SIST EN 13445-3:2002/A10:2008
(Amendment)Unfired pressure vessels - Part 3: Design
Unfired pressure vessels - Part 3: Design
Amendment to flanges Annex G
Unbefeuerte Druckbehälter - Teil 3: Konstruktion
Récipients sous pression non soumis à la flamme - Partie 3: Conception
Neogrevane tlačne posode - 3. del: Konstruiranje
General Information
Relations
Standards Content (Sample)
SLOVENSKI STANDARD
SIST EN 13445-3:2002/A10:2008
01-junij-2008
1HRJUHYDQHWODþQHSRVRGHGHO .RQVWUXLUDQMH
Unfired pressure vessels - Part 3: Design
Unbefeuerte Druckbehälter - Teil 3: Konstruktion
Récipients sous pression non soumis à la flamme - Partie 3: Conception
Ta slovenski standard je istoveten z: EN 13445-3:2002/A10:2008
ICS:
23.020.30
SIST EN 13445-3:2002/A10:2008 en,fr,de
2003-01.Slovenski inštitut za standardizacijo. Razmnoževanje celote ali delov tega standarda ni dovoljeno.
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EUROPEAN STANDARD
EN 13445-3:2002/A10
NORME EUROPÉENNE
EUROPÄISCHE NORM
March 2008
ICS 23.020.30
English Version
Unfired pressure vessels - Part 3: Design
Récipients sous pression non soumis à la flamme - Partie Unbefeuerte Druckbehälter - Teil 3: Konstruktion
3: Conception
This amendment A10 modifies the European Standard EN 13445-3:2002; it was approved by CEN on 27 November 2006.
CEN members are bound to comply with the CEN/CENELEC Internal Regulations which stipulate the conditions for inclusion of this
amendment into the relevant national standard without any alteration. Up-to-date lists and bibliographical references concerning such
national standards may be obtained on application to the CEN Management Centre or to any CEN member.
This amendment exists in three official versions (English, French, German). A version in any other language made by translation under the
responsibility of a CEN member into its own language and notified to the CEN Management Centre has the same status as the official
versions.
CEN members are the national standards bodies of Austria, Belgium, Bulgaria, Cyprus, Czech Republic, Denmark, Estonia, Finland,
France, Germany, Greece, Hungary, Iceland, Ireland, Italy, Latvia, Lithuania, Luxembourg, Malta, Netherlands, Norway, Poland, Portugal,
Romania, Slovakia, Slovenia, Spain, Sweden, Switzerland and United Kingdom.
EUROPEAN COMMITTEE FOR STANDARDIZATION
COMITÉ EUROPÉEN DE NORMALISATION
EUROPÄISCHES KOMITEE FÜR NORMUNG
Management Centre: rue de Stassart, 36 B-1050 Brussels
© 2008 CEN All rights of exploitation in any form and by any means reserved Ref. No. EN 13445-3:2002/A10:2008: E
worldwide for CEN national Members.
