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STANDARDS OF
THE EXPANSION JOINT
MANUFACTURERS
ASSOCIATION INC
NINTH EDITION
EXPANSION JOINT MANUFACTURERS ASSOCIATION INC.
25 NORTH BROADWAY TARRYTOWN NY 10591
RICHARD BYRNE SECRETARY
TEL: 914 332 0040
FAX: 914 332 1541
E MAIL: [email protected]
www.ejma.org
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STA DARDS OFTHE EXPANSION JOINT MANUFACTURERS ASSOCIATION. INC.
~ I M R S H I P LIST
EXPANSION JOL \ T L-I.NUFACTURERS
ASSOCIATION H C
American BOA. Inc. - Cumming.
GA
Badger Industries. Inc. - Zelienople. PA
Expansion Joint Systems. inc. - Santee. CA
FJexider S.r.I.- Torino. Italy
Hyspan Precision Products. loc.- Chula Vista. CA
Idrosapiens. 5 r l Leini Torino), Italy
Microflex -
Omond
Beach. FL
Senior Flexonics. Inc.. Pathway Division -
New
Braunfels. TX
SFZ
- Lyon. France
U.S. Bellows. Inc. - Houston. TX
WahlcoMetroflex. Il1c Lewis[QI1. ME
\ It Leomann. GmbH - Pforzheirn.
Genmmy
CURRENT
TECHNICAL COMMITTEE MEMBERS
EXPANSION JO I
T
MANUFACTURERS
ASSOCIATION I
c.
Patrick Vainio· American BOA. Inc.
Jack Hanna - Badger Industries. Inc.
Mike Cabrera - Expansion Joint Systems. Inc.
Mana Nivoli - Flexlder S.r.l.- Torino. Ital)
COli Sleimar - Hyspan Precision Products. Inc.
AOilio Pietrafesa - Idrosapiens.
S r 1
Jeff
DePJero - Microflex
Bob Broyles - Senior Flexonics. Inc.. Pathway Dlyision
Max Micheni - SFZ
Roy Felkner·
u.S.
Bellows. Inc.
Rick Marcoue- WahleoMetroflex. Inc.
Peter Berger - \\ itzenmann. GmbH
E.xpafbion Joml
Manufaclurer: >
AS:>OClatlon Inc
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STA DARDS
O TH
EXPA SION JOI T MANUFACTURERS ASSOCIATION INC.
his
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\ xpansion Joint Manufacturers ssociation
[nco
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STANDARDS
OF THE
EXPANSION JOINT MANUFACTURERS ASSOCIATION.
INC.
COi\'TE:\'TS
Section
Foreword
Page
i\lembel' ship of EJ 'IA.
Current Technical
Comnlitte{'
i\lenlbers
SECTiON
1 -
SCOPE. DEFINITIOl S.
AND NOMENCLATURE
1.1
Scope .....................•..........................•.............................................................................................................•..... )·1
1 2
IJefinitiolls.............................................................................................................................................................
I I
1.3
Nonlt'nclaturt' 1-6
SECTION
2 - SELECTIO:-; AND APPLICATIONS
2.1
Selection
of
Expllnsion
Joints
2 1
2.2 St'Il'1:tion for Axial J\'lo\·t'ment 2-2
2.3 Sel ect ion ror
Lateral
Deflection.
Angular
Rotation.
Combined l \ o n ~ m e n t s
2-5
2...1 Applications Using Singlt' Expansion
Joints
2-6
2.5 Applications Using Uni ersal Expansion
Joints
2-8
2.6 Applica tions Using
Pressure
Balanced Expansion
Joints 2 2
2.7 Applications Using Hingt'd E:.\:pansion
Joints
2-15
2.8 Calculation orAngular Rotation in a 3 inge Piping S ~ s t e m 2-20
2.9 Applica tions
L sing Gimbal
Expansion
Joints
2-22
2.10 Anchor. Guidt', and SUPI)Orl Requircnu nls 2-23
SECTION 3 - SAFETY
R E O M ~ I E N D T I O N S
FOR PIPING SYSTEMS CONTAINING
BELLOWS EXPANSION
JOINTS
3.1
Design Specification
3-1
3.2 Expansion Joint Design 3-3
3.3 Expansion Joint
l\-lanuracturing Qualit)·
3-3
3 4
Installation 3 3
3 .5 Pos t Ins ta llat ion Inspect ion Prior
to
S ~ s t c m
Pressure Test
3-4
3 .6 Inspe ct ion
During and m m e d i a t c l ~ Afler
stem
Pressure
Tests
3 4
3.7
Periodic
In-Sen
ice Inspection 3-5
SECTION
4 -
CIRCULAR
EXPAliSIO:-l JOINT DESIGN
1.1
l\'IO\enlent Equalions...........................................................................................................................................
