EJMA 2008

STANDARDS OF THE EXPANSION JOINT MANUFACTURERS ASSOCIATION, INC. NINTH EDITION

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EXPANSION JOINT MANUFACTURERS ASSOCIATION , INC. 25 NORTH BROADWAY, TARRYTOWN , NY 10591 RICHARD C. BYRNE , SECRETARY TEL: 914-332-0040 FAX: 914-332-1541 E-MAIL: ejma@ejma .org www.ejma.org

STANDARDS OF THE EXPANSION JO INT MANUFACTURERS ASSOCIATION. INC. FOREWO RD Since 1958. when the Expans10n J0 ll11 Manu lacturcr" s Assoc iation (EJMATM ) first publi shed these Standards. continuing technologica l improvemen ts in the application and design of Expansion Joi nts have been reported through the cooperat ive e fforts of its assoc iation members by expanding the scope and con tClH of Ihis pub lication . founded three years earlier in 1955.lhc Expansion Jo illl Manufac turer's Association began wim a group of companies ex perienced inlhc application. design. and fabrication of Expansion Joints. T he firs t EJMATM Standard edit ion was. of necessity. somewhat brief a nd covered only applications in vo lving ax ial movement. But as research and extensive tcsti ng res uhs werc catalogued. more detailed design data has been included in thc EJMA T\I Sta ndard. Thc EJMA ™ Standards are intcnded for application to mctallic bellows expansion jo ints h:lVi ng only thc convolution shapes s hown in thc S tandards and ha ving convolution welds onl y in the meridional direction with the exception of the bellows anach ment welds. The EJMATM Technical Committee is ded icated to continuously improving the utility and tec hnical content of the Standards. Suggest ions an d comments fro m industry uscrs are welcomed and s hou ld he forwarded to the Secretary of this Association in w riting. It is imponant to note that the EJMATM Standard is a trade association document containing recommendations for application of expansion joint products and in-depth tcchnical infonnation for usc in design ing expans ion join t products. It is not a manufacturing standard or a q uality ass urance document. The type of non-destructive examinat ion and the extent ofqua li ry assurance test ing to be applied to given prod uct sho uld be addressed by o ther documents such as the ASME 8 3 1.3 Piping Code. the ASME Pressure Vessel Code or another user provided s peci fication . The Standard docs not limit or dictate thc manufacturing process to be lIscd for cons truc tio n of expansion joints. no r docs it estab lis h spccific engi neering requ irements deemed necessary for the !wfe application. design and manufacture of Expansion Joints. If there is a strong preference for a eenain type o f manufacturing process. the user s hould provide this infonnation. Industry users arc cautioned that these Standards s hould not be considered as a design handbook. and must not replace sound enginceringjudgment. educat ion and experience.

As o f this writing, the EJMA ™ Standard thoroughly covers the design of expa nsion joint bellows elements. However. the Standard docs nOi cover the design of hardware associated w ith res tra int of pressure thrust. Press ure thrust restraint hardware is as imponant as the bellows element in the design and fabrication of an ex pansion joint assembly. Users a re strongly advised to ob tain doc umented design res ults for bellows clemen ts and pressure thrust restraint hardware for any cri tical application.

NO WA RRANT Y EXPR ESSE D O R IM PLI E D The engi neering Standards herein are recommendcd by the Expansion Joint Manufacturers Association. Inc. to assist u scrs. engineers. architects and others who spec ify. design and install Expansion Joints in piping sys t e m ~ to obtai n the most efficient service (rom Expansion Joint installations. T hese Standards are based upon sound engineering principles. research and field experiencc in thc ma nufacture. design. installat ion and use of Expansion Joint s. Th ese Standards may be s ubject to revision as funher investigation o r experience may s how is necessary o r desirable. Utilizati on of th ese Standards remains em ircJy optional. Nothi ng herein sha ll constitute a warranty of any ki nd. expressed or implied . Accordingly. all warrnnties o fwha lever nature. cxpressed or implicd. arc herewi th s pec ifically di sclaimed and di sa vowed.

Co pyright 1958, 1962, 1969, 1975, 1976, 1980, 1985, 1993, 1998, 2003, 2U05, 20U8 EXPANSION JOINT MA UFACTURERS ASSOCIATlON.INC. All ri ghts reserved. This book or any pan thereof may not be reproduced in any fonn without wri tten penn ISS ion of the Expa nsion Joint ManufaclUrers Assoc iation. Inc. The speci fi cation sheets constituting Append ix A arc not covered by any copyright restrictions and may be freel y reproduced tlnd utilized by purchascrs of this Standards manual.