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EN 13445-3:2002/A10:2007 (E)
Contents Page
Foreword.3
Annex GA (informative) Alternative design rules for flanges and gasketed flange connections.4
GA.1 Purpose.4
GA.2 Specific definitions.4
GA.3 Specific symbols and abbreviations .5
GA.3.1 Use of figures (General) .5
GA.3.2 Subscripts .5
GA.3.3 Symbols.6
GA.4 General.22
GA.4.1 Conditions of applicability.22
GA.4.2 Mechanical model.23
GA.4.3 Calculation method.24
GA.5 Parameters.24
GA.5.0 General.24
GA.5.1 Flange parameters.25
GA.5.2 Bolt and washers parameters.28
GA.5.3 Gasket parameters.29
GA.5.4 Lever arms.32
GA.6 Forces.33
GA.6.0 General.33
GA.6.1 Loads .33
GA.6.2 Compliance of the joint .34
GA.6.3 Elastic deformations .34
GA.6.4 Actual gasket forces.35
GA.6.5 Required gasket force .35
GA.6.6 Forces in assembly condition (ΙΙΙΙ = 0) .37
GA.6.7 Forces in subsequent conditions (ΙΙ = 1, 2, 3 …).38
ΙΙ
GA.7 Load limits.38
GA.7.0 General.38
GA.7.1 Bolts.39
GA.7.2 Bolt load contact pressure and washers .39
GA.7.3 Gasket.41
GA.7.4 Integral flange, stub or collar .42
GA.7.5 Blind flange .43
GA.7.6 Loose flange with stub or collar.44
GA.8 Supplements to the method .45
GA.8.1 Dimensions of standard metric bolts .45
GA.8.2 Bolting-up methods.46
GA.8.3 Flange rotations.47
GA.9 Gasket properties.48
GA.9.1 Basic explanations .48
GA.9.2 Tables for gasket properties.51
GA.10 Bibliography.63
2
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EN 13445-3:2002/A10:2007 (E)
Foreword
This document (EN 13445-3:2002/A10:2008) has been prepared by Technical Committee CEN/TC 54
“Unfired pressure vessels”, the secretariat of which is held by BSI.
This Amendment to the European Standard EN 13445-3:2002 shall be given the status of a national standard,
either by publication of an identical text or by endorsement, at the latest by September 2008, and conflicting
national standards shall be withdrawn at the latest by September 2008.
Attention is drawn to the possibility that some of the elements of this document may be the subject of patent
rights. CEN [and/or CENELEC] shall not be held responsible for identifying any or all such patent rights.
This document has been prepared under a mandate given to CEN by the European Commission and the
European Free Trade Association, and supports essential requirements of EU Directive 97/23/EC.
For relationship with EU Directive 97/23/EC, see informative Annex ZA, which is an integral part of this
document.
The document includes the text of the amendment itself. The corrected pages of EN 13445-3 will be delivered
as issue 30 of the standard.
According to the CEN/CENELEC Internal Regulations, the national standards organizations of the following
countries are bound to implement this European Standard: Austria, Belgium, Bulgaria, Cyprus, Czech
Republic, Denmark, Estonia, Finland, France, Germany, Greece, Hungary, Iceland, Ireland, Italy, Latvia,
Lithuania, Luxembourg, Malta, Netherlands, Norway, Poland, Portugal, Romania, Slovakia, Slovenia, Spain,
Sweden, Switzerland and the United Kingdom.
Add the following Annex GA:
3
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EN 13445-3:2002/A10:2007 (E)
Annex GA
(informative)
Alternative design rules for flanges and gasketed flange connections
GA.1 Purpose
This annex provides a calculation method for bolted, gasketed circular flange joints. It is applicable to flanges
and bolted domed ends, and it is an alternative to the methods in Clauses 11 and 12.
Its purpose is to ensure structural integrity and leak tightness for an assembly comprising two flanges, bolts
and a gasket. Flange loadings are shown in Figure GA.3-1. Different types of bolts and gaskets are shown in
Figures GA.3-2 to GA.3-3.
This annex does not consider bolted tubesheet flange connections with two gaskets and/or two different fluid
pressures. It also does not consider flange joints with integral tubesheet-flange-connections and such with two
shells connected to a flange (jacketed vessels or pipes).
NOTE This informative Annex is a further development of the Alternative method contained in Annex G. It may be
used particularly in the case of bolted flanged connections of vessels containing gases or vapours, for which it is
necessary to fix a maximum allowable leak rate in order to protect the environment. The gasket factors contained in
Tables GA.9.1 to GA.9.6 are partially based on research results, and partially on theoretical considerations. Use of such
factors should be made with caution, with the agreement - whenever possible - of the gasket manufacturer concerned.
GA.2 Specific definitions
The following terms and definitions apply in addition to those in 11.2.
