see 2ig. 5

' - determining the design thicness of a wallB '' - determining the permissible external pressureB ''' - determining the permissible design lengthB m - start of procedureB n - intermediate pointsB × - final result 2ig. ; &.+.&.&. The permissible external pressure should be found from the formula

[ p ]H

[ p] =

 [ p]H    [ p] ( 

&

$ + 

.

3$+5

where the permissible pressure based on the condition for strength is to be found by means of the formula &[σ ] ( s − c ) =p>H J D + 3 s − c 5 .

3$75

whilst the permissible pressure obtained from the condition for stability within the limits of elasticity is to be determined using the formula &(.I ⋅ $(−; ( D $((3 s − c5 

n * ⋅ )$

=p>U J

l



&.-

 ,

D

3$5

where

 

min $.(B

$ J

1.7-

D l

D

 

$((3 s − c 5 

.

3$;5

hen determining the length of the shell l or  the length of the ad4oining element, l+ should be determined from the formulae  l+

l+

=

=

D ;t.α - for conical shells 3end plates5 witho ut flanges, but not more than

+ - for convex end plates,

the length of the conical elementB

 D  l+ = max r sin α B  ;t.α   - for conical shells 3end plates5 with flanges, but not more than the length of the conical element. The coefficient &$ is to be determined from the nomogram given in 2ig. . If the value obtained for coefficient &$ lays below the corresponding dot-and-dash line 3see

2ig. 5, it is permissible to determine the value of =N> in the preliminary calculation by means of the formula

[ p ] = &,7

&$ ⋅ $( −; ( n*

3$:5

&.+.+. Shells which re lo!e! with n "il tensile /orce &.+.+.$. The thicness of the wall should be calculated using the formula s ≥ sp+c, sp

3$5 0

=

πD[σ ]ϕ E .

where

3$15

&.+.+.&. The permissible axial tensile force should be calculated by means of the formula => = π3D+s - c53s - c5=σ>ϕE.

3&(5

&.+.7. Shells which re lo!e! with n "il compressi1e /orce &.+.7.$. The permissible axial compressive force should be calculated using the formula

[ 0 ]H

[0 ] =

 [ 0 ]H    [ 0 ]( 

&

$ + 

,

3&$5

where the permissible axial compressive force =2> H obtained from the condition for strength is =>H = π3D+s - c53s - c5=σ>,

3&&5

and the permissible axial compress ive force within the limits of elasticity = >U obtained from the condition for stability is =>U J min V=>U$B =>U&W.

3&+5

In formula 3&+5, the permissible axial compressive force =>U$, is to be determined from the condition for local stability within the limits of elasticity by means of the formula +$( ⋅ $(−; (

n* ⋅ )$

=>U$ J

$((3s − c5  D& ⋅   D 

&.-

,

3&75

and the permissible axial compressive force = >U& to be determined from the condition for general stability within the limits of elasticity using the formula =>U& J

π 3 D + s − c 53 s − c 5 (  π  n* λ

  

&

3&5

The flexibility λ, is to be determined from the formula

λ

=

&.I+lп D + s-c

3&;5

The reduced design length lHN is to be obtained from 2ig. :. l D ote. In a case where $(, formula 3&+5 assumes the form 324 5 J 324 5$. &.+.7.&. 2or woring conditions 3пL J &.75, the permissible compressive force may be determined from the formula => J π 3 D + s − c 53 s − c 5[σ ] min {ϕ$ Bϕ & } .

3&:5

The safety factors ϕ$ and ϕ& should be found from 2igs.  and 1.

!educed design length lHN / l

lHN

-

l

-

&l

-

(.:l

-

(.l

( (.& (.7

&.((l $.:+l $.7:l

(.; (. $.( ( (.& (.7 (.; (. $.(

$.&+l $.(;l $.((l &.((l $.:(l $.7(l $.$$l (.l (.:(l

*alculation diagram

2ig. :

&.+.. Shells which re lo!e! with  ben!in moment &.+..$. The permissible bending moment should be calculated from the formula

[6 ] =

[ 6 ]H &  [ 6 ]H   $ +   [ 6 ]( 

,

3&5

where the permissible bending moment =7>H obtained from the condition for strength is to be calculated using the formula π

=7>H = 7 D3D+s - c53s - c5=σ>

D

=>H,

3&15

and the permissible bending moment =7>U from the condition for stability within the limits of elasticity is to be calculated using the formula I1 ⋅ $(−; (

=7>U J

n*

$((3 s − c5  D+ ⋅   D 

&.-

=

D +.-

[  ] ($ .

3+(5

&.+..&. 2or woring conditions 3пL J &.75, the permi ssible bending moment may be determined by means of the formula π

=7> = 7 D 3D+s - c53s - c5=σ>ϕ+.

3+$5

The safety factor ϕ+ should to be determined from 2ig. $(. &.+.;. Shells which re lo!e! with trns1erse /orces The permissible transverse force =8> should be calculated from the formula

[8 ] H

[8 ] =

 [8 ] H    [8 ] ( 

$ + 

&

,

3+&5

where the permissible transverse force =X> H obtained from the condition for strength is =8>H J (.& πD 3s - c5, and the permissible transverse force =X> elasticity is

M

from the conditio n for stability within the limits of

&.7 ( 3 s − c5

=8>U J

n*

3++5

&

(.$I + +.+ D3 s − c5    l& .

3+75

&.+.:. Shells which /#nction #n!er the combine! e//ects o/ e"ternl press#re, n "il compressi1e /orce,  ben!in moment n!  trns1erse /orce Shells which function under the combi ned effect s of loadings are to be checed for stability using the formula &

p 0 6 8    [ p ] R [ 0 ] R [ 6 ] R  [8 ] $ ≤

where

=> =>

.(,

- is the permissible external pressure in accordance with clause &.+.&B - is the permissible axial compressive force in accordance with clause &.+.7B =7> - is the permissible bending moment in accordance with clause &.+.B =8> - is the permissible transverse force in accordance with clause &.+.;.

3+5

G& ."& *++&'))/ + .$"&

1

2ig.  G& ."& *++&'))/ + .$"&

2

2ig. 1

G& ."& *++&'))/ + .$"&



2ig. $( &.7. *yli ndri cal she lls r einf orce d wit h sti ffen ing r ings &.7.$. Shells with sti//enin rins which re lo!e! with n e"cess internl press#re &.7.$.$. %etermination of the dimensions of the stiffening rings when there is internal pressure The coefficient &7 for a given design pressure  and wall thicness s, should be calculated from the formula &7

=

p3 D + s − c5 &ϕ p [σ ] 3 s − c 5

−$ .

3+;5

If &7≤ (, reinforcement by means of stiffening rings is not reui red. ithin the range

0

< &9<2

ϕт ϕp

−$ , the distance between two stiffening rings should be calculated using

the formula

b≤

D 3 s − c 5  &  &7

− ϕ p $ + $   ϕE  & 7  ,

3+:5

and the area of the transverse cross section of the ring from the formula

[σ ] ⋅ ϕ p ⋅& [σ ] ⋅ ϕ ; 7 . :O ≥ l$ 3s - c5

3+5

&

ϕE ϕp

If &7 ≥ -$, it is necessary for the wall thicness to be increased to such a dimension that the following condition is fulfilled &

(  &7 

ϕE ϕp

-$.

ote. The corrective addition <$ to compensate for corrosion should be taen into account when determining the area of the transverse cross section of the stiffening ring :;. &.7.$.&. The permissible internal excess pressure should be determined from the condition => J min V=>$B =>&W. 3+15 The permissible internal excess pressure = >$ determined from the condi tions for the strength of the complete shell should be calculated using the formula

=; σ ;ϕ; l$ D + 3s − c5 .

&] [σ ϕ p 3 s − c 5 ]+[ &

[ p ]$ =

37(5

The permissible internal excess pressure = >& determined from the condi tions for the strength of a shell between two ad4oining stiffening rings should be calculated from the formula

[ p] & =

&[σ ]ϕ E 3 s − c5 & + λ&H

D + 3 s − c5

$+

ϕ E λ&H ϕ

.

37$5

where λ&п

=

b& D3 s − c 5 .

37&5

&.7.&. Shells with sti//enin rins which re lo!e! with n e"ternl press#re &.7.&.$. The design parameters for the reinforced shell are to be@ The design parameters for the reinforced shell are to be@ the effective length of the wall of the shell l , which is to be taen into account when determining the effective moment of inertia and should be determined from the condition D3 s − c 5

l J minVl$B t R $.$

WB

37+5

the effective moment of inertia ' of the design transverse cross section of a stiffening ring, which should be determined using the formula l$ 3 s − c 5 + '

$(,1

= '; +

&

+e

=; le 3 s − c 5 =;

+ le 3 s − c 5 B

3775

the coefficient of rigidity ? of a shell which is reinforced with stiffening rings ?

=

$(,1 '

l$ 3 s − c 5 +

.

375

ote. The additive correction <$ to compensate for corrosion should be taen into account when determining the moment of inertia of a stiffening ring. &.7.&.&. The permissible external pressure should be determined from the condition

=> J min V=>$B =>&W.

37;5

&.7.&.&.$. The permissible external pressure = >$ determined on the basis of the condition for the stability of the complete shell should be calculated from the formula

[ p ]$H

[ p ]$ =

 [ p ]$H    [ p ]$( 

&

$ + 

,

37:5

The permissible external pressure =>$H shall correspond to the value for = >$ determined by means of formula 37(5 when the values of the safety factor ϕN and ϕE are ϕN J $.( and ϕE J $.(. The permissible external pressure = >$U obtained from the condition for stability within the limits of elasticity should be calculated using the formula &(.I ⋅ $(−; ( D

?)& n*

=>$U J

l

$((? 3 s − c5 

⋅  

D

&.-

 ,

375

where



min $.(B



& J

1.7-

D l

D $((? 3 s

 − c5 

.

3715

&.7.&.&.&. The permissible external pressure = >& is to be determined starting from the conditions for the stability of the shell between stiffening rings. The permissible external pressure =>& when the value for the length

bB  lJ 

l&

t −  &

shall correspond to the pressure = > 3see clause &.+.&.&5. It is permissible to use = >& found from formula 37$5 with the value of fact or ϕE J$.( instead of using = >H determined from formula 3$75. &.7.&.+. %etermining the dimensions of a stiffening ring when there is external pressure /fter the dimensions of the ring and shell have been determined in accordance with design considerations, a chec should be carried out in accordance with clause &.7.&.&. The wall thicness s or the distance b between stiffening rings for a given design pressure  should be determined with the aid of the nomograms 3see 2igs.  and ; 5. hen the nomogram given in 2ig.  is used, it should be taen that l = b. The design effective moment of inertia of the stiffening ring should be calculated using the formula + (.$ pD l$ n*

'p

=

(

&.7 &- .

The coefficient &@ should be determined from 2ig. $$.

G& ."& *++&'))/ + $"+..$+) K5

3(5

2ig. $$ /fter the design effect ive moment of inertia has been obtained using the successive approximations method, a profile for the stiffening ring with a moment of inertia 'O, should be selected which ensures that the reuirement of the following condition is fulfilled ' ≥ ',

3$5

where ' - is the effective moment of inertia of the design transverse cross section of the stiffening ring determined using formula 3775. &.7.+. Shells with sti//enin rins which re lo!e ! with "il tensile or compressi1e /orces,  ben!in moment or  trns1erse /orce The permissible loadings should be calculated by means of the formulae in clauses &.+.+&.+.; with l = b. hen determining the reduced design length lHN from 2ig. :, the total length  should be used instead of l. 2.9.9. Shells with sti//enin rins which re s#bAecte! to lo!s ctin sim#ltneo#sl* *alculation should be carried out in a similar manner to the calculation given in clause &.+.: and, when doing so, the permissible external pressure is to be determined in accordance with clause &.7.&.&.