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, Expansion Joinl Manufacturers Associ3lion. Inc.

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STANDARDS OFTHE EXPANSION JOINT MANUFACTURERS ASSOCIATION. INC.

MEMBERSlllP LIST

EXPANSION JOINT

~lANUFACTURERS

ASSOCIATION. INC.

American BOA. Inc. - Cumming. GA Badger Industries. Inc. - Zelienople. PA Ex pansion Joint Systems. Inc. - Santee. CA Flexider S.LI.- Torino, Italy Hyspan Precision Products. Inc.- Chula Vista. CA Idrosapi ens, S.r.1 - Leini (Torin o), Italy

Microflex - Ormond Beach. FL Senior Flexonics. Inc .. Pathway Di vision - New Braunfels. TX SFZ - Lyon. France

U.S. Bellows. Inc. - Houston. TX WahlcoMetroflex. Inc.- Lewiston. ME Witzenmann. GmbH - Pforzheim. Gennany

CU RRENT TECHN I CAL COMM ITTEE

M E~ IB ERS

EXPANS ION JOINT MANm' ACTU RERS ASSOCIATION. INC. Patrick Vainio - American BOA, Inc.

Jack Hanna - Badger Industries, Inc. Mike Cabrera - Expansion loint Systems. Inc . Mario Nh-oli - Flexider S.r.I.- Torino. Ital y Scott Stelmar - Hyspan Precision Products. Inc . Arulio Pietrafesa - Idrosapiens. S.r.1 Jeff DePiero - Microtlex Bob Broyles - Senior Flexonics. Inc .. Pathway DiviSIOn

M., Micheni - SFZ Roy Felkner - U.S. Bellows. Inc . Rick Marcotte- WahlcoMerrotlex. Inc . Peter Berger - Witzenmann. GmbH

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Expansion JOInI Manufaclurers

ASSOCiation.

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STAN DA RDS OF TH E EX PANSION JOI NT MANUFACTU RERS ASSOCIATION. INC.

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STANDARDS OF T HE EXPANSION JO INT MANUFACTURERS ASSOCIAT ION. INC.

CONTENTS

Pa ge

Sectio n Foreword 1\lembenhip of [J IA. ........................................................................................................................ ................... ......

Current Technical Conlnlittec

~ I embers

......... ,......................................................................... ................... ..............

ii iii

iii

SECT ION 1 - SCO I) E. DEFINITIOi'\'S, AND NOMENCLATURE 1.1 1.2 1.3

Sco pe ...............................................................................................................................................................•.... Definition s............................................ ............................. .................................................................................... Nomt"nclaturt" ......................................................................................................................................................

I- I I-I 1-6

SECT ION 2 -S ELEcrIO~ AND APPLICATIONS 2.1 2.2 2.3 2A 2.5 2.6

St" It"Clioll of Expansion Joints ............................................................................................................................. Seit"clion for Axial j\'iovement .............................................................................................................. ..............

2- 1 2-2

Selection for Ltter!ll Oenec:tion. Ang ular Ro tation. & Co mbined Mon! m ents .............................................

2~5

Applic.alions Us ing S ingle Ex pansion Joints ..................................................................................................... Applications Usin g Uni" ersal Expansion Joints ...................................... ......................................................... Applic:ltions Usi ng Pressure Balanced Expansion Joints ................................................................................ 2.7 Applications Using Hinged Expa nsion Joints ................................................................................................... 2.8 Ca lculation of Angular H.otat ion in a 3 Hinge Piping Systt"111 ......................................................................... 2.9 Applicatio ns t;sing G imba l Expansion Joints .................................................................................................. 2.10 Anchor. G uide, and S upport Requirements .....................................................................................................

2~6

2-8 2~12 2~15

2-20 2~22

2-23

SECTION 3 - SAFETY RECOMMENDATIONS FO R PIPII'G SYSTE~IS CONTA INI"IG BELLOWS EXPANS ION JOINTS 3.1 3.2 3.3 3A 3.5 3.6 3.7

Des ig n Specification .............................................................................................. .............................................. Ex pa nsion Joint Design ...................................................................................................................................... Expansion J oint J\'l anufacturing QuaJi~ .......................................................................................................... Installation ........................................................................................................................................................... Post InstaU:llion In spection Prior to System Press ure Test .................................. .......................................... Inspection During and Immediatel) Afler S) stem Pressurt" Tt"sls ................................................................. Period ic In~Ser\·ice Inspection ...........................................................................................................................