GA.2.1
integral flange
flange either integral with or welded to the shell, see Figures GA.3-4 to GA.3-8
GA.2.2
blind flange
flat closure connected by bolts, see Figure GA.3-9
GA.2.3
loose flange
separate flange-ring abutting a stub or collar, see Figure GA.3-10
GA.2.4
hub
axial extension of a flange-ring, usual connecting flange-ring to shell, see Figures GA.3-4 and GA.3-5
GA.2.5
collar or stub
abutment for a loose flange, see Figure GA.3-10
GA.2.6
load condition
application of a set of applied simultaneous loads; designated by the identifier Ι
4
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EN 13445-3:2002/A10:2007 (E)
GA.2.7
load change
change of load condition
GA.2.8
assembly condition
as defined in 11.2 and designated by Ι = 0 in this annex
GA.2.9
subsequent condition
load condition subsequent to the assembly condition, e.g. working condition, test condition, conditions arising
during start-up and shut-down, designated by Ι = 1, 2, 3…
GA.2.10
external loads
forces and/or moments applied to the joint by attached equipment, e.g. weight or thermal expansion of pipes
GA.2.11
compliance
inverse of the stiffness of the assembly, symbol Y, units mm/N
GA.2.12
flexibility modulus
inverse of the stiffness modulus of a component, excluding the elastic constants of the material; axial; symbol
3
X, units 1/mm; rotational: symbol Z; units 1/mm
GA.3 Specific symbols and abbreviations
GA.3.1 Use of figures (General)
Figures GA.3-1 to GA.3-10 serve only to illustrate the notation. They are not intended to give all the detail of
different designs. They do not illustrate all possible flange types for which the method is valid.
GA.3.2 Subscripts
Subscripts to indicate parts are always large (uppercase). Subscripts to indicate properties (behaviour) may
be small (lowercase). Subscripts written in brackets (Ι and/or J) may be waived.
A for Assembly load condition, Additional (F , M )
A A
B for Bolt
C for Contact (bolt/nut/washer/flange)
E for Equivalent or effective values (cylinder, gasket pressure)
F for Flange
G for Gasket
H for Hub
for
Ι Load condition identifier, written in brackets, (Ι = 0, 1, 2, 3 …)
J for Identification for parts of the one or other side of the flange connection, or for
cases to determine tightness parameters, written in bracket, (J = 1 or 2)
L for Loose flange, Loading
M for Moment
5
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EN 13445-3:2002/A10:2007 (E)
P for Pressure (fluid pressure)
Q for Net axial force due to pressure
R for Net axial force due to external loads (Resultant)
S for Shell, Shaft, Shear, Subsequent load condition
U for Unloading
W for Washer
X for Flange weakest cross section
X, Y, for Subscript for components of additional loads (forces, moments)
Z
for Symbol for change or difference
∆
act for Actual (real, for several times calculated values the last calculated)
av for Average
d for Design, desired
e for Effective
i for Interim (calculated, not finally)
max for Maximum (also: mx)
min for Minimum
nom for Nominal
req for Required
t for Theoretical
0 for
Zero load condition (Ι = 0, see subscript Ι), also other use
GA.3.3 Symbols
Units are given in square brackets; [-] indicates that the quantity is dimensionless (dimension [1]).
Subscripts to the symbols are written as follows:
First subscripts specify the structural element (e.g. F for flange or G for gasket) and the kind of quantity
(e.g. 3 for diameter 3 or E for effective).
If an element exists more than once (e.g. two different flanges, numbered by J = 1 and J = 2), their
distinction may be specified by an additional subscript (number in brackets); however it is not necessarily
given.
The last subscript specifies the load condition (Ι). If it is written, then always in brackets; however it is not
necessarily given. In some cases the both last subscripts look as follows: (J, Ι).