3 CALCULATION OF CONVE= END PLATES

+.$. *alculation diagrams +.$.$. 2ig. $& shows calculation diagrams for elliptical, hemispherical and torospherical end plates.

C")+ E)* P+#

 - elliptical end plateB b - hemispherical end plateB c - torospherical end plate 2ig. $& ote. This 2ig. does not define the construction of the end plates and is given only to show the necessary design dimensions. +.&. *ondi tion s for appl ica bil ity of de sign for mula e +.&.$. The design formulae are to apply when the following conditions are fulfilled@ for elliptical end plates (.((&≤

s$ − c D ≤(.$((, -

(.&≤ D

≤(.B

for torospherical end plates

s$ − c (.((&≤ D ≤(.$((. 2or torospherical end plates, the following types of end plates are to be used in calculations depending on the relationship between the parameters R, D$ and r$@ type / R≈D$, r$ ≥ (.(1 D$B type Q R≈(.1 D$, r$ ≥ (.$:( D$B type  R≈(. D$, r$ ≥ (.$( D$. +.&.&. The design formulae given in clauses +.+.& and +.7.& are to apply provided that the design temperatures do not exceed the values at which creep of materials is taen into account, i.e. at those temperatures when the permissible stress is determined only by the yield point or tensile strength 3strength limit5. If there is no accurate information available, it is permissible for the formulae to be used provided that the design temperature of the wall of an end plate made of carbon steel does not exceed +()*, that of one made of low-alloy steel does not exceed 7&()*, and that of one made of austenitic steel does not exceed &)*. +.+. Mlli pti cal and hemi sphe ric al end plat es +.+.$. (llipticl n! hemisphericl en! pltes lo!e! with e"cess internl press#re +.+.$.$. The thicness of the wall s$ should be calculated using the formula s$ ≥ s$p+c,

3&5

where

=

s$ p

pR &ϕ [σ ]

− (.- p .

3+5

+.+.$.&. +.+.$.&. The permissible internal excess pressure = > should be calculated from the formula

&( s$ − c )ϕ [σ ] + (.-3 s$ − c5 . R =p> J

375

+.+.$.+. The radius of curvature at the crown of an end plate is to be eual to@ R

=

D& 7- ,

35

where R = D - for elliptical end plates with B J (.& DB R = (. D - for hemispherical ends plates with B J (. D. +.+.$.7. If the length of the cylindrical flanged part of the end plate is h$ Z (. D3 s$ − c 5 - for an elliptical end plate, or h$ Z (.+ D3 s$ − c 5 - for a hemispherical end plate, the thicness of the end plate shall not be less than the thicness of the shell calculated in accordance with clause &.+.$ with ϕN J $. +.+.$.. 2or end plates which are manufactured from a single blan, the safety factor ϕ J $. 2or end plates manuf actured from a number of blans, factor ϕ should be determined in accordance with /ppendix . +.+.&. (llipticl n! hemisphericl en! pltes which re lo!e! with n e"ternl press#re +.+.&.$. The thicness of the wall is to be determined approximately by means of formulae 3;5 and 3:5 with subseuent checing using formula 35 s$ ≥ s$p+c,

3;5

where

s$ p

 = max  & C R  -$(

n* p pR   B  ; − $( ( &[σ ]  

.

3:5

2or the preliminary calculation, & is to be taen as being eual to (.1 for elliptical end plates, and $.( for hemispherical end plates. +.+.&.&. The permissible external pressure = > should be calculated from the formula

[ p] =

[ p ]H

 [ p]H   [ p]  (  

&

$ + 

, where the permissible pressure =>H obtained from the condition for strength is

35

&[σ ] ( s$ − c ) =p> J

R + (.-3 s$ − c5 ,

315

and the permissible pressure =>U from the condition for stability within the limits of elasticity is

=>U J

&; ⋅ $( − ; ( $(( ? 3 s$ − c 5   & R  n* C  

&

.

3;(5

+.+.&.+. The coefficient & should be determined in accordance with 2ig. $+ or by means of formula 3;$5 depending on the ratios D s$ − c &C

=

-

and D

$ + 3&.7 + I "5 " $ + 3+.( + $( "5 " ,

3;$5

where " = $(

s$ − c  D  D  &

 − &  D .

3;&5

G& ."& *++&'))/ + $"+..$+) Kэ

2ig. $+ +.7. Torospherical end plates +.7.$. Torosphericl en! pltes which re lo!e! with 'nternl e"cess press#re +.7.$.$. The thicn ess of the wall in the bound ary area should be calculated using the formula s$ ≥ s$p+c,

3;+5

pD$ ⋅ β$ &ϕ [σ ] .

3;75

where

s$ p

=

2or welded end plates, an additional chec of the thicness of the wall in the central area should be carried out using the formula@ s$ ≥ s$p+c, where

3;5

s$ p

=

pR &ϕ [σ ]

− (.- p .

3;;5

+.7.$.&. The permissible excess pressure obtained from the condition of strength of the boundary area should be calculated using the formula

[ p] =

&3 s$ − c 5ϕ [σ ]

D$ ⋅ β &

.

3;:5

2or welded end plates, it is necessary to carry out an additional chec of the permissible excess pressure from the condition for the strength of the central area using the formula

[ p ] = R&3+s$(−.-c35sϕ−[σc]5 $ .

3;5

The lesser of the pressures determined using formulae 3;:5 and 3;5 should be taen as the permissible pressure. In the case of welding of end plates made up of sheet steel of differing thicnesses, the relative values for the thicness of the walls in the edge and central areas should be substituted in formulae 3;:5 and 3;5.

G& ."& *++&'))/ + $"+..$+)

2ig. $7

1

G& ."& *++&'))/ + $"+..$+)

2

2ig. $ +.7.$.+. The coefficient β$ should be determined in accord ance with fig. $7 , and the coefficient β& accordance with 2ig. $ or from the formulae@

type / β& J max

 $.&-B 

type Q β& J max

type  β& J max

  

(.&- +

 $.((B 

 (.1(B 

  

D$ s$ − c

(.$& +

  

(.$& +

 + $.((   B

D$ s$ − c

 + +.:-   B

3;15

 + +.&(  s$ − c  . D$

+.7.$.7. 2or end plates manufactu red from a complete blan, the factor ϕ J $. 2or end plates manufactured from a number of parts, factor ϕ should be determined from Table &. Table & Setches of end plates

ϕ for σ for formulae 3;$5, 3;5 formulae 3;+5, 3;;5 2or seam / ϕP

$ 2or seam Q

ϕQ

$ ! hen D (.;

$

ϕQ

ϕ for formulae 3;$5, 3;5

Setches of end plates

σ for formulae 3;+5, 3;;5

! hen D ≥(.;

ϕP

$

The values of factors ϕP and ϕQ should be determined in accordance with /ppendix . +.7.$.. If the length of the cylindrical flanged part of an end plate h $ ≥ (. D$ 3 s$ − c 5 , the thicness of the cylindrical part of the end plate shall not be less than the thicness of the shell calculated in accordance with clause &.+.$ when ϕ J $. +.7.&. Torospheric en! pltes which re lo!e! with n e"ternl press#re +.7.&.$. Torospheric end plates loaded with an external pressure should be calculated in accordance with clause +.+.& using formulae 35, 315 and 3;(5 with & J $. In addition, the external pressure shall not exceed the permissible pressure determined using formula 3;:5. 7. */D*"D/TI9 92 2D/T !9"% M%
s$ − c Dp

≤ (.$$ .

s$ − c Dp

> (.$$ 7.$.&. It is permissible to carry out calculations when , but the value for the permissible pressure which is obtained by means of formula 3:5 or 375 should be multiplied by the corrective factor@ &p

=

& .&

  

$+ $+ ;

s$ − c  D p 

&

.

3:(5

If, when determining the thicness of the end plates in accordance with clauses 7.&.$ or s$ − c > (.$$ Dp 7.+.$, it proves to be that , it is necessary to carry out an additional determination of the permissible pressure in accordance with clause 7.&.: or 7.+. and to multiply it by the coefficient &. If &=>  , the thicness of the end plates should be increased so as to satisfy the condition &=> ≥ . 7.&. *alc ula tion of f lat roun d end plat es and c over s 7.&.$. The thicness of flat round end plates and covers of vessel sand apparatus which function under internal excess pressure or external pressure is to be calculated using the formula s$ ≥ s$p R c,

3:$5

where s$ p

= &&

o

Dp

p ϕ 3σ 5 .

3:&5

7.&.&. The value of the coefficient & is to be taen from Table + according to the construction of the end plates and covers. Table + T+

$

D&%)/

C")*")# ) %$ +)* + )* $"+& + $"))+$+*

K

 ≥ $.:×s

(.+

Dp J D

&

 ≥ (.×s

(.(

Dp J D

+

s−c

< (.&-

s$ − c

s −c

(.7

≥ (.&-

s$ − c

(.7$

Dp J D

7

s−c s$ − c

s−c s$ − c

< (.-

(.7$

≥ (.(.+

Dp J D 

s−c s$ − c

s−c s$ − c

< (.&-

≥ (.&(.7$

Dp J D Z (.

; 

Dp

(.7

×s JD

(.(

T+

D&%)/

C")*")# ) %$ +)* + )* $"+& + $"))+$+*

s−c

:

s$ − c

s−c s$ − c

K

< (.-

(.7$

≥ (.(.+

Dp J D s−c



s$ − c

s−c s$ − c

< (.-

(.7$

≥ (.(.+

Dp J D max VsB (.&×s$W ≤ r ≤ minVs$B (.$DW

1

h$ ≥ r

&

  = max (.$$ × $ − (.&+   (.+

D J D - &r s−c

$(

s$ − c

s−c

−c

s

< (.-

≥ (.-

$

(.7$

Dp J D (.&×s$ ≤ r ≤ s$ - s2

(.+

+() ≤ γ ≤ 1() $$ Dp J DE

(.7(

Dp J D[.H

(.$$

$&

7.&.+. The value of the coefficient of weaening &F for end plates and covers which have a single opening is to be determined from the formula &o

=

$+

! Dp

 ! +  D

p

&

    .

3:+5

7.&.7. The value of the coefficient of weaening 3 &F5 for end plates and covers which have a number of openings is to be determined from the formula

! D  = ! $ − Σ D  $ − Σ

&o

+

i

p

i p

       

.

3:75

*oefficient &F is to be determined for the cross section which is most weaened. The maximum sum of the lengths of chords of the openings and the most weaened cross section of the end plate or cover is to be determined in accordance with 2ig. $; using the formula Σ!i J m" V3!$ R !25B 3b2 R bE5W. The main design dimensions of the openings are given in 2igs $; and $:.