3-1 3~3

3-3 3-3

3-' 3-' 3~5

SECTION 4 - C IRCULAR EXPANSION JOINT DESIGN -1.1 -1.1 4.3 -IA -1.5

-1.6 -1.7 4.8

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l\lo\emenf Equations........................................................................................................................................... Conlbilling l\lo\'elllt"nts ....................................................................................................................................... l\ l o\'elnent Range ................................................................................................................................................ Uni\ersal Circ ular Expansion Joint l\ lo\'ements ............................................................................................. Cold Springing of Circular Expansion Joints .............................................................................................. .... -1.5.1 Forct" Reduction ...................................................................................................................................... -1.5.1 Slabi li ~ .................................................................................................................................................... -1.5.3 COlllllonenl C learanct"s ........................................................................................................................... Forces and l\lonlt"llts .......................................................................................................................................... -1.6.1 Force a nd l\loment Calculation ............................................................................................................. ~ Iuimum A\ial Co mpression Based On Instabilil) ....................................................................................... Expansion Joint Flange Loading Co nsiderations ................................................................................ .............

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Expall:.ion Joint Manufacturers Association. Inc.

-I-I -1-2 -1-3 4~5

-I~5

-1-5 -I~5

-1-6 4-6 4-6 -I~IO -I~IO

SECT ION 4 - C IRCULAR EXPANS ION JOINT D ES ICN (co ntinu e d) 4.9

4. 10

4.11 -' . 12

-'. 13

4. 1-' -'. 15

Vi bral ion .................... .......................................................................................................................................... -1.9. 1 Singl(' BclIO\\ s .......... ...... ............................... ................. ... .. .... ............ .................. .. .......... .. ..................... -'.9.2 Du a l Bellows (U niversa l Ex pa ns ion J oinl ) ............................................................................................ I nlernal Slcc\'es - C ircular Ex pa nsion J oinlS ............................ .. ....... ..................................... ......................... 4.10. 1 C riteria for Determinin g the Need for IlIl ernal SieHl'S .............................. ......................................... 4.10.2 Design Rcco mme nda tions for Internal Slee\'es ..................................................................................... Externa l Covers - C ircu lar Expa nsion Joints.. .................................................................................................. Bello\\$ Oesign ............................. ........................................................................................... ............................. -' .12.1 Pa r a mete rs and C ril'eria J\ fffi:ling Bellows Des ign .............................................................................. 4.12. 1. 1 Un reinforced Bel lows ....................................................................................................................... 4.12. 1.2 Reinforced Bellows ........................................................................................................................... 4.12. 1.3 Internal Press ure Ca pacity ................................ .............................................................................. -1 .12.1.4 Den eclion Stress ................ .......... .......... ....... ...... ........................................... ................................... -' .12.1.5 Fatigue Life Expec l a n c~r .................................................................................................................. 4.12. 1.6 Bellows Stabi lit·~ ................................................................................ ............................................... 4.12.1.7 Bello\\ SSllri ng Ra il' ..................................................................... .................................................... 4.12 .1.8 Correla l.ion Testi n::! ........................................................................................................................... 4. 12.1.9 Bellows 1-l eal Trea lnlcnl ................................................................... .................... ........................... Oesign Eq ua tio ns ...................... ................................................ ............... ...................... ...................................... 4.13.1 Design Eq uat io ns for Ullrei nfo r ced Bellows ......................................................................................... 4. 13.2 Des ign Eq uatio ns for Reinfo r ced Bellows ......................... .................................................................... 4. 13.3 lles ign'[ ........................ .................................................. ............................................................. 9.1.1.3 Spri.ng Forces ....................................................................... ... .......................................................... 9. 1. 1.4 Bellows Stability ............................................................................................................................... 9.1 .2 l\ lulti-PI~' Construction with t he Same Thickness ror Each Ply as a Single PI~' Construction ......... 9.1.2. 1 Pressure Capacity ........................................................ ................................................................ ..... 9.1 .2.2 Fatigue Lire ........................................................................ ............................................................... 9. 1.2.3 S pring Forces ............................................................... ........ ............................................................. 9. 1.2.4 Bellows Stabilit y ............................................. ............. ........... ............................................. ............. 9. 1.3 Multi-Ply Construction wil h G rea ter T hi ckness ror Each Ply Than for Single Ply Const ruc tion ... 9. 1.3. 1 Pressure Capacity ............................................................................................................................. 9. 1.3.2 Fatigue Lire ........................... .... .............. ........................... .. ...................... .................. ........ ............. 9.1.3.3 Spri ng Forces ......... .......... ....................... ........................... .......................................... ..................... 9. 1.3.4 Bellows Stabili ty ............................................................................................................................... 9.1.4 l\l ultiple l\lateria l Usage .......... ............................................................................................................... 9.1.5 Redundant Ply Const ru ction with the Sa me T hickness for Eac h PI~' as a Si ngle Ply Construction 9.1.5. 1 Pressure Cu pacity ........................................................................................................ ..................... 9. 1.5. 2 F:ltigue Lire ....................................................................................................................................... 9. 1.5.3 Spring Forces ................... ....... ........................................... ............................................................... 9. 1.5.4 Bellon'S S ta bility ............................................................................................................................... 9. 1.5.5 l\'l o nitored Ply " cllows ..................................................................................................................... Tie Rods, Hinges and Sinlil a r Accessories .......................... ............................................................................... 9.2. 1 Forces and Loads ..................................................................................................................................... 9.2.2 l\let hods or Attachme nt ........................................................................................................................... 9.2_1 I>esig n Considerat ion .............................................................................................................................. 9.2.3. 1 Tie Rods. t-linges. and G inlba.ls ....................................................................................................... 9.2.3. 2 AUachnlcnls til I'iring ............................ ........ .................................................................................. 9.2.3.3 Compon ent Des ig n S tress Linlits ................................................................................................ .... 9.2.3.4 References ...................... .................................................... ............................................................... Flanges .......................................................................................................... ........................................................ Co rrosion ..... .................................................................................................. ........................................... ............