2
A is the effective total cross-section area [mm ] of all bolts, Equation (GA.5-43);
B
2
A , A is the radial cross-section area [mm ] of flange ring, loose flange, Equations (GA.5-7), (GA.5-
F L
11) and (GA.5-14);
2
A , A is the gasket area [mm ], effective, theoretical, Equations (GA.5-67) and (GA.5-56);
Ge Gt
2
A is the effective area [mm ] for the axial fluid-pressure force, Equation (GA.5-69);
Q
b is the width [mm] of the chamfer or radius on a loose flange, Figure GA.3-10;
0
6
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EN 13445-3:2002/A10:2007 (E)
b , b are contact widths [mm], bolt side, flange side, see GA.5.2.3 and GA.7.2.2;
CB CF
b is the contact width common for bolt and flange side of a washer [mm], Equation (GA.5-49);
CC
b , b is the effective width [mm] of a flange, loose flange, Equations (GA.5-5) to (GA.5-12);
F L
b , b , b , b are gasket widths [mm], effective, interim, plastic, theoretical, Table GA.5-1,
Ge Gi Gp Gt
Equations (GA.5-54), (GA.5-65) and (GA.5-66);
b is the effective width [mm] of a washer, Equation (GA.5-45);
W
C is the deformation modulus [MPa] for loading of the gasket at zero compressive stress
0
(Q = 0), see GA.9.2;
C is the rate of change of the deformation modulus [-] for loading of the gasket with
1
compressive stress (Q > 0), see GA.9.2;
c , c , c , c , c , c , are correction factors [-], Equations (GA.5-26), (GA.5-58), (GA.7-1) to (GA.7-3),
A B C E F G
c , c (GA.7-5), (GA.7-10), (GA.7-12), (GA.7-24) and (GA.7-30) to (GA.7-33);
M S
d is the inside diameter of the flange ring [mm] or outside diameter of the central part of a blind
0
flange (with thickness e ). In no case it is greater than the inside diameter of the gasket [mm],
0
Figures GA.3-4 to GA.3-10;
d is the average diameter of hub, thin end [mm], Figures GA.3-4 and GA.3-5;
1
d is the average diameter of hub, thick end [mm], Figures GA.3-4 and GA.3-5;
2
d is the bolt hold circle diameter [mm], Figures GA.3-4 to GA.3-10;
3
d is the flange outside diameter [mm], Figures GA.3-4 to GA.3-10;
4
d is the diameter of bolt holes [mm], Figures GA.3-4 to GA.3-10, Equations (GA.5-2) and
5
(GA.5-3);
d is the inside diameter of a loose flange [mm], Figure GA.3-10;
6
d is the diameter of the position of the reaction between a loose flange and a stub or collar
7
[mm], Figure GA.3-1, Equations (GA.5-75) to (GA.5-81);
d is the outside diameter of stub or collar [mm], Figure GA.3-10;
8
d is the diameter of a central hole in a blind flange [mm], Figure GA.3-9;
9
d , d , d are bolt diameters (nominal, effective, waisted) [mm], Figure GA.3-2;
B0 Be BS
d is the maximum possible outside contact diameter [mm] between bolt head or nut and
B4
flange or washer; Equation (GA.5-48) and Table GA.8-1;
d , d are extreme contact diameters (inside, outside) [mm], see GA.5.2.3 and GA.7.2.2;
C1 C2
d , d are average contact diameters [mm], bolt side, flange side, see GA.5.2.3 and GA.7.2.2;
CB CF
d , d , d are gasket contact diameters (real contact at curved surfaces, theoretical inside,
G0 G1 G2
theoretical outside) [mm], Figure GA.3-3;
d , d , d are gasket calculation diameters (effective, interim, theoretical) [mm], Figure GA.3-4,
Ge Gi Gt
Table GA.5-1;
d , d , d , d , d , d are average diameters of a part or section (designated by the subscript) [mm],
E F L S W X
Equations (GA.5-6) to (GA.5-22) and (GA.7-26) to (GA.7-46);