2ig. $;

2ig. $: 7.&.. The value of the coeff icient of weaening &F for end plates and covers without openings is to be taen as being eual to $.(. 7.&.;. In all cases of connection of an end plate to a shell, the minimum thicness of the flat round end plate shall be greater than, or eual to, the thicness of the shell calculated in according with clause &.+. 7.&.:. The permissible pressure on the flat end plate or cover is to be determined from the formula



s$ − c



&

] [ p =  ] [  σ ϕ  & ⋅ &o ⋅ Dp  . 7.&.. The thicness s2 for connections of types $(, $$ and $& 3see determined using the formula

3:5 Table +5 are to be

      s$ max $.$sB  /or t*pe $0 D p − &r   $+ ⋅ sin γ  s& ≥    $,& s$    D p − D&  p max (.-D p + cB s$ &  /or t*pes$$ n! $2. [σ ] Dp    

3:;5

7.+. *alcula tion of flat round covers with an additiona l edge moment 7.+.$. 2lat circular covers with an additional edge moment 32ig. $5 are to be calculated for internal pressure using the formula s$ ≥ s$p R c,

3::5

where s$ p

= &&

;

D

Dp

ϕ =σ >

.

3:5

7.+.&. The value of the coefficient &G is to be determined from the formula

&;

= (.7$

 D+  − $  D<.п 

$ + +ϕ 

D+ D<.п

3:15

or by means of the graph in 2ig $1, depending on the ratios DEHD<.п and ψ. The value of ψ is to be found from the formula ψ

where

= $+

0п 08

2

8 J (.: pD

2ig. $

=

ψ

or

.

<.п

0G , 08

3(5

2ig. $1 7.+.+. The value of the coefficient &F is to be determined in accorda nce with clause 7.&.+, or 7.&.7 if Σ!i ≤ (.:DpB when doing so, bolt holes are not to be taen into accou nt in the calculation. 7.+.7. 2or covers which have a groove to receive an upstand 3e.g., the chamber of a heat exchanger5 the value of coefficient &G for determining the thicness at the position of the groove 32ig $b5 is to be calculated taing into account the force due to compression of the gaset in the groove by using the formula

&;

= (.7$

$ + +ϕ  D+  D<.п

− $ + 1.; DD+ ⋅ Ds7 <.п <.п  D+ D<.п

.

3$5

7.+.. The thicness of a flat round cover s2 32ig $\5 which has an additional edge moment at the sealing position 32ig $a5 is to be determined from the formula s&

 ≥ max&: 

IB

(.;

D$

 

I + <

,

3&5

where

0 0  B   [σ] [ ] σ  .

I = max 

K. 

K. J

p

J

In formula 3&5, the subscript p denotes that the value relates to the operational state or to tests, whilst the subscript m denotes that the value relates to installation conditions.. 7.+.;. The value of coefficient &L is to be determined from the formula &:

= (.I

D+ D<.п

−$ 3+5

or in accordance with 2ig. &(, depending on the ratio of the diameters. 7.+.:. The thicness sE of the edge of a flat round cover with an additional edge moment outside the sealing 6one 3 2ig $5 is to be deter mined by means of formula 3&5 , using D2

instead of Dc.п when doing so 7.+.. hen chec calculations of the permissible pressure for a flat round cover with an additional edge moment are made, the permissible pressure is to be determined from the formula &

 s −c  ] [ p =  ] [  σ ϕ  & ⋅ & ⋅ Dp  . $

375

;

2ig. &(

53 CALCULATION OF CONICAL SHELLS

.$. %es ign dia gram s and desi gn p ara mete rs .$.$. 2igs. &$-&; show design diagrams for the connection arrangements of conical shells .$.&. Desin prmeters .$.&.$. The design lengths of the transition parts are to be determined from the following formulae for conical shells 32igs. &$a, &$b and &$c5 $

= (.:

D cosα$

3 s$

− c5

&

D

= (.:

cosα &

B

3 s&

− c5

for conical shells 32igs. &&a and &&b5 $

= (.:

D cosα$

3 sM

− c5 B

for conical shells 32ig. &$d5 $

D

=

3 s$

cosα $

− c5 B

for cylindrical shell 32igs. &$b and &$c5 &

= (.:

D 3 s&

− c5 B

for toroidal transition 6ones 32igs. &&a and &&b5 &

= (.-

D cosα &

3 sM

− c5

B & = (.- D3 sM − c5 B

B

for cylindrical shells or pipe connections 3see 2ig. &$d5 &

= $.&-

D 3 s&

− c5 .

C"))+$")# ". #+# %$ *" )" + "&"* &)#") >")+#

 - connection of two conical shellsB b - connection of a conical shell to a cylindrical shellB c - connection of a conical shell to a cylindrical shell with a reinforcing ringB ! - connection of a conical shell to a cylindrical shell of smaller diameter 2ig. &$ C"))+$") ". #+# %  "&"* &)#") >")+

 - connection between two conical shellsB b - connection of a conical shell to a cylindrical shell 2ig. && ?#$ *'+)#")# ".  $")$ &)#") >")+

2ig. &+

C"))+$") ". #;+%-#''+&$ #+#

2ig. &7

C")$ #+ % #..+))/ &)/

2ig. &

C")$ +)* +# %  /&* #"+

 - end plate with toroidal transition 6oneB b - end plate with reinforcing ringB c - end plate without a toroidal transition 6one and reinforcing ring 2ig. &; .$.&.&. The desig n diameter of a smooth conic al shell is to be determined from the following formulae@ for conical shells without a toroidal transition 6one 32igs. &$a, &$b and &$c5 D; J D - $.7$sinα$B for conical shells with a toroidal transition 6one 32igs. &&a and &&b5 D; J D - & =r 3cosα2 - cosα$5 R (.:α$ sinα$>B for conical shells with a stepped change in the thicness of the wallB for the second and all subseuent parts, the internal diameter of the larger base should be taen as the design diameter D; of that particular part of the shell. .$.&.+. The design coefficien t for the strength of welded seams in the transition 6ones of shells is to be obtained from Table 7. Table 7

2orm of connection of shells

in accordance with clauses .+.+ .+.7

Internal pressure or tensile force

ϕp

= ϕ

M

D+#/) #.+ .$"& ."& #&+)/ ". %+*+* #+'# in accordance in accordance with with clauses clauses .+. .+.7 .+.: .+. .+.1 .7.

ϕp

= ϕ

M

ϕp

= ϕ

in accordance with clauses .+.; .7.;

ϕM W

ϕp J minV ϕpB

M

ϕp J ϕ

Internal pressure ϕp J minVϕpB or compressive force ]ending moment

ϕp J minVϕpB

.&. 2ie ld and c

ϕp

= ϕ

ϕ M W ϕ J minV ϕ B ϕ M W ϕ J minV ϕ B p p p p ϕp J $

ϕM W

ϕ M W ϕ J minV ϕ B ϕ M W ϕ J minV ϕ B p p p p ϕp J ϕ

ϕ M W ϕ J minV ϕ B p p

ondi tion s of a ppli cabi lit y of des

ign f ormul

ae

M

ϕM W

.&.$. The design formulae are to apply when the relationship between the thicness of an external shell and its diameter are within the limits

(.(($ ≤

s$ cos α$ D

≤ (.(-( .

It is not reuired that this condition should be fulfilled for a fully conical end plate 3 α$ Z :()5. .&.&. The design formulae given in clauses .+.&, .7.& and ..$. are to apply provided that the design temperatures do not exceed the values at which creep of the metal is taen into consideration, i.e., at temperatures when the permissible stress is determined only by the yield point and tensile strength 3strength limit5. If no precise information is available, the formulae are to be applied provided that the design temperature of the shell wall does not exceed +()* if it is made of carbon steel, 7()* if it is made of low-alloy steel, and &)* if it is made of austenitic steel. .&.+. The design formu lae in this Standard are not applicable for calculations for the strength of conical transition parts in positions where a 4acet is fastened to the casing. In that case, calculation is to be carried out in accordance with 89ST &;:. .&.7. The design formulae are not applicable if the distance between two neighbouring 4unctions of connections of shells is less than the total of the corresponding design lengths of the shells, or if the distance from the assembly connections to the supporting elements of the vessel 3other than sirt supports or support rings5 is less than double the design length of the shell in accordance with clause .$.&.$. .&.. The design formulae are to apply on condition that the construction length of the transition parts of the shells are not less than the design lengths $ and 2. If this conditioned is not fulfilled, it is necessary to mae a chec of the permissible pressure in which the following are substituted for s$ and s2@ for a connection of shells without a toroidal transition 6one     s$ ( = max  $D s$ B s ;  s& ( = max  & D s& B s   $ B  & B for connections of shells with a toroidal transition 6one when coefficient β is determined by means of formula 315.

s$ (

 = max   

$D $



sM B s ;  s & ( B

 = max  

&D &

 B

sM B s 

s;, s - are the actual thicnesses of the walls of the shells being connected 32igs. &$a, &$b, &$d and &&b5. .&.;. The design formulae for the connection assemblies of conical and cylindrical shells without a toroidal transition 6one are to apply provided that the fillet weld is formed with continuous double-sided fusion. .&.:. The manufactured thicness of the wall of a conical elemen t at the posit ion of connection of two shells, s$, s2 or sM, is always to be taen as being not less than thicness s; determined in accordanc e with clause .+.$ or clauses .+.& and .7.$ or clauses .7.& and ..$ for the relative loadings. The construction thicness of the wall of a cylindrical element at the position where two shells are 4oined shall not be less than the minimum wall thicness determined in accordance with the formulae in Section &. .&.. *alculation of the reinforcement to the openings of conical shells is to be carried out in accordance with 89ST &7:. .&.1. *alculation of the thicness of the walls of the transition parts of shells should be

carried out using either the method of successive approximations based on preliminary selection with subseuent checing for the selected values of

D s2

s$ − c

or

−c

s2

−c

or obtained directly from the diagrams. *alculation using the diagrams is to be carried out for conical transition 6ones which have α2 J (. If the permissible stresses of the materials of the transition 6ones differ from each other, the calculation by means of the diagram is to be carried out using the lesser of the values. The permissible pressure, axial force and bending moment for conical shells shall be taen as being the lower of the values obtain ed from the condition for the strength or stability of a smooth conical shell and from the condition for the strength of the transition part. .&.$(. The calculation is also applicable for sew-symmetrical shells which are connected to cylindrical shells. The design values for α$, D and D$ are to be taen as shown in 2ig. &7. .+. *oni cal she lls whic h are load ed wi th a p res sur e .+.$. Smooth conicl shells lo!e! with n internl e"cess press#re .+.$.$. The thicness of the wall is to be determined by means of the formula s; ≥ s;. R <,

35

where

s; . 

pD;

=

$

⋅

&ϕ p [σ ] − p cosα $

.

3;5

.+.$.&. The permissible internal excess pressure is to be determined from the formula

[ p ] = &[σ ]ϕ p 3 s ; − c5 D; cos α i

+ 3 s − c5 ;

.

3:5

.+.&. Smooth conicl shells which re lo!e! with n e"ternl press#re .+.&.$. The design formulae are to apply provided that α$ ≤ :(). .+.&.&. The wall thicness is to be determined in accordance with the formula given in clauses &.+.&.$ in the first approximat ion, and is subseuently to be checed using formula 35. hen maing the preliminary determination of the wall thicness, value s of l( and D( found from formulae 31$5 and 31&5 are to be taen as being the design values. .+.&.+. The permissible external pressure is to be determined by means of the formula

[ p] =

[ p] п

 [ p]  $ +  [ p ] 

&

п

(

,

35

where the permissible pressure from the condition for strength is

[ p] п =

&[σ ]ϕ p 3 s ; − c 5 D; + 3 s; − c5 cos α$ ,

315

and the permissible pressure obtained from the condition for stability within the limits of elasticity is

[ p] ( =

&(.I ⋅ $( − ; 5 D( $((3 s; − < 5   D  п N ⋅ +$ l(   (

& .-

.