1 1
1.2
Combining
l\'lo\'emt'nts 1 2
1.3 I\lo\ enlent Range 1 3
1 1
Unhersal Circular E:\pansion Joint I\lo\'ements
1 5
1.5 Cold Springing orCircular Expansion
Joints 1 5
1.5.1
Force Reduction
1 5
1.5.2 Slabilit)
1 5
1.5.3 Component Clearanct s
1 6
1.6 Forces
and
l\lonlents
1 6
1.6.1
Force
and
l\lonlcnt Calculation
1 6
1.7
l\laximulII A\:ial Compression Based On I n s t a b i l i l ~
1 10
1.8
Expansion Joint
Flange Loading
Considerations 1 10
\ \ \ \ ~ e j m a o r g
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STANDARDS OF THE EXPANSIO JOINT
MANUFACTURERS
ASSOCIATION. INC.
SECTIOJ 6 -
QUALITY S S U R ~ E
AND
BELLOWS FORMING
I\'IETHODS (continued)
6.16 \'Ielhods
of
Fornling Ietal Bellons
6.16.1 El:tstonlcric Fornling
6.16.2
Expansion [ ~ p a n d i l l g
l\lulldr{'l)
Forming 6·5
6.16.3
Hydraulic Fornling
6-5
6.16.4 Pneunlalic Tube
rorTlling
6-6
6.16.5 Rolled
Con\ oluted
Shel.'t 6-6
6.16.6 Roll
Forming
6-7
6.16.7 Rolled
Ring
6-7
6.16.8 Press-Brake Forlliing ,................................................................................................ 6-8
6.16.9
Combined Forming
6-8
6. t 7 rabrication
Tolerances
6-9
SECTION
7 - EXA1\,IINATION AND
TESTINC
7 1
~ o n - d e s t r u c t h e
Exanlinalion 7 1
7.1.1
Radiographic
Exalllillation
7 1
7.1.2 liquid PenetJ anl
Examination 7 1
7.1.3
Fluorescent
PenetJ ant
Examination
7-2
7 1 1
l\'lllgnetic PaJ ticie Examination 7-2
7.1.5 Ultrasonic EXllnlination 7-2
7.1.6
Halogen leak
Examination 7-2
7.1.7 i\lass SpcctJ ollu·ter ExanlinilliOIl 7-3
7.1.8
A ir Je t leak
EX31ninaiion 7-3
7.2 Non-destructh e
Testing
7-)
7.2.1 PJ essure
Testing
7- )
7.3 Deslructivl.'
Testing
7-'-
7.).1
Fatigue
life
Testing
7-'-
7.3.2 SCluirm
Testing
7-4
7.3.3 l\leJ idional Vielil-RuptuJ eTesting 7-5
SECTION
SHIPPINC
N
INSTALLATION
8.1 Shipping Tags 8-1
8.2
Shipping
DC'\ices
8 1
8.3
Installation
8-2
8 Gaskets 8-2
8.5
Reconlnlended Inslallation
Instructions 8-3
\\
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STANDARDS
THE
EXPANSION
JOINT MANUFACTURERS ASSOCIATION INC
APPENDICES
Appendix A Standard Expansion
Joint
Specification Sheets
Appendix 8 Key to Symbols Used
Appendix
C
Circular and
Rectangular
l\lon·ment.
F o rc e a n d M o me nt [ I l lation s
Appendix 0 COII\ eTsion Factors
an d
Rderences
Appendix
[ Preparation
of
Technical Inquiries
Appcndh r BeIlOl S Fatigue
Tt st Requiremellts
Appendix G BelJo\\s High Temperature
Life
Appendh:
U Angular
Rotation About
Ont
End
Appendix I
Tabulatl. d
V:lllles
for
p
• C
e l
B:
an d B
J
Appendix J Examples
Round Expansion Joints. Forces. and l\lo\ enu.>nls....................................................................................... J· I
I Single Expansion Joint subjected 1 axial
mo\ ement
J- l
Single EXp:ulsion Joint subjected axial
an d
I:ueral mOHllIent J- 4
3 Single Expansion
Joint
with
tie
rods subjected
1
axial
and laleral
movement......................................