9-1 9- 1 9-1 9-1 9-1 9-1 9-1 9-1 9-1 9-1 9-2 9-2 9-2 9·2 9-2 9-2 9-3 9-3 9-3 9-3 9-3 9-3 9-4 9-4 9-4 9-4 9-4 9-5 9-5 9- 12 9· 13 9- 14

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FIGURE 2.5

Figure 2.5 shows the application ofa sing le Expansion Joi nt to a pipe line containing an offset. It shou ld be noted that app li cations of thi s type arc not usuall y recolllmended and will pcrfonn sati sfactoril y only within certain lim its. As in Figure 2.1. the line is provi ded wi th main anchors at eac h end to absorb the pressure. movement loading, and guide fri ction. Where the line conta ins an offset. thi s load must first be transmitted through the offset leg. resu hing in a moment on the piping. Where the line size is smai L the offset appreciable, or where the pressure and movemen t fo rces are relatively high, this configurati on may result in over-stressing, or distortion of the piping and gu ides. Note the nearness of the Expan sion Joint to an anchor (MA). the closeness of the first alignment gu ide (G I). the spacing between the first alignment gu id e and the second alignment guide (G2) and the spacing of intermediate guides (G) along the balance of the line. Guides should be installed near both ends of the offset leg to minimi ze the effects of the bending moment on the system. For spacing of other guides, see guide chart Figure 2.3 i , an(Vor equati on (2-7).

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FIGURE 2.6

Figure 2.6 typifies good practice in the use of a pressure balanced Expans ion Joinl to absorb axial pipe line expansion. ote that the Expansion Joint is located at a change in direction of the piping and that the elbow and the end of the pipe line are sec ured by internledi ate anchors. Since the pressure thrust is absorbed by the Expansion J01l11 itself, and only the forces required to deflect the Expansion Joim are imposed 011 the pipi ng. a minimum of guiding is required. Frequently, directional gu iding adjacent to the Ex pansion Joint . as shown. may suffice. in long. small-diameter pipe lines, add itiona l gu iding may be necessary.

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STANDARDS OF THE EXPANS ION JOINT MANU FACTURERS ASSOCIAT ION. INC.