31(5

The effec tive dimensions of the conical shell are to be determined by means of the formulae

l(

D(

=

D − D$ & sin α $

,

31$5

 D + D$ D = max B − (.+$3 D + D$ 5  & cosα$ cosα$

 D + D$ ⋅ t.α$  s; − < 

.

31&5

The value of the coefficient $ is to be determined from the formula@

)$

 = min$.(B 

1.7-

D( l(

D( $((( s;

 − c ) 

.

31+5

.+.+. Oonnection o/ shells which !o not h1e  toroi!l trnsition Pone 3see 2igs. &$a and &$b5 .+.+.$. The design formulae are to apply under the following conditions

α$ ≤ :()B ( ≤ α2  α$B 3s$ - c5 ≥ 3s2 - c5. If 3s$ - c5 ≥ 3s2 - c5, a chec calculation is to be made using the formula s$ - c J s2 - c. .+.+.&. The thicness of the wall is to be found from the formulae

s& 2

=

pDβ$ ⋅ $ &[σ ] & ϕ p − p cos α &

B

3175

s2 ≥ s2 R <.

315

In a case where a conical and a cylindrical shell are connected 3 2ig. &$b5, cosα2 J $. hen determining β$ coefficient β is to be cal culated usi ng formula 315 or is to be found in accordance with the diagram 32ig. &:5. *alculation of the wall thicness of the conical element of the transition 6one is to be carried out with the aid of the ratio of the wall thicnesses

 s −c     s −c $ &

s$

 s − c  ≥  s + c  s −c . $

&p

&

31;5

D/&' ."& *++&'))/ $"+..$+) %+) $$)/ + $;)+## ". + %# ". + &)#") >")+# ". #+#

2ig. &: .+.+.+. The shape coefficient is to be determined from the formula

β$ ≥ maxV(.B βW.

31:5

where β is determined by means of the formula

β

= ( .7

3t.α$ − t.α & 5 cos α &

D ⋅ s& − c

&

$ cos α &

 s −c  $ + " $ s& − c   s$ − c    + " & cos α$  s& − c 

− (.&-

. 315 2or connections of conical and cylindrical shells 3 α2 J (5 coefficient β may be determined from a diagram 32ig. &: or 2ig. &5. .+.+.7. The permissible internal excess or external pressure = > obtained from the condition for the strength of the transition part is to be determined by means of the formula

[ p] =

&[σ ] & ⋅ ϕ p 3 s & − c 5 Dβ$ + 3 s& − c5 cos α & ,

3115

where the coefficient β$ is determined in accordance with clause .+.+.+ .+.7. Oonnection o/  conicl shell to  rein/orcin rin 32igs. &$b and &5 .+.7.$. The design formulae are to be used provided that

α$ ≤ :() and when the ring is connected to a cylindrical shell 32ig, &$c5 that 3s$ - c5 ≥ 3s2 - c5. If 3s$ - c5  3s2 - c5, should be used In the chec calculation s$ - c J s2 - cB but if the connection is as shown in 2ig. &, only if there is no bending moment of the ring. D/&' ."& *++&'))/ + $"+..$+)

%+) ';)/ + $+$; $$")

2ig. & .+.7.&. The area of the transverse cross section of the reinforcing ring shall be determined using the formula when connection is as shown in 2ig. &$c

=;

=

pD &t.α$  β + (.&-  $ − =  I[σ ] ; ϕ p  β + (.&- 

,

3$((5

where β=

 &[σ ] ϕ  s −c =  − $  p  D . &

p

&

3$($5

*oefficient β is to be determined either by means of formula 31;5 or from the diagram 32ig. &5. If :; ≤ ( there is no reuirement for reinforcing by means of a stiffening ring where connection is as shown in 2ig. &

=;

pD & t.α $ I[σ ] ; ϕ p

=

.

3$(&5

In cases where there is a loading action from external pressure, an axial compressive force or a bending moment, the welded seam of the butt 4oint of the ring shall be welded with a continuous seam. hen determining the area of the transverse cross section :;, consideration should also be given to the cross section of the shell walls in the positions between the external welded seams of the ring and the shells. .+.7.+. The permissible internal excess or external pressure obtained from the condition for the strength of the transition part is to be determined using the formula when the connection is as shown in 2ig. &$c

[ p] =

&[σ ] & ⋅ ϕ p 3 s&

Dβ &

− c5 + 3 s − c5 , &

3$(+5

when the connection is as shown in 2ig. &

[ p] = =;

I[σ ] ; ⋅ ϕ p

D & t.α $

.

3$(75

.+.7.7. The general shape coefficient for the transition part is to be found from the formula

β2 J maxV(.B βFW,

3$(5

where

(.7

βo

=

&    s$ − c     $ + "   s − c   D  &  " s$ − c  t.α $ − )+ $ +    s& − c & cosα $  s& − c        &     s − c $  $ + "  s − c   s − c     &  " $ )& + $ +  s − c   & cosα$  &       .

3$(;5

The coefficients 2 and )E are to be determined by means of the formula )&

$.; =;

= 3s&

− c5

⋅

D3 s&

[σ ] ; ϕ p

− c5 [ σ ] & ϕ p

B E J (.&.

.+.7.. *hecing of the welded seam of the reinforcing ring

Σt ≥ A

7 =; D ,

3$(:5

where ΣtA - is the sum of all the effective widths of the load-bearing welded 4oints between the reinforcing ring and the shell 32ig. &$c5. here there is an intermittent weld, its actual width is to be reduced in the proportion of the length of the welded seam to the whole perimeter of the shell. The distance between the

ends of discontinuous welded seams shall be not more than eight times the thicness of the shell wall, and the sum of all the lengths of the welded seams shall be not less than one half of the length of the circumference of the ring. .+.. Oonnection o/ shells with toroi!l trnsition Pones 32ig. &&a and &&b5 .+..$. The design formulae are to apply when the following conditions are met

α$ ≤ :()B ( ≤ α2  α$B

(

≤

r D

< ( .+

.

.+..&. The thicness of the wall is to be determined from the formula ST ≥ sT. R <,

3$(5

where

sT . 

=

pDβ +

⋅

$

&ϕ p [σ ] − p cos α &

.

3$(15

D/&' ."& *++&'))/ + $"+..$+) T %+) $$)/ + $;)+## ". + %# ". &)#") #+#

2ig. &1 In the case of connection of a conical shell to a cylindrical shell 3 2ig. &&b5, cos α2 J l. The coefficient βE is to be determined from formula 3$$$5, and coefficients β and βM are to be found from formulae 315 and 3$$&5 or by means of the diagrams 32igs. &: and &15. .+..+. The permissible internal excess or external pressure obtained from the condition for the strength of the transition part is

[ p] =

&[σ ]ϕ p 3 sT − c 5 Dβ + + 3 sT − c 5 cos α & .

3$$(5

The coefficient βE is to be found by mean s of formula 3$$$5, and coefficients β ^ βM are to be determined using formulae 315 and 3$$&5 or from the diagrams 32igs. & and +(5. D/&' ."& *++&'))/ + $"+..$+) %+) $&&)/ " + $+$; $$")

2ig. +( .+..7. The shape coefficients are to be found from the following formulae@ coefficient βE from

βE J max V(.B β, βMW,

3$$$5

where β is to be determined from formula 315 with

 s −c    = $  s −c , $

Q J $ and

&

and coefficient βM obtained from

βT

=

$

r D ⋅ 3α$ − α & 5 (.(&I D sT − c $+ $ $ cosα$

+

cosα &

.

3$$&5

.+.;. Oonnection o/  pipe connection or internl c*lin!ricl shell to  conicl shell 32ig. &$d5. .+.;.$. The design formulae are to apply when the following condition is fulfilled

α$ ≤ :(). .+.;.&. The wall thicness is to be determined from the formula s2 ≥ s2p R c,

3$$+5

where

s& p

pDβ 7

=

&ϕ p [σ ] − p .

3$$75

*alculation of the wall thicness of the conical element of the transition part is to be carried out using the ratio of the wall thicnesses

s$

 s −c  s + c ≥   s −c . $

&p

3$$5

&

.+.;.+. The permissible internal excess or external pressure obtained from the condition for the strength of the transition part is to be determined using the formula

[ p] =

&[σ ] & ϕ p 3 s&

Dβ 7

− c5 + 3 s − c5 .

3$$;5

&

.+.;.7. The shape coefficient is to be determined from the formula

β9 J maxV$.(B βW,

3$$:5

where &

β J β R (.: when

βR

= ( .7

 s −c   ≥ $  s −c B

"

$

3$$5

&

t.α$

D s& − c

 s$ − c  s$ − c   s& − c  ( s& − c ) cosα$

"

 s −c  $ + " $ s& − c   + &

&

+ (,-

3$$15

when &

 s −c   < $  s −c .

"

$

&

In both cases the coefficient β can also be determined from the diagrams 3 2igs. +$ and +&5.

D/&' ."& *++&'))/ + $"+..$+) н, %+) $$)/ + $;)+## ". + %# ". + &)#") >")+# ". + #+#

2ig. +$

.+.:. entl* slopin en! pltes with  toroi!l trnsition Pone 3see 2ig. &;a5 .+.:.$. The design formulae are to apply for the action of an excess internal pressure when the following condition is satisfied

α$ Z :(). .+.:.&. The wall thicness is to be taen as being s′ ≥ min VmaxV s;B sTWB Sp′ R cWB s′p

= (.+3 D − r 5 α$

1(

3$&(5

p

[σ ]ϕ p

,

3$&$5

where s; is to be determined in accordance with clause .+.$ with D; J D and sT determined in accordance with clause .+..

D/&' ."& *++&'))/ + $"+..$+)

н

%+) $&&)/ " + $+$; $$")

2ig. +& .+.:.+. The permissible internal excess pressure is to be taen as being the larger of the value of



3 s′ − c 5

1(





[ p] = ϕ[ ]p σ    (.+3 D − r 5 α$ 

&

3$&&5

and the lesser of the values of = > determined in accordan ce with clauses .+.$ when s; J s′ and .+. when sM J s′. .+.. entl* slopin conicl en! plte with rein/orcin rin 3see 2ig. &;b5 .+..$. The design formulae are applicable for the effect of an internal excess pressure when the following conditions are fulfilled@

α$ Z :()B s′ = s;. .+..&. The thicness of the wall of the conical end plate is to be determined in accordance with clause .+.$.$ when D; J D. .+..+. The area of the transverse cross section of the reinforcing ring is to be determined in accordance with clause .+.7.&, in which 3s$ - <5 J ( should be used when determining β. .+..7. The permissible internal excess pressure is to be determined for the conical end plate in accordance with clause .+.$.& with D; J DB and for the reinforcing ring in accordance with clause .+.7.+ in wh ich 3 s$ - <5 J ( J ( should be used whe n determining β2. The calculation is to apply if the reuirements of clause .+.7.. are fulfilled. .+.1. r!#ll* slopin conicl en! plte witho#t  toroi!l trnsition Pone n! witho#t  rein/orcin rin 3see 2ig &;c5. .+.1.$. The design formulae are to apply for the effect of an internal excess pressure when

the following condition is fulfilled

α$ Z :(°. .+.1.&. The wall thicness is to be taen as being s′ ≥ min VmaxV s;B s$WB Sp′ R cWB

3$&+5

sp′ is to be determined using formula 3$$15 with r r J (B s; is to be determined in accordance with clause .+.$ with D; J DB s$ is to be determined in accordance with clause .+.+. .+.1.+. The permissible internal excess pressure is to be taen as being the larger of the value of = > determined from formula 3$&(5 when r J ( and the lesser of the values of = > found in accordance with clause .+.$ when s; J s′ and D; J D and in accordance with clause .+.+. .+.$(. entl* slopin conicl en! plte which is lo!e! with n e"ternl press#re .+.$(.$. The design form ulae are to apply for the effect of an external pressure when the following condition is fulfilled

α$ Z :(°. .+.$(.&. The permissible external pressure is to be determined from formula 3;5 , the permissible pressure within the limits of plasticity from formula 3:5 , and the permissible pressure within the limits of elasticity from the formula

[ p] ( =

7 (& n*

 s′ − c     D 

&

cos & α$

;

,

3$&75

where &

  (,$ξ +  = min(.+;B max ξ − 7 B(,$& ξ

=

B

D; &3 s ′ − c 5 cos α $ .