J-7
4 Tied Universal Expansion
Joinl subjected
to
lateral
mO\ ell1enl in two plant s....................................... J-IO
5 Universal pressure balanced Expansion Joint located between two pieces
of
equipment
with movements at
en d
points........................................................................ J-I-I
6 Single Expansion Joinl. allached to \ essel nozzle. subjected :lxial a n d la te r al m o ve m en t J·19
7 Calculation
of Angular
ROlation in a 3 hinge piping system.................................................................... J-23
8
Three
(3) hinge
Expansion
Joint s ~ s t e n l
J·25
9 Bellows [q u i\ all nt Movement I)er COIn olution J-28
10 Rectangular Expansion Joint ~ \ e n l e l l t s ; .. .. ... .. J -31
II Calculation f or a
Straight
Run of Pipe
Containing
lUI A:\ial
Expamion
Joint
J-35
TABLES
Table
I
Table II
Table
Table IV
Table \
Recommended Idl ntilicalion Dala Required for Bello\\s subjected to Destructive Tests .
Conlponent Design
Stress
L.ilnits , .
Shape Factors , .
Thermal E:\p:tnsion of Pipe in
Inches
pe r 100 feet .
M o du li o f
Elasticil) or
Commonl)
Used Bello\\s
Materials
.
7 6
9-6
9 8
0-12
1 1
\\ \\ \\ .cJm.l.org ( E\.pansion
Joint Manufacturers
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STANDARDS
OF
THE EXPANSION JOINT MANUFACTURERS ASSOCIATION. INC.
SECTlOI\ I - SCOPE.
DEFINITIONS
AI\ D
I \ O ~ I E N C L T U R E
1 1 SCOPE
The EJMAT\ I Standards arc only intended for application to metallic bellows expansion joints
2
DEFINITlOI\ OF TERMS
The Expansion Joint Manufacturers Association. Inc. has adopted the following definitions of
Expansion Joint
components
and related equipment
AI\ GULAR ROTA
TlOI\
The displacement of the longitudinal axis of the Expansion Joint from its initial straight line
position inlo a circular arc. Angular rotation
is
occasionally referred to as rotalional
movement
This is
11 1
torsional rotation which is described funher in this section.
AXIAL C O ~ I P R E S S I O N
The
dimensional
shonening of
an Expansion Joint along its longitudinal axis. Axial compression
has been referred to as axial mo\ 'emenl.
tra\erse or
compression.
AX lAL EXTE
SIOI\
The
dimensional lengthening
of
an Expansion Joint along its longitudinal axis. Axial extension has
been referred
as axial movement. traverse. elongation
or
extension.
BELLOWS
The flexible element of an Expansion Joint consisl1ng of one
or
more convolutions and the end
tangents \\-ith
L D ::;;
3 with no more than five plies.
CONTROL RODS
Devices. usually
in
the fonn
of
rods
or
bars. anached to the Expansion Joint assembly whose
primary function
is
to distribute the movement between the two bellows
of
a universal Expansion
Joint
Control rods arc not designed to restrain bellows pressure
thrust
CONVOLUTION
The smallest flexible unit ofa bellows. The total movement capacity ofa bellows is proportional
to the number of convolutions.
COVER
A deyice used to provide limited protection
of
the exterior surface
of
the bellows
of
an expansion
jomt from foreign objects or mechanical damage. A cover is somelimes referred 1 as a shroud.
DIRECTlOI\AL ANCHOR
A directional
or
sliding anchor
is
one
which
IS
designed
1
absorb loadmg in
ODe
direction while
pemlming mOlion
in
another. It may be either a main
or
intennedl3te anchor. depending upon the
application m\'oh'ed. When designed for the purpose. a directional anchor
may
also function as a
pipe alignment gUlde ln the design
ofa
directIOnal anchor. an effort should be made to minimize
the friction between its moving
or
slidm£ parts. smce this will reduce the loading on the piping and
equipment and insure proper functioning ofme anchor.
\\ .eJllla.orl,
E.'-paru>ion
Joint
Manufal.:luren,
. \ > ~ o : : i a t l O n .
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STANDARDS DF
THE EXPANSION
JOINT
MANUFACTURERS
ASSOCIATION. INC.