d , d are washer diameters (inside, outside) [mm], Figure GA.3-1, Equations (GA.5-45) to
W1 W2
(GA.5-52);
D is the deformation modulus [MPa] for loading of the gasket, see GA.9.1;
G
E is the modulus of elasticity [MPa] for unloading/reloading of the gasket, see GA.9.1;
G
E , E E , E , E are the moduli of elasticity [MPa] for bolt, flange, loose flange, shell, washer;
B F, L S W
e is the wall thickness of central plate of blind flange (inside d ) [mm], Figure GA.3-9;
0 0
7
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EN 13445-3:2002/A10:2007 (E)
e is the minimum wall thickness at thin end of hub [mm], Figures GA.3-4, GA.3-5;
1
e is the wall thickness at thick end of hub [mm], Figures GA.3-4, GA.3-5;
2
e , e is the wall thickness of equivalent cylinder for load limit and flexibility calculations
D E
respectively [mm], Equations (GA.5-16) and (GA.5-17);
e , e is the effective axial thickness of flange, loose flange [mm], Equations (GA.5-7) to (GA.5-
F L
14);
e is the gasket axial thickness [mm], Figure GA.3-3;
G
e is the theoretical thickness; normally this is the thickness given on drawing or
Gt
specification; for an exception see NOTE in GA.5.3.1; see also Figure GA.3-3;
e is the thickness actual after all load conditions, calculated for F = 0;
G(A) G(A)
e is the thickness (height) of a nut [mm], Figure GA.3-1, Equation (GA.7-2);
N
e is the portion of the flange thickness subject to radial pressure loading [mm],
P
Figures GA.3-4 to GA.3-10;
e is the portion of the flange thickness not subject to radial pressure loading [mm],
Q
Figures GA.3-4 to GA.3-10;
e is the shell thickness [mm], Figures GA.3-4 to GA.3-10;
S
e is the washer thickness [mm], Figure GA.3-1, Equation (GA.7-14);
W
e is the flange thickness at the weakest section [mm], Figure GA.3-9, Equation (GA.7-46);
X
F is the external axial force [N], Figure GA.3-1, tensile force positive, compressive force
A
negative, F = F ;
A Z
F is the total force of all bolts [N];
B
F is the gasket force [N];
G
is the minimum gasket force in assembly condition that guarantees that the required
F
G(0),∆
gasket force is maintained in all subsequent conditions [N], Equation (GA.6-24);
F is the axial fluid pressure force [N], Equation (GA.6-1);
Q
F is the axial force resulting from F and M [N], Equation (GA.6-4);
R A B
F is the resulting shearing force [N] at the gasket, Equation (GA.6-2);
S
F , F , F are the additional forces [N] in the directions X, Y, Z, Figure GA.3-1 and GA.6.1.2;
X Y Z
f , f , f , f , f , f are the nominal design stresses [MPa] for bolts, flange, loose flange, nuts, shell,
B F L N S W
washers;
h , h , h are lever arms (gasket, hub, loose flange) [mm], Figure GA.3-1, and Equations (GA.5-
G H L
72) to (GA.5-84);
h , h , h , h , h are lever arm corrections [mm], Equations (GA.5-27) to (GA.5-30), (GA.5-38), (GA.5-
P Q R S T
39) and (GA.5-70);
h is the maximum lever arm variation for loose flanges [mm], Equations (GA.5-80) to
V
(GA.5-84);
Ι is the load condition identifier [-], for assembly condition Ι = 0, for subsequent conditions
Ι = 1, 2, 3 …;
j , j are sign numbers for moment, shear force (+1 or –1) [-], Equations (GA.7-34) and
M S
GA.7-35);
K is the modulus of elasticity [MPa] for unloading/reloading of the gasket at zero
0
compressive stress (Q = 0), see GA.9.1;
K is the rate of change of the modulus of elasticity [-] for unloading/reloading of the gasket