3$&5

3$&;5

.7. *oni cal she lls load ed wit h ax ial forc es .7.$. Smooth conicl shells which re lo!e! with n "il tensile /orce .7.$.$. The thicness of the wall is to be determined using the formula sO ≥ sO.p + c,

3$&:5

where sO.N

=

0 ⋅ $ πD$ϕ E [σ ] cos α$ .

3$&5

.7.$.&. The permissible tensile force is to be => = πD$3sO - c5ϕE=σ> cos α$.

3$&15

.7.&. Smooth conicl shells lo!e! with n "il compressi1e /orce .7.&.$. The design formula are to apply when the following condition is fulfilled

α$ ≤ :(°. .7.&.&. The permissible axial compressive force = > is to be determined from the formula

   [  ] = min    

 

[  ]H

 [  ]H  [  ](

$+  

  

&

D  B $ [  ]H  D 

  ,

3$+(5

where the permissible axial force obtained from the condition for strength is =>H = πD23sO - c5=σ> cos α$

3$+$5

and the permissible axial force obtained from the condition for stability within the limits of elasticity is &.-

−;

=>U J

+$( ⋅ $( ( ( D0 cos α$ ) & ⋅ $((3 s; − c 5  n*  D0 

D0

B

3$+&5

= (.1 D + (.$D$ cos α$

3$++5

.7.+. Oonnection o/ shells witho#t  toroi!l trnsition Pone 32igs. &$a and &$b5. .7.+.$. The design form ulae are to apply when the cond itions in clause .+.+.$ are fulfilled. .7.+.&. The permissible axial tensile or compressive force = > obtained from the condition for the strength of the transition part is to be determined by means of the formula 3 s&

[ 0 ] = πD

− c5[σ ] & ⋅ ϕ p cosα & β-

,

where the shape coefficient is β J max V$.(B 3&βR$.&5W.

3$+75 3$+5

The coefficient β is to be determined using formula 315, or from the diagram 3see 2ig. &5. .7.7. Oonnection o/  conicl n!  c*lin!ricl shell with  rein/orcin rin 32ig&$c5. .7.7.$. The design form ulae are to apply when the conditions in clause .+.7.$. are fulfilled. .7.7.&. The permissible axial tensile or compressive force = > obtained from the condition for the strength of the transition part is to be determined from the formula

[ 0 ] = πD

3 s&

− c5[σ ] & ⋅ ϕ p β;

,

3$+;5

where

β; J max V$.(B &β(W.

3$+5

The coefficient β( is to be determined by means of formula 3$(;5, in which E = -(.+ should be used. .7.7.+. *hecing of the welded seam of a reinforcing ring shall be carried out in accordance with clause .+.7.. .7.. Oonnection o/ shells with  torroi!l trnsition Pone 3figs. &&a and&&b5. .7..$. The design form ulae are to apply when the cond itions in clause .+..$ are fulfilled. .7..&. The permissible axial tensile or compressive force = > to satisfy the condition for the strength of the transition part is to be determined by means of the formula

[ 0 ] = πD

3 sE

− c 5[σ ]ϕ p cosα & β:

,

3$+5

where

β: J max V$.(B βE3&βR$.&5W.

3$+15

The coefficients β and βE are to be determined by means of formulae 315 and 3$$&5, or from the diagrams 32igs. & and +(5. .7.;. Oonnection o/  pipe connection or internl c*lin!ricl csin with  conicl shell 32ig. &$d5 .7.;.$. The design form ulae are to apply when the cond itions in clause .+.;.$ are fulfilled. .7.;.&. The permissible axial tensile or compressive force = > obtained from the condition for the strength of the transition part is to be determined by means of the formula

[ 0 ] = πD where

3 s&

− c5[σ ] & ⋅ ϕ p βI

,

3$7(5

β J max V$.(B 3&β_-$5W.

3$7$5

The shape coefficient β_ is to be determined by means of formulae 3$$5 or 3$$:5, or from the diagram 32ig. +&5. .. *oni cal she lls whic h are load ed wi th a b endi ng mom ent ..$. The permissible bending moment is to be calculated using the following formulae@ from the condition for strength D

[ 6] = [ ] p 0 7

,

3$7&5

where the design diameter Dp J D$ for a conical transition 6one 3 2ig. &+5, and = > is determined by means of formula 3$&15B from the condition for stability

[ 6 ]H

[6 ] =

 [ 6 ]H    [ 6 ]( 

&

$ + 

,

3$7+5

where

[ 6] [6 ]

H

=D [] 0

U

=D [] 0

7

+,-

0 0

H

,

U

3$775

,

3$75

and D is determined using formula 3$++5. The permissible axial forces are to be determined as follows@ => in accordance with clause .7.$.&B =2>H and =2>( in accordance with clause .7.&.&. ..&. Oonnection o/ shells ..&.$. The permissible bending moment from the condition for the strength of the transition part is to be determined from the formula D 7

[ 6] = [ ] 0

,

3$7;5

where the permissible axial force = > is to be dete rmined in acco rdance with clauses .7.+.&, .7.7.&, .7..& and .7.;.&. .;. *ombination of loadings

.;.$. Oon!itions /or pplicbilit* o/ the /orm#le If a conical shell which is loaded with a pressure, an axial force and a bending moment and the total of the euivalent pressures from these loadings determinedly means of the formulae p0

=

70

πD &p

p6

B

=

$;6

πD+p

,

3$7:5

maes up less than $(0 of the woring pressure for the relevant design diameter, the conical shell should be calculated for the effect of the pressure only. .;.&. Oombine! ction o/ lo!s hen checing strength or stability for the combined actions of the loadings, minus p is to be substituted for the design external pressure in formula 3$75 and 3$(5B and when checing for the effect of axial compressive force, minus  is to be substituted. The bending moment 6 is always to be used with a plus sign. .;.&.$. Smooth conical shells In the case of the effect of external pressure, it is necessary to chec the stability condition using the formula p

0

6

- [ p] - [ 0 ] R [ 6 $]

≤

.

3$75

In addition, a chec must be carried out for stability under the individual loadings

 ≤ =p>B  ≤ =>B 6 ≤ =6>.

3$715

The permissible loadings =p>, = > and = 6> are to be determined in accordance with clauses .+.&.+, .7.&.& and ..$. The chec is to be carried out even if the conditions in clause .;.$ are not fulfilled for only one of the design diameters of a conical shell. hen there is internal pressure, it should be taen that p = ( in formula 3$75. .;.&.&. Transition parts of conical shells In addition to checing for the conditions of strength under the individual loadings in accordance with formulae 3$715, it is necessary to chec that the following condition is fulfilled p

0

6

[ p ] R [ 0 ] R [ 6$ ]

≤

,

3$(5

where =p>, => and =6> are the permissible loadings for the transition part of the shell. / chec is to be carried out if the conditions given in clause .;.$ are not fulfilled when Dp = D.

(UD'V $ Wblitor* Table  P+&'##<+ #&+##+# ."& $&<") )* "%-" #++# %esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &( +(( +( +: 7(( 7$( 7&( 7+( 77( 7( 7;( 7:( 7(

, #
KSt+

upto&( $73$7(5 $713$71(5 $73$7(5 $7&3$7&(5 $+$3$+$(5 $$3$$(5 $(3$((5 1+31+(5 3(5 $3$(5 :3:(5 :$?3:$(5 -

$7(3$7((5 $+73$+7(5 $+$3$+$(5 $&;3$&;(5 $&(3$&((5 $(3$((5 131(5 1+31+(5 3(5 $3$(5 :3:(5 :$?3:$(5 -

$1;3$1;(5 $::3$::(5 $:$3$:$(5 $;3$;(5 $;&3$;&(5 $$3$$(5 $7(3$7((5 $++3$++(5 $&&3$&&(5 $(73$(7(5 1&31&(5 ;3;(5 :3:(5 :$3:$(5 ;73;7(5 ;3;(5 +3+(5

$+3$+(5 $;(3$;((5 $73$7(5 $73$7(5 $73$7(5 $+73$+7(5 $&+3$&+(5 $$;3$$;(5 $(3$((5 $(73$(7(5 1&31&(5 ;3;(5 :3:(5 :$3:$(5 ;73;7(5 ;3;(5 +3+(5

$7:3$7:(5 $7&3$7&(5 $+13$+1(5 $+;3$+;(5 $+&3$+&(5 $$13$$1(5 $(;3$(;(5 131(5 1&31&(5 ;3;(5 (3((5 :3:(5 ;:3;:(5 ;$3;$(5 3(5 71371(5 7;?37;(5

$+(3$+((5 $&3$&(5 $&&3$&&(5 $$3$$(5 $$&3$$&(5 $((3$(((5 3(5 &3&(5 ::3::(5 :3:(5 :&3:&(5 ;3;(5 ;(3;((5 +3+(5 7:37:(5 7&37&(5 +:3+:(5

$(3$((5 $;(3$;((5 $73$7(5 $73$7(5 $73$7(5 $+73$+7(5 $&+3$&+(5 $(3$((5 1&31&(5 ;3;(5 (3((5 :3:(5 ;:3;:(5 ;$3;$(5 3(5 71371(5 7;??37;(5

$:8$S $:8S $(8&SI $+3$+(5 $;(3$;((5 $73$7(5 $73$7(5 $73$7(5 $+73$+7(5 $&+3$&+(5 $$;3$$;(5 $(3$((5 $(73$(7(5 1&31&(5 ;3;(5 :3:(5 :$3:$(5 ;73;7(5 ;3;(5 +3+(5

X 2or design wall temperature of 7&)*. X X 2or design wall temperature of 7:)*.

otes@ $. hen the design temperatures are less than &()*, the permissible stresses are to be taen as being the same as when the design temperature is &()* provided that it is permissible to use the materials for the particular temperature. &. 2or intermediate values of design temperatures of walls, the permissible stress is to be determined by linear interpolation with the results being rounded down to the nearest (. #
Table ; P+&'##<+ #&+##+# ."& $&++-&+##) $&"'' #++ , #
%esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &(

$&`h#

$&#`h

$`h#

$`h#

$`h#-"