SECTION 4
CIRCULAR
EXPANSION
JOINT DESIGN
4.1
M O \ ~ I N T
EQUATIONS
Expansion Joints may be subjected to axial movement. angular rotatioll. lateral deflection. or
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combination of these. Figure L2 shows a single bellows Expansion Joint subjected to axial
movement only. Note that the total applied movement
is
absorbed
by
a unifonn displacement
of
al1
the convolutions. This also applies
to
dual bellows assemblies such as universal. swing and
universal pressure balanced Expansion Joints.
x
e = N For a single bellows Expansion Joint)
x
e
= For a dual bellows Expansion Joint)
N
4 1
4-2)
In
equation 4-2) above. the value of-r should include the thennal expansion of the center pipe
nipple connecting the two bellows. This may be a significant factor in applications involving
long cemcr pipe nipples. or a large differential between rhe minimum and maximum design
t em peratu res. When the cen ter p ip e n ip pl e is ancho red. as it is
in
a double Expansion Joint see
Section 1.2). each eod of the assembly should be treated as a single Expansion Joint.
In
s uc h a
case. equation 4-1) will apply
nd
the value
ofx
should include the hennal expansion
ofth t
p onion of the center pipe nipple which
is
located between the anchor base and the bellows in
question.
Figure 4.3 illustrates that
an
Expansion .Ioint bellows absorbs pure angular rotation by
extending uniformly on one side and compressing unifornlly on the other.
he
movement
of
any convolution may be cxpressed as:
e =
e
= O
m
u
For a single bellows Expansion Joint)
For a dual bellows Expansion Joint)
4-3
4-4
As illustrated
in
figures 4.4 and 4.5. lateral deflection of
an
Expansion Joint is,
in
reality. a
special case of angular rotation. he two bellows in a universal type Expansion Joint. or each
end oflhe bellows of single type Expansion Joint. rotate in opposite directions to produce the
total lateral deflectiony. Unlike the case
of
pore angular rotation. lateral deflection results
in
unequal movement distribution
over
the bellows. the amount
of
displacement increasing with
the distance from the center of the Expansion Joint. This applies to both single and universal
type Expansion Joints. Since we are concerned only with the maximum displacement per
convolUlion which may be imposed upon any convolution in the Expansion JOIllt. the following
equations are arranged to arrive t the maximum displacement figure. For universal Expansion
Joints. a factor K
is
introduced which is a function of the ratio of the total distance between
the OUlemlost ends of the elements to the convoluted length of the Expansion Joint. he value
of for any given ratio of may be found in figure 4.1 and the displacement per
convolution resulting from applied lateral deflectiony. is as follows:
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Expansion Joint Manufacturers Association. Inc.
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STANDARDS
OF THE
EXPANSION JOINT MANUFACTURERS ASSOCIATION. INC.
SECTION 5 - RECTANGULAR EXPANSION JOINT DESIGN
The following sections describe the various movements. forces. and moments which occur
at
the
interface ofrectangular bellows and the associated dueling system. The movements arc identical all
respects those imposed on circular expansion joinrs and are defined in Section 1 2 of these standards.
Further. the method of analysis ofdetemlining forces and moments resulting from these movements is
also identical 10 circular bellows. Therefore. the same nomenclature can be used. with the exception thaI
[he
lemlS
L
and
L
mean length
oflong
or short sides)
is
substituted for D
1/1
mean diameter).
The
summary
of equations which follows is the rectangular counterpart of the circular bellows. The
explanation for the use of these equations is found in Section 4.6.1.
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5 1
MOVEIVLENT EQUATIONS
Rectangular Expansion Joints may be subjected
to
axial movement angular movement. lateral
detleclion or any combination of these.
Axial movement for single bellows Expansion Joint
b
x
-
N
Axial movement for universal bellows Expansion Joints.
x
2N
5-1)
5-2)
c. Equiva lent axial movement per convolution for single or universal bellows with angular
rotation.
r
L _
c
8
5-3)
SINGLE BELLOWS
FIGURE
5 1
8 L
I
til 4N
r
5-4
\\\\ \\ ,eJma.org
UNIVERSAL BELLOWS
FIGURE 5.2
c Expansion Join Manufaclurers Associalion. lnc. 5 1
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ST ND RDS
OF
THE
EXPANSION JOINT
M NUF CTURERS SSOCI TION
INC
8 3 INST LL TION
It
is important that Expansion Joims be installed
t
the proper lengths as recommended
by
the
manufacturer. They should never be extended or compressed to make up deficiencies in pipe
length. or offset to 3ccommodatc piping which is nOI properly aligned unless such installation s
tolerances have been specified
by
the system designer and anticipated
by
the Expansion Joint
manufacturer. Do not neglect pre-compression
or
pre-extension of the Expansion Joint where it
is required or as designaled by the manufacturer. Generally. such instructions arc included on
the shipping tags and additional infonnation is available in Section 2.