1
with compressive stress (Q > 0), see GA.9.1;
8
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EN 13445-3:2002/A10:2007 (E)
k , k , k , k are correction factors [-], Equations (GA.5-31) to (GA.5-34), (GA.7-36) and (GA.7-37);
Q R M S
l , I are bolt axial dimensions [mm], Figure GA.3-2 and Equations (GA.5-44) and (GA.6-6);
B S
l is the length of hub [mm], Figures GA.3-4 and GA.3-5;
H
M1, M2, MJ is an exponent for tightness calculations [-], case 1, case 2, general (J = 1, 2), see GA.6
and GA.9;
M is the external bending moment [Nmm], Equation (GA.6-3);
B
M is the bolt assembly torque [Nmm], Equation (GA.8-5);
t
M , M , M are the additional moments [Nmm] with the vector directions X, Y, Z, related to the mid-
X Y Z
plane of the gasket, Figure GA.3-1 and GA.6.1.2;
N1, N2, NJ is an exponent for tightness calculations [-], case 1, case 2, general (J = 1, 2), see GA.6
and GA.9;
N is the number of times that the joint is re-made during the service life of the flanges,
R
Equation (GA.6-34); without of influence on results for N ≤ 10;
R
n is the number of bolts [-], Equations (GA.5-1), (GA.5-4) and GA.5.2;
B
P is the fluid pressure [MPa], internal pressure positive, external negative, see GA.6.1;
p is pitch between bolts [mm], Equation (GA.5-1);
B
p is pitch of the bolt-thread [mm], Table GA.8-1;
t
Q, Q is the mean existing effective compressive stress in gasket [MPa] in load condition No.Ι;
(Ι)
Q is the minimum required compressive stress in gasket [MPa] for assembly condition, see
A,min
GA.6.5;
Q , Q , is a gasket material parameter for tightness [MPa], defining required values for
A0 A1
Q , Q assemblage, case 0, case 1, case 2, general (J = 1, 2), see GA.6 and GA.9;
A2 AJ
Q is the mean existing compressive stress in gasket [MPa], effective in load condition No. Ι
E (Ι)
for deformation with prevented sliding on surfaces, Equations (GA.5-59) to (GA.5-63);
Q is the minimum required compressive stress in gasket [MPa] for subsequent load
S,min
conditions, see GA.6.5;
Q is the resistance of the gasket against destruction or damage [MPa], excluding support
R
by friction on the contact flange surfaces, including safety margins, which are the same
for all load conditions, see GA.9.1;
q is a parameter [-] to determine the contact widths at washers, see GA.7.2.2;
r is the radius of curvature in gasket cross section [mm], Figure GA.3-3;
2
S is the strength of a washer [Nmm], Equation (GA.7-14); (S corresponds to a resistance W);
W
(TP) is the tightness parameter [not dimensionless], defined in GA.9.1.2;
special values are (TP) and (TP) (maximum values for the cases 1 and 2);
1mx 2mx
t , t , t , t , t , t are design temperatures (average for the part designated by the subscript) [°C],
B F G L S W
Equation (GA.6-5);
t is the temperature of the joint at bolting-up [°C], usually +20 °C;
0
U
is an axial deformation of the gasket [-], used for explanation in GA.9.1, U = ∆e /e ;
G G
W , W , W are resistances (of the part or section designated by the subscript) [Nmm], Equations
F L X
(GA.7-26), (GA.7-44), (GA.7-46) and (GA.7-48);
W is a special resistance of stub or collar [Nmm], supported by the resistance of the gasket
Q
Q , Equation (GA.7-50);
R
is an auxiliary parameter [-] to find the optimum load transfer position for loose flange
x
(Ι)
9