$7:3$7:(5 $7;.3$7;5 $7;3$7;(5 $73$7(5 $73$7(5

$7:3$7:(5 $7;.3$7;5 $7;3$7;(5 $73$7(5 $73$7(5

$3$(5 $+3$+(5 $&.3$&5 $&3$&(5 $&3$&(5

$7;3$7;(5 $7$3$7$(5 $+3$+(5 $+73$+7(5 $&:3$&:(5

&7(3&7((5 &+3&+(5 &+(3&+((5 &&3&&(5 &&(3&&((5

+(( +( +: 7(( 7$( 7&( 7+( 77( 7( 7;( 7:( 7( 71( (( $( &( +( 7( ( ;( :( ( 1( ;((

$7$3$7$(5 $+:3$+:(5 $+3$+(5 $+&3$+&(5 $+(3$+((5 $&13$&1(5 $&:3$&:(5 $&;3$&;(5 $&73$&7(5 $&&3$&&(5 $$:3$$:(5 $$73$$7(5 $(3$((5 1;31;(5 &3&(5 ;13;1(5 ;(3;((5 (3((5 7$37$(5 ++3++(5 -

$7$3$7$(5 $+:3$+:(5 $+3$+(5 $+&3$+&(5 $+(3$+((5 $&13$&1(5 $&:3$&:(5 $&;3$&;(5 $&73$&7(5 $&&3$&&(5 $$:3$$:(5 $$73$$7(5 $(3$((5 1;31;(5 &3&(5 ;13;1(5 :3:(5 7:37:(5 -

$7:3$7:(5 $7&3$7&(5 $7(3$7((5 $+:3$+:(5 $+;3$+;(5 $+3$+(5 $+73$+7(5 $+&3$+&(5 $+$3$+$(5 $&:3$&:(5 $&&3$&&(5 $$:3$$:(5 $(:3$(:(5 11311(5 737(5 :73:7(5 ;:3;:(5 :3:(5 71371(5 7$37$(5 -

$&(3$&((5 $$73$$7(5 $$(3$$((5 $(3$((5 $(+3$(+(5 $($3$($(5 11311(5 1;31;(5 17317(5 1$31$(5 131(5 ;3;(5 +3+(5 :13:1(5 :&3:&(5 ;;3;;(5 ;(3;((5 737(5 7:37:(5 7(37((5 +3+(5 +(3+((5 &3&(5 &3&(5

&$(3&$((5 &((3&(((5 $(3$((5 $:(3$:((5 $;(3$;((5 $(3$((5 $7(3$7((5 $+3$+(5 $+(3$+((5 $&;3$&;(5 $&&3$&&(5 $$3$$(5 $$73$$7(5 $(3$((5 1:31:(5 3(5 :&3:&(5 3(5 &3&(5 737(5 7(37((5 +73+7(5 +(3+((5 &3&(5

otes@ $. hen design temperatures are less than &()*, the permissible stresses are to be taen as being the same as for &()* provided that it is permissible to use the material at the particular temperature. &. 2or intermediate design temperatures of the wall, the permissible stresses are to be determined by linear interpolation with the results being rounded down to the nearest (. #, +. It is recommended that steels of Types $&#`h, $&`h# and $ `h# should not be used when design temperatures are less than &(()*.

Table : P+&'##<+ #&+##+# ."& /-+'+&&+, +-&+##) )* $"&&"#")-&+##) #++# ". + #+)$ $##

, #
$(3$((5 $:+3$:+(5 $:$3$:$(5 $:$3$:$(5 $;:3$;:(5 $713$71(5 $7+3$7+(5 $7$3$7$(5 $7(3$7((5 -

$;(3$;((5 $++3$++(5 $&3$&(5 $&(3$&((5 $$3$$(5 $$&3$$&(5 $(3$((5 $(:3$(:(5 $(:3$(:(5 $(:3$(:(5 $(:3$(:(5 $(:3$(:(5 $(:3$(:(5 $(:3$(:(5 -

$+3$+(5 $7(3$7((5 $+(3$+((5 $&(3$&((5 $$+3$$+(5 $(+3$(+(5 $($3$($(5 1(31((5 :3:(5 +3+(5 &3&(5 $3$(5 $3$(5 (3((5 -

$;3$;(5 $;3$;(5 $73$7(5 $7(3$7((5 $+&3$+&(5 $&+3$&+(5 $$+3$$+(5 $(3$((5 $(+3$(+(5 $(&3$(&(5 $($3$($(5 $((.3$((5 $((3$(((5 11311(5 131(5 1:.31:5 1:31:(5 1;31;(5 131(5

$73$7(5 $:73$:7(5 $;3$;(5 $;(3$;((5 $73$7(5 $73$7(5 $773$77(5 $7(3$7((5 $+:3$+:(5 $+;3$+;(5 $+3$+(5 $+73$+7(5 $++3$++(5 $+&3$+&(5 $+$3$+$(5 $+(3$+((5 $&13$&1(5 $&3$&(5 $&:3$&:(5

$( &( +( 7( ( ;( :( ( 1( ;(( ;$( ;&( ;+( ;7( ;( ;;( ;:( ;( ;1(

--

--

--

17317(5 :13:1(5 :13:1(5 :3:(5 :;3:;(5 :+3:+(5 ;13;1(5 ;3;(5 ;$3;$(5 :3:(5 -

$&;3$&;(5 $&3$&(5 $&73$&7(5 $$$3$$$(5 $$$3$$$(5 $($3$($(5 1:31:(5 1(31((5 $3$(5 :73:7(5 ;3;(5 ;&3;&(5 :3:(5 &3&(5 737(5 737(5 7&37&(5 +3+(5 +73+7(5

:((

-

-

-

-

+(3+((5

otes@ $. hen design temperatures are less than &()*, the permissible stresses are to be taen as being the same as for &()* provided that it is permissible to use the material at the particular temperature. &. 2or intermediate design wall temperatures, the permissible stress is to be determined by interpolation between the two neares t values shown in the Table with the results being rounded down to the nearest (. #
 R ?p (.&     &7((   ,

where RXp0.& - is the yield point of the material of the rolled steel determined in accordance with 89ST 171B for rolled steel of Type (+`hlll the permis sible stresses are to be multiplied by (.. . 2or forgings and rolled metal of steel Type (`hll9T, the permissible stresses given in Table : for temperatures up to ()* are to be multiplied by (.1 . ;. 2or forgings of steel Type (+`hl:$7#+, the permissible stresses given in Table : are to be multiplied by (.1. :. 2or forgings of steel Type (+`hlll, the permissible stresses given in Table : are to be multiplied by (.1B for rolled metal of steel Type (+`hlll, the permissible stresses given in Table : are to be multiplied by (..  . 2or pipe of steel Type (+`h&$&$#78] 3I-+5, the permissible stresses given in Table : are to be multiplied by (.. 1. 2or forgings of steel Type (+`h&$&$#78] 3I-+5, the permissible stresses given in Table : are to be multiplied by the ratio R ?p (.& &-(

 R ?p (.&     &-((   ,

where RXp0.& - is the yield point of the material of the forging determined in accordance with 89ST &(7 3by correlation5.

Table  P+&'##<+ &+##)$+# ."& /-+'+&&+, +-&+##) )* $"&&"#")-&+##) #++# ". + #+)$ )* #+)$-.+&&+ $##

%esign , #
otes@ $. hen design temperatures are less than &()*, the permissible stresses are to be taen as being the same as for &()* provided that it is permissible to use the material at the particular temperature. &. 2or intermediate design temperatures of the wall, the permissible stress is to be determined by linear interpolation with the results being rounded down to the nearest (. #
(UD'V 2 or in/ormtion M+$)$ $&$+&#$#@ ."& $&<") )* "%-" #++# - T<+# 1 )* 2, ."& $&++-&+##) $&"'' #++ T<+#  )* 4, ."& / +'+&&+, +-&+##) )* $"&&"#")-&+##) #++# ". + #+)$ )* #+)$-.+&&+ $## T<+# 5 )* 6

Table 1 &

%esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &( +(( +( +: 7(( 7$( 7&(

%esign value of yield point !e, <\ 3g forceA[m 5 for steels of Types (18&S, $;8S &(, &(` Thicness, mm $(8&, $( (18& over&( upto+& over+& upto$;(

KSt+

upto&( &(3&((5 &+(3&+((5 &&73&&7(5 &&+3&&+(5 $1:3$1:(5 $:+3$:+(5 $;:3$;:(5 $;73$;7(5 -

&$(3&$((5 &($3&($(5 $1:3$1:(5 $13$1(5 $(3$((5 $;&3$;&(5 $7:3$7:(5 $7(3$7((5 -

+((3+(((5 &;.3&;5 &;.3&;5 &7:.3&7:5 &7+3&7+(5 &&;.3&&;5 &$(3&$((5 $11.3$115 $+3$+(5 -

&(3&((5 &7(3&7((5 &+$3&+$(5 &&&3&&&(5 &$3&$(5 &($3&($(5 $3$(5 $:73$:7(5 $3$(5 $;3$;(5 $+3$+(5

&&(3&&((5 &$+3&$+(5 &(13&(1(5 &(73&(7(5 $13$1(5 $:13$:1(5 $13$1(5 $7:3$7:(5 -

$13$1(5 $3$(5 $+3$+(5 $::3$::(5 $;3$;(5 $(3$((5 $+&3$+&(5 $&+3$&+(5 -

&:(3&:((5 &7(3&7((5 &+$3&+$(5 &&&3&&&(5 &$3&$(5 &($3&($(5 $3$(5 $;&3$;&(5 -

$:8$S, $:8S, $(8&SI &(3&((5 &7(3&7((5 &+$3&+$(5 &&&3&&&(5 &$3&$(5 &($3&($(5 $3$(5 $:73$:7(5 $3$(5 $;3$;(5 $+3$+(5

Table $( %esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &( +(( +( +:

&

%esign value of tensile strength ! т, <\ 3g forceA[m 5 for steels of Types KSt+ (18&S,$;8S &(,&(` $(8&, Thicness, mm upto&( 7;(37;((5 7+37+(5 7;(37;((5 (3((5 $(3$((5 &(3&((5 7(37((5 7(37((5

over&( +(3+((5 +;(3+;((5 +1(3+1((5 7&(37&((5 7+37+(5 77(377((5 7&(37&((5 7(&37(&(5

upto+&

$(

over+&

7:(37:((5 7&37&(5 7+(37+((5 7+137+1(5 7773777(5 77377(5 77$377$(5 7&37&(5

upto$;(

77(377((5 +3+(5 7+(37+((5 7+137+1(5 7773777(5 77377(5 77$377$(5 7&37&(5

7$(37$((5 +(3+((5 7&37&(5 7;(37;((5 7;(37;((5 7;(37;((5 7+(37+((5 7$(37$((5

+7(3+7((5 +$(3+$((5 +7(3+7((5 +&3+&(5 7((37(((5 +:73+:7(5 +;(3+;((5 ++(3++((5

(18&, $:8S, $(8&SI, $(8&S$ 77(377((5 +3+(5 7+(37+((5 7+137+1(5 7773777(5 77377(5 77$377$(5 7&37&(5

Table $$ %esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &( +(( +( +: 7(( 7$( 7&(

%esign value of yield point Rp(.&, <\ 3g forceA[m&5 for steels of Types $&#`h

$&`h#

$`h#

$`h

$`h-"