All Expansion Joints provided with internal sleeves should be provided with flow arrows
or
other
suitable means of assisting the installer in properly orienting the Expansion Joint to flow
direction. Correct installation of Expansion Joints with illtemal sleeves is Illost important and
should be checked by the installer. See Section 4.10)
In order 1 insure the proper functioning of any Expansion Joint. it is highly important lhat all
pipelines in which the Expansion Joints are located be suitably 3l11 :horeu guided. and supported.
See Sections 2.2 through 2.10)
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Remember. a bellows is designed to absorb motion by flexing. The bellows is sufficiently thick
to withstand the design pressure, but also sufficiently thin to withstand its cyclic
movement
Optimum design will always require a bellows of thinner materials than virtually every other
component
of
the piping system
in
which it
is
installed. The installer must recognize this and
take all necessary measures to protect the bellows during installation. Avoid denting, weld
spatter. strikes. or the possibility of allowing foreign matter to interfere with the proper
flexing
of
the bellows. With reasonable care during storage. handling. and installation. the user
will assured of the reliability designed and built into the Expansion Joint.
8 4
G SKETS
When removable flanged sleeves are inserted
in
the Expansion Joint. an extra gasket is required
between Ihe face
of
the Expansion Joint and the back face
of
the flanged sleeve. i.e
two gaskets
per Expansion Joint ordinarily, three gaskets if onc flanged sleeve is used per Expansion Joint
and four gaskets
if
a pa ir
oftdes oping
flanged sleeves are used. Caution should be used with
graphite impregnated gaskets
in
contact with stainless steel facings
or
sleeves l high
temperature.
x p n ~ i o n Joint Manufacturers Association. Inc.
www.cjm,l.Vlg
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ST N R S OF
THE
EXPANSION JOINT M NUFACTUR ERS ASSOCIATION INC
This page intentionally blank.
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8-4
xp nsion Joint Manllfticllll :-f:) A : ~ u o : i a l ; U l l II,;.
\\
t jIll J urg
STA, DARDS OF
THE
EXPANSION JOINT MANUFACTURERS ASSOClATION. INC.
SECTION
9 - FEATURES, ACCESSORIES AND
MATERIALS
9 1 M ULTI-PLY
BELLOWS
A multi-ply bel lows can be used
in
many applications. II is important to understand the
functional characteristics of each type of construction. These Standards apply
t
bellows with no
more than five plies.
9.1.1
MULTI-PLY
CONSTRUCTION WITII THE SAME
TOTAL THICKNESS
AS A
SINGLE PLY
CONSTRUCTION
9.1.1.1
PRESSURE
CAPACITY
The circumferential membrane and meridional membrane 5 , pressure
stresses are unaffected since the rotal bellows thickness is the same as a single ply
conslnlction. The meridional stress due to pressure will be higher for the
multi-ply construction due the thinner material per
ply.
9.1.1.2 FATIGUE LLFE
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An increase
in
fatigue life over that
ofa
single
ply
construction will usually result
since the meridional deflection stresses 55 and Sf, aTC reduced due
to
the
thinner material per ply.
9.1.1.3
SPRING FORCES
A decrease
in
the spring force will result since the spring rate will be lower due to
the thinner material per ply.
9.1.1.4 BELLOWS STABILITY
Column stability is reduced due to the thinner material per ply. In-plane stability
is also reduced.
9.1.2
MULTI-PLY CONSTRUCTION
WITH THE SAME THICKNESS FOR
EACli
PLY AS A
SINGLE
PLY CONSTRUCTION
9.1.2.1
PRESSURE CAPACITY
The pressure capacity
of
the bellows is higher than a single ply construction. The
circumferential membrane and meridional membrane SJ pressure stresses
are lower since the total bellows thickness is greater. The meridional bending
stress due to pressure will be lower for the multi-ply construction.
9.1.2.2 FATIGUE
LIFE
The effect on fatigue life over that ofa single ply construction will be minimal.
9.1.2.3 SPRING
FORCES
An
increase
in
the spring force will result since the spring rate
wiJI be
bigher due
to the greater total material thickness.
9.1.2.4 BELLOWS
STABILITY
In-plane and colunm stability are increased due to the greater total material
thickness.
v V, \\ .eJma.org
Expansion
Joil l1
Manufacturers s ~ o c i a t i o n Inc. 9-1
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