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EN 13445-3:2002/A10:2007 (E)
with stub or collar, see GA.5.4.2 and GA.7.6.3;
X , X ,X are axial flexibility moduli of bolts, gasket, washer [1/mm], Equations (GA.5-44),
B G W
(GA.5-53) and (GA.5-68);
Y , Y , Y , Y are axial compliances of the joint [mm/N] corresponding to loads F , F , F , F ,
B G Q R B G Q R
Equations (GA.6-8) to (GA.6-11);
3
Z , Z are rotational flexibility moduli of flange, loose flange [1/mm ], Equations (GA.5-35),
F L
(GA.5-36) and (GA.5-40) to (GA.5-42);
-1
are average thermal expansion coefficients [K ], averaged between t and t , t , t ,
α , α , α , α , α
0 B F G
B F G L W
t , t ;
L W
are intermediate working variables [-], Equations (GA.5-15), (GA.5-23) to (GA.5-25),
β, γ, δ, ϑ , κ,
(GA.5-79), (GA.7-28) and (GA.7-29);
λ
is the change of the gasket thickness [mm] during bolt tightening in assemblage (up to
∆e
G(0)
the end of the load condition No. 0), Equation (GA.5-63);
is the change of the gasket thickness [mm] after assemblage up to the end of load
∆e
G(Ι)
condition No. Ι, Equation (GA.5-63);
is the overall axial thermal deformation [mm] relative to assemblage in load condition
∆U
T(Ι)
No. Ι, Equation (GA.6-5);
is the overall axial elastic and thermal deformation [mm] at the gasket relative to
∆U
G(Ι)
assemblage in load condition No. Ι, Equation (GA.6-12);
are the scatter values of the initial bolt load [-] for n bolts and 1 bolt, above and below
ε , ε , ε , ε -
n+ n- 1+ 1 B
the nominal value respectively, see GA.8.2;
Θ , Θ is the rotation of flange, loose flange, due to an applied moment [-],Equations (GA.8-7)
F L
and (GA.8-8);
is the coefficient of friction at the bolts, at the gasket [-], see GA.8, GA.9;
µ , µ
B G
is a diameter ratio for blind flanges [-], Equation (GA.5-37);
ρ
are load ratios (of the part or section designated by the subscript) [-], Equations
Φ , Φ , Φ , Φ ,
B C F G
(GA.7-1), (GA.7-4), (GA.7-7) to (GA.7-9), (GA.7-23), (GA.7-25) and (GA.7-43) to
Φ , Φ , Φ
L W X
(GA.7-49);
is the angle of inclination of a sealing face [rad or deg], Figure GA.3-3, Table GA.5-1;
ϕ
G
is the angle of inclination of the connected shell [rad or deg], Figures GA.3-6, GA.3-7,
ϕ
S
with sign convention;
Ψ is the load ratio of flange ring due to radial force [-], Equation (GA.7-38);
Ψ is the particular value of Ψ[-], Table GA.7-1.
Z
10
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EN 13445-3:2002/A10:2007 (E)
F
A
d
W2(1)
P
d h
E(1) H(1)
e
E
M
M Z
Y
M
X
F
Z
F
F
Y
X
F
G
F
B
d
3e
d h
Ge G
F
F
G
B
F
Y
F
X
F
Z d
7
M
X
M M
d
Y Z h
E(2) h
L
H(2)
d
W2(2)
P
F
A
Figure GA.3-1 — Applied loads and lever arms (Integral flange and loose flange)
11
e e e e e
e
W(2) L(2) F(2) F(1) W(1)
N
---------------------- Page: 12 ----------------------
EN 13445-3:2002/A10:2007 (E)
d
d d d
BO
BO BO B0
d
B2
d
B3
Z
d
BS
d
BS
a) Hexagon headed bolt b) Stud bolt c) Waisted stud d) View on 'Z'
Figure GA.3-2 — Bolt details
12
l
S
l
B
l
B
l
S
l l
5t B
---------------------- Page: 13 ----------------------
EN 13445-3:2002/A10:2007 (E)
d d d
Gt Gt Gt
b /2 b /2 b /2
Gt Gt Gt
b /2
b /2 b /2
Gt
Gt Gt
j
d b d d
G1 Gt G1 G1
d
d d
G0
G2 G0
d
d
G2
G2
a) b) c)
d
d d
Gt
Gt Gt
b /2 b /2
Ge Ge
j
j
d b d b
G1 Gt G1 Gt
d b
G1 Gt
d d
G2 G2
d
G2
d) e) f)
Figure GA.3-3 — Gasket details
13
r2
r2
G
G
r2
r2
G
e
G
e
G
e
G e
G
e
G
e
G
...
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