&&(3&&((5 &$13&$1(5 &$3&$(5 &$:.3&$:5 &$:.3&$:5 &$&3&$&(5 &(;3&(;(5 &(&3&(&(5 $13$1(5 $13$1(5 $173$17(5

&&(3&&((5 &$13&$1(5 &$3&$(5 &$:.3&$:5 &$:.3&$:5 &$&3&$&(5 &(;3&(;(5 &(&3&(&(5 $13$1(5 $13$1(5 $173$17(5

&++3&++(5 &+(3&+((5 &&13&&1(5 &&3&&(5 &&3&&(5 &&(3&&((5 &$+3&$+(5 &$(3&$((5 &(3&((5 &(73&(7(5 &(&3&(&(5

&&(3&&((5 &$(3&$((5 &(:3&(:(5 &($3&($(5 $1(3$1((5 $(3$((5 $:$3$:$(5 $;73$;7(5 $3$(5 $3$(5 $&3$&(5

7((37(((5 +&.3+&5 +73+7(5 ++:.3++:5 ++(3++((5 +$3+$(5 +((3+(((5 &:(3&:((5 &3&(5 &7(3&7((5 &&3&&(5

Table $& %esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &( +(( +( +: 7(( 7$( 7&(

%esign value of tensile strength ! т, <\ 3g forceA[m&5 for steels of Types $&`h

$&`h

$`h

$`h

$`h-"

7(37((5 77(377((5 7+737+7(5 7+(37+((5 77(377((5 77377(5 7+:37+:(5 7&:37&:(5 7$37$(5 7$+37$+(5 7$(37$((5

7(37((5 77(377((5 7+737+7(5 7+(37+((5 7+:37+:(5 77377(5 77&377&(5 7+;37+;(5 7&;37&;(5 7&737&7(5 7&$37&$(5

7(37((5 77(377((5 7+737+7(5 7+(37+((5 7+:37+:(5 77377(5 77&377&(5 7+;37+;(5 7&;37&;(5 7&737&7(5 7&$37&$(5

7((37(((5 +(3+((5 +3+(5 ++(3++((5 +&(3+&((5 +$3+$(5 +$73+$7(5 +$&3+$&(5 +$(3+$((5 +(;3+(;(5 +((3+(((5

;((3;(((5 :&3:&(5 3(5 +3+(5 &(3&((5 (+3(+(5 71&371&(5 77377(5 7:&37:&(5 7;37;(5 7;&37;&(5

Table $+ %esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &( +(( +( +: 7((

%esign value of yield point Rp(.&, <\ 3g forceA[m&5 for steels of Types (`h$8& (:`h$+/8&( 3(-+5 3*hS-7;5

+(3+((5 +&3+&(5 +$73+$7(5 +((3+(((5 &:3&:(5 &:73&:7(5 -

+(3+((5 &;(3&;((5 &+(3&+((5 &((3&(((5 $1(3$1((5 $(3$((5 $:(3$:((5 $;3$;(5 $;(3$;((5

(&`h&&S; 3M<-:175

&((3&(((5 $;(3$;((5 $(3$((5 $+3$+(5 $&3$&(5 $$3$$(5 -

$`h$$&S7Yu (`h&&;, (;`h&%, 3MI-;75 (`h&$;& (+`h&%

+(3+((5 ++(3++((5 +$(3+$((5 +((3+(((5 &(3&((5 &:(3&:((5 -

+(3+((5 +((3+(((5 &(3&1((5 &+3&+(5 &(3&((5 &7(3&7((5 -

&&(3&&((5 &(:3&(:(5 $13$1(5 $;3$;(5 $:3$:(5 $;3$;(5 $;(3$;((5 $:.3$:5 $3$(5

Table $7 %esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &( +(( +( +: 7((

%esign value of tensile strength ! т, <\ 3g forceA[m&5 for steels of Types (`h$8& 3(-+5

(:`h$+/8&( 3*hS-7;5

(&`h&&S; 3M<-:175

$`h$$&S7Y u 3M<-;75

(;`h&%, (+`h&%

;((3;(((5 +3+(5 71371(5 737(5 7$37$(5 +:3+:(5 -

;:(3;:((5 (3((5 &(3&((5 71(371((5 737(5 7(37((5 7;37;(5 737(5 7(37((5

(3((5 ((3(((5 7(37((5 7;37;(5 7(37((5 77(377((5 -

:((3:(((5 ;7(3;7((5 ;$(3;$((5 (3((5 :(3:((5 :(3:((5 -

(3((5 &:.3&:5 $&.3$&5 ((3(((5 71(371((5 7&.37&5 7:37:(5 7:737:7(5 7:(37:((5

Table $ %esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &( +(( +( +: 7(( 7$( 7&( 7+( 77( 7( 7;( 7:( 7( 71( (( $( &( +(

%esign value of yield point Rp$.(, <\ 3g forceA[m&5 for steels of Types $&`h$$(, $&`h$$&, $(`h$:$+&, $(`h$:$++

(`h$$(, (`h$$&, (`h$:$+&, (`h$:$+

(+`h&$&$78]

(+`h$$$

(+`h$:$7+

&:;3&:;(5 &;$3&;$(5 &&3&&(5 &7(3&7((5 &+$3&+$(5 &&&3&&&(5 &$;3&$;(5 &$(3&$((5 &(.3&(5 &(73&(7(5 &(&.3&(&5 &($3&($(5 $11.3$115 $13$1(5 $1;.3$1;5 $13$1(5 $1+.3$1+5 $1&3$1&(5 $1(.3$1(5 $13$1(5 $:.3$:5 $;3$;(5

&&3&&(5 &+73&+7(5 &&&3&&&(5 &$(3&$((5 $13$1(5 $7.3$75 $;1.3$;15 $;&3$;&(5 $7.3$75 $+3$+(5 $$.3$$5 $(.:3$(5 $(3$((5 $7.3$75 $7:3$7:(5 $7;3$7;(5 $7.3$75 $773$77(5 $7&.3$7&5 $7$3$7$(5 $+1.3$+15 $+3$+(5

&:(3&:((5 &;(3&;((5 &:3&:(5 &:3&:(5 &(3&((5 &&+3&&+(5 &$3&$(5 &$&3&$&(5 &$(3&$((5 -

&7(3&7((5 &((3&(((5 $:.3$:5 $(3$((5 $:+3$:+(5 $;3$;(5 $;&3$;&(5 $;(3$;((5 $;(3$;((5 $;(3$;((5 $;(3$;((5 $;(3$;((5 $;(3$;((5 $;(3$;((5 -

&+(3&+((5 &$(3&$((5 $13$1(5 $(3$((5 $:(3$:((5 $3$(5 $&3$&(5 $+3$+(5 $+(3$+((5 $&3$&(5 $&+3$&+(5 $&&3$&&(5 $&$3$&$(5 $&(3$&((5 -

ote. The yield point for forgings, rolled steel and pipe when the temperature is &()* should be taen as being@ for forgings of steels Types $&`hl$(T, $(`$:$+#&T and $(`hl:$+#+T R p&($.( ( o/ sheet steel ) B $ .& R p&($.( ( o/ sheet steel ) B $.(for forgings and rolled steel of Type (`hl$(T for rolled steel of Types $&`hl$(T, $(`hl:$+#&T and $(`hl:$+#+T $.$- R p (.& ( o/ rolle! steel ) &(

R p&($.( ( o/ sheet steel ) $.$$

for forgings of steel Types (+`hl:i7#+ and (+`hlll -

B

&(

R p$.( ( o/ sheet steel ) B $.&for rolled steel of Type (+`hl$$ R p&($.( ( o/ sheet steel ) for pipe of steel Type (+`h&$&$#78] 3I-+5 for forgings of steel Type (+`h&$&$#78] 3I-+5 R

&( p (.&

$.$7 $.(I

R p&((.&

B

3forgings5

where is the yield point of the material of the forgings in accordance with 89ST &(7 3by correlation5.

Table $; %esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &( +(( +( +: 7(( 7$( 7&( 7+( 77( 7( 7;( 7:( 7( 71( (( $( &( +(

%esign value of yield point Rp(.& , <\ 3g forceA[m&5 for steels of Types $&`h$$(, $&`h$$&, $(`h$:$+&, $(`h$:$++

(`h$$(, (`h$$&T, (`h$:$+&, (`h$:$+#+T

(+`h&$&$78]

(+`h$$$

(+`h$:$7#+

&7(3&7((5 &&3&&(5 &$13&$1(5 &$(3&$((5 &(73&(7(5 $13$1(5 $1(3$1((5 $;3$;(5 $$3$$(5 $(3$((5 $(3$((5 $:13$:1(5 $::3$::(5 $:;3$:;(5 $:73$:7(5 $:+3$:+(5 $:+3$:+(5 $:$3$:$(5 $:(3$:((5 $;3$;(5 $;3$;(5 $;:3$;:(5

&$(?3&$((5 $13$1(5 $(3$((5 $:+3$:+(5 $;3$;(5 $(3$((5 $+:3$+:(5 $++3$++(5 $&13$&1(5 $&3$&(5 $&3$&(5 $&:3$&:(5 $&;3$&;(5 $&3$&(5 $&3$&(5 $&73$&7(5 $&+3$&+(5 $&&3$&&(5 $&&3$&&(5 $&(3$&((5 $$13$$1(5 $$13$$1(5

&(3&((5 &7(3&7((5 &+3&+(5 &+3&+(5 &+&3&+&(5 &(3&((5 $113$11(5 $13$1(5 $1$3$1$(5 -

&((3&(((5 $;(3$;((5 $(3$((5 $7(3$7((5 $+3$+(5 $+(3$+((5 $&:3$&:(5 $&3$&(5 $&&.3$&&5 $&$.3$&$5 $&$3$&$(5 $&(.3$&(5 $&(3$&((5 $&(3$&((5 -

&((3&(((5 $(3$((5 $;3$;(5 $(3$((5 $7(3$7((5 $&;3$&;(5 $$3$$(5 $(3$((5 $((3$(((5 131(5 1:.31:5 1:31:(5 1;31;(5 131(5 -

? 2or steels (`hl:l+#&T, (`$:$#+T, the yield point when the temperature is&()* is to be eual to &(( #
 R ?p (.&     &7((   ,

where RXp0.& - is the yield point of the material of the rolled steel determined in accordance with 89ST 171. +. 2or forgings and rolled steel of Type (`h$$( the yield points given in Table $; are to be multiplied by (.1. 7. 2or forgings of steel Type (+`h$:$7+ the yield points given in Table $; are to be multiplied by (.1. . 2or forg ings of steel Type (+`h$$$ the yield point s given in Table $; are to be multiplied by (.1B for rolled steel of Type (+`h$$$ the yield point is to be multiplied by (.. ;. 2or pipe of steel Type (+`h&$&$78] 3I-+5 the yield points given in Table $; are to be multiplied by (.. :. 2or forgings of steel Type (+`h&l&$#78] 3I-+5, the yield points given in Table $; are to be multiplied by the relationship R ?p (.& &-(

 R ?p (.&     &-((   ,

where RXp0.& is the yield point of the materials of the forgings determined in accordance with

89ST &(7 3by correlation5. Table $: %esign temperature of wall of vessel or apparatus, ° &( $(( $( &(( &( +(( +( +: 7(( 7$( 7&( 7+( 77( 7( 7;( 7:( 7( 71( (( $( &( +(

%esign value of tensile strength ! т, <\ 3g forceA[m &5 for steels of Types

(+`h&$&$78]

(3((5 7(37((5 +3+(5 +3+(5 +73+7(5 &(3&((5 $3$(5 $:3$:(5 $;3$;(5 -

(`h$$(, $&`h$$(, (`h&&;, (`h$$&, $&`h$$&, (+`h$:$7+ (+`h$$$ (`h&$;& (`h$:$+&, $(`h$:$+&, (`h$:$+ $(`h$:$++

;((3;(((5 +3+(5 (3((5 $3$(5 (+3(+(5 ((3(((5 -

? 2or design temperature of the wall of ()* .

((3(((5 7:737:7(5 7+37+(5 7+&37+&(5 7$&37$&(5 +1&3+1&(5 +:;3+:;(5 +;3+;(5 +;(3+;((5 +3+(5 +;3+;(5 +73+7(5 +&3+&(5 +(3+((5 -

&(3&((5 7(37((5 7++37++(5 7$37$(5 7(37((5 +1:3+1:(5 +173+17(5 +1&3+1&(5 +1(3+1((5 +3+(5 +;3+;(5 +73+7(5 +&3+&(5 +(3+((5 -

&(3&((5 7(37((5 737(5 7+(37+((5 7&737&7(5 7$:37$:(5 7(37((5 7(37((5 7(&37(&(5 7((37(((5 +13+1(5 +1;3+1;(5 +173+17(5 +1&3+1&(5 +1(3+1((5 +3+(5 +;3+;(5 +3+(5 ++3++(5 +$3+$(5 +(3+((5 +:7?3+:7(5

7(37((5 ((3(((5 7:37:(5 7(37((5 77+377+(5 77(377((5 7+37+(5 7+:37+:(5 7+;37+;(5 7+737+7(5 7+&37+&(5 7+$37+$(5 7+(37+((5 7&37&(5 7&;37&;(5 7&737&7(5 7&&37&&(5 7&$37&$(5 7&(37&((5 7$37$(5 7$;37$;(5 7$&?37$&(5

(UD'V E /or in/ormtion Table $ C"+..$+) ". )+& +)#") Type of Steel KSt+, &(, &(` (18&S, $;8S, $:8S, $:8$S $(8&S$, $(8& $&`h#, $&#`h, $`h#, $`h#, $`h#-" (`&&;T,(`h&$;#&T $&`h$$(T, $&`h$$&T, (+`#:$7#+, $(`$:$+#&T $(`.h$:$+#+T, (`#$(T (`#$&T, (+`h$$$ (`#:$+#&T,(`h$:l#+T (+`h&$&$#78] (;`&#%T, (+`&#%T (`h$8]&T

%esign value of coefficient α×$(;, °-$, when temperature, )*, is &(-$(( &(-&(( &(-+(( &(-7(( &(-(( $$.; $&.; $+.$ $+.; $7.$ $+.( $$.1

$7.( $&.;

$.+ $+.&

$;.$ $+.:

$;.& $7.(

1.;

$+.

$;.(

$;.(

$;.

$;.; $7.1

$:.( $.:

$.( $;.;

$.( $:.+

$.( $:.

$.+ $&.+

$.1 $+.$

$;. $7.7

$;.1 $7.7

$:.+ $.+

(UD'V 9 Wblitor* D+#/) +# ". + '"*# ". +#$

$ - carbon and low-alloy steelsB 2 - creep-resisting and corrosion-resistant steelsB E - high-temperature, heat-resistant and corrosion-resistant austenitic steels Table $1 Steel

#odulus of elasticity $( 5 <\ 3$(-; 5 g forceA[m&5 when temperature, ), is &( $(( $( &(( &( +(( +( 7(( 7( (( ;( ;(( ;( :((

*arbon and low-alloy $.11 $.1$ $.; $.$ $.:; $.:$ $.;7 $. $.7( steels *reep-resisting and &.$ &.$ &.( $.1 $.1 $.1( $.7 $.: $.:$ $.;+ $.7 $.7( corrosion-resistant chrome steels igh-temperature and &.(( &.(( $.11 $.1: $.17 $.1( $. $.( $.:7 $.;: $.;( $.& $.7+ $.+& heat-resistant austenitic steels

(UD'V @ Wblitor* Table &( S.+ .$"&# ."& + #&+)/ ". %+*+* :")#

2orm of welded seam

]utt or Tee-shaped with continuous fusion from both sides, welded automatically or semi-automatically ]utt with re-welding of the root of the seam or Tee-shaped with weld continuous through the seam, welded manually ]utt, accessible for welding from one side only and having a metal bacing plate held against the root of the base metal of the root of the weld for the full length of the seam during welding Tee-shaped with a constructional clearance between the welded parts ]utt, welded automatically or semiautomatically from one side using flux or ceramic bacing ]uttweldedmanuallyfromoneside

Kalue of safety factor for strength of welded seams Dength of monitored Dength of monitored welds of total length is welds of total length is $((0? $( to (0?

(.1

$.(

(.1

$.(

(.1

(.1

(.

(.

(.;

(.1

(.

(.;

? The extent of monitoring is determined by technical specifications for manufacture and the regulations of the "SS! State #ining Industry Inspectorate.

(UD'V G /or in/ormtion Table &$ T+&'# #+* ) # S)*&* )* +& #'<"#

Term /rea of transverse cross section of stiffening ring, mm & 3[m&5 %esign lengths of transition parts of shells, mm 3[m5 /ctual lengths of the transition parts of shells, mm 3[m5 on-dimensional coefficients %istance between two ad4acent stiffening rings, mm 3[m5 Dength of chords of openings in end plates, mm 3[m5 Sum of additions to design thicnesses of walls, mm 3[m5 /ddition to compensate for corrosion and erosion, mm 3[m5 /ddition to compensate for negative tolerance, mm 3[m5 /ddition for technological process used, mm 3[m5 Internal diameter of vessel or apparatus, mm 3[m5 Mxternal diameter of perimeter of end plate or cover having a thicness of s$, mm 3[m5 /verage diameter of gaset, mm 3[m5 Mffective diameter of conical shell when there is external pressure, mm 3[m5 Mffective diameter of conical shell when there is axial compression and bending, mm 3[m5 %esign diameter of smooth conical shell, mm 3[m5 %esign diameter of end plate 3cover5 and conical shell, mm 3[m5 Mxternal diameter of vessel or apparatus, and also of diameter of smaller base of conical shell, mm 3[m5 Smallest diameter of external part of cover with reduced thicness, mm 3[m5 %iameter of bolt perimeter, mm 3[m5 %iameter of opening in end plate or cover, mm 3[m5 %iameter of openings in end plates, mm 3[m5 #odulus of longitudinal elasticity at design temperature, #
Symbol :O $, & $, & )$, )&, )+, )7, ), );, ): b bi 3i = $, &, + ...n5 < <$ <& <+ D DF D[.H D( D DO DN D$ D& D+ ! !i 3i = $, &, + ...n5 ( 



K 8 H =2> =2>U

Term
Symbol =2>H =2>U$

=2>U&

B h$ h2 ' 'O

'p & &$, &&, &+, &7, &, &;, &: ? &o &p &C  l l( le lHN l$

l& l+ 6 =6> =6>( =6>H

Term Safety factor for tensile 3strength limit5 Safety factor for rupture stress Safety factor for limiting creep stress Safety factor for yield point Safety factor for stability %esign internal excess or external pressure, #
Symbol пF п пH пE пL  

 p#

#
=p> =p>( =p>H =p>$

=p>$(

=p>$H

&

forceA[m 5 internal excess or external pressure determined
=p>&

=8>( =8>H 8 8 =

8> R RK RH R R&( R(.&

R p&((.&

Rm

Term design temperature, #
Symbol

!adius of groove, mm 3j5 Mxternal radius of flange of torospherical end plate, mm 3[m5 *onstruction thicness of wall of shell, mm 3cm5 *onstruction thicness of wall of conical shell, mm 3[m5 Thicness of cover at sealing position, mm 3[m5 %esign thicness of wall of shell, mm 3[m5 %esign thicness of wall of conical shell, mm 3[m5 %esign thicness of wall of end plate 3cover5 or transition part of shell, mm 3[m5 %esign thicness of wall of transition part of shell, mm 3[m5 *onstruction thicness of wall of toroidal transition 6one of conical shell, mm 3[m5 *onstruction thicness of wall of gently sloping conical end plate, mm 3[m5 %esign thicness of wall of transition part with a toroidal transition 6one, mm 3[m5 %esign thicness of gently sloping end plate, mm 3[m5 Mffective thicness of wall of transition part of shells, mm 3[m5 *onstruction thicness of wall of end plates 3cover5 or transition part of conical shell, mm 3[m5 *onstruction thicness of wall of transition part of shell, mm 3[m5 Thicness of cover outside seal, mm 3[m5 Thicness of part of end plate of reduced thicness in the position of circular groove, mm 3[m5 idth of transverse cross section of stiffening ring at the place where it is welded to the shell, mm 3[m5 ]earing width of circular welded seam, mm 3[m5 alf of angle of flare at crown of conical shell, degrees Shape coefficients

rв r$ s sO sH sN sO.N s$N

*orrection coefficient to permissible stress

[σ ]$ [σ ] &

!atio of permissible stresses 2lexibility of element
RmH$0

@

R$.(A$(



R$.(

r

s&N sE s′ sE.N sN′ s$UB s&U s$ s& s+ s7 t tA

α% α$% α2

β$ , β& , β+ , β7 . β , β; , β: , β , β, βo, βE, β_, β/ η χ λ =σ> =σ>&( =σ>O

Term #
Symbol =σ>$B =σ>&

Σ! i ϕ ϕP, ϕQ ϕO ϕρ ϕN ϕE ϕα

ϕ$ ϕ& ϕ+

CONTENTS

$. 8MM!/D !MX"I!M#MTS..............................................................................................& $.$. %esign temperature...........................................................................................................& $.&. oring, design, and test pressure...................................................................................& $.+. %esign forces and moments..............................................................................................& $.7.
REFERENCE DATE 13 DEVELOPED AND SU?MITTED < + M)#& ". C+'$ )* O M$)+ ?*)/ COLLA?ORATORS V3I3 R$;", *andidate of Technical SciencesB S3I3 #')"#;, *andidate of Technical Sciences 3pro4ect managers5B N3M3 S'#")", %octor of Technical SciencesB G3V3 M'")", *andidate of Technical SciencesB V3D3 ?<)#;, V3F3 B&+,*andidate of Technical SciencesB S3M3 B+", *andidate of Technical SciencesB L3S3 P&;), I3V3 S;&);", I3E3 +*+, A3B3 B>)+#", 3S3 M+*+*+, *andidate of Technical

Sciences 23 APPROVED AND INTRODUCED INTO OPERATION < R+#"") ". + S+ C"''++ ". + USSR ."& S)*&*# ". 18305389, N"3 1264 3 R+$+# 14249-80 43 T+ #)*&* . '++# ST SEV 596-86, ST SEV 597-77, ST SEV 109-78, ST SEV 1040-88, ST SEV 1041-88 53 REFERENCE NORMATIVE AND TECHNICAL DOCUMENTS

%esignation of ormative %ocument to which !eference is #ade 89ST 17189ST &7:-$ 89ST &7:;-$ 89ST &(7-$ 89ST &1-+ 89ST &;:-+