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FI GURE 2.7 Fi gure 2.7 shows the use of an in-line pressure ba lanced Expansion Joints to absorb axial pipe li ne movements in a long. straight piping run. By utilizing this arrangement the two anchors s hown Hre relieveci of pressure loading and are rle!o>igned as intennedia le anchors . Since the

piping is rel ieved of compressi ve pressure loading. a mi nimu m of guiding is req uired. primarily to direct the thenna! expansion of the piping into the Expansion Joints in an ax ial direction.

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FI GU RE 2.8 Figure 1.8 typifies good practice in the use of a pressure balanced Expansion Joint to absorb the thennal expansion of equipment such as nlrbines, pumps, compressors. etc. Tbe primary fu nction of the Expansion Joint is [0 minimize loading upon the equipment casing. Note that only an intennediate anchor is required at the change of piping direction and that, if the Expansion Joint is located immediately adjacent to the machine. no guiding is required. Care should be taken to provide suffic ient flexibility in both the flow be ll ows and the balancing bellows, so that the forces required to compress the Expansion Joint do not exceed loading limits for the equipment as es tablished by the equipmem manufacturer. See Section 2.6 for further infomlation. 2.3

SE LE CTION FOR LATERAL DEFLECTION, ANGULAR ROTATION AND COMBINED MOVEMENTS The selection and proper app li cation of Expansion Joints for late ra! deflection. angular rotation and combined movements. invol ves the evaluat ion of a number of va riables. These can include the piping configuration, the operating conditions. desired cyclic life. load limitations upon piping and equipment, and available su pponing structure. In some cases, two or more types of Expansion Joints may be suitable for a particular application. The selection then becomes purely an economic one. More frequently one or the other of the available designs possesses ul1Ique characteristics which make il particularly suitab le for a given application.

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E.\pansion Joint Manufacturers Associalion. Inc.

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STAN DARDS O F THE EXPA SIO ' JOINT MANUFACTURERS ASSOCIATIO , I C. 2.4

APPLI C ATIONS US ING SINGLE EXPANS ION JO IN T S

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FI GU RE 2.9 The single Ex pansion Joint is usua ll y considered first for any application because it offers the lowest Expansion Joint cost. Figure 2.9 shows a typica l application of a single Expansion Joint absorbing combined ax ial movement and lateral deneclion . The system closely resembles the arra ngements shown for axia l movement on ly in the preceding section. The Expansion Joint is located at one end of the long piping leg with main anchors a l each end and guides properl y spaced for both move ment control and protection of the pipin g against buckl ing. The anchor al the len end oftbe line is a direct ional main anchor (DMA ) which. while absorbing the ma in anchor loading in the direction of the Expansion Joint axi s, permits the rhemlal expansion of th e short piping leg to act upon the Ex pansion Joint as latera l defl ection. Beca use the main anchor load ing exists onl y in the piping segmcnI containing the expansion joint. the anchor al the end of the shorter piping leg is an intennediate a nchor.

2-6

(" Expansion Joint M!lIlUfadUl'cl 1> A:.1>rn:ialiun. Inc.

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STANDARDS OF THE EXPANSION JOINT MA UFACTURERS ASSOCIATION. INC.

FIGURE 2.10

Figure 2.10 shows an alternate arrangemcm in which the Expansion Joint is installed in the shon piping leg and the principal expansion is absorbed as lateral deflection. The longer piping leg is free of compressive pressure loading and requires only an intemlcdiate anchor and direclional guiding. The functions of the directional main anchor imd the pipe guide may be combined in a single device . ,

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FIGURE 2.1 I

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STANDARDS OF TH E EXPANSION JOINT MANUFACTURERS AS OCIATION.INC.

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COLD POS it iON CENTERLINE

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HOT POSITION

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NEUTRAL POSITION

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FIGURE 2.12 Fi gures 2.1 1 and 2.12 represent modifications of Figure 2.10 in which the main anchors at either end of th e Expansion Joi nt are replaced by ti e rods. Where the piping confi guration penniLS, the use af tie rods adj usted to prevent ax ial movemen t freq uently simplifies and reduces the cost of the insta llation. Because of these tie rods, the Expansion Jo int is not capable of absorbing any axial movement other than its own th emlal expansion. The thermal expansion of the pipi ng in the shorter leg is. as a result. imposed as de fl ection on the longer piping leg. Where the longer piping leg is not suffic ientl y fl exib le and where the di mension of the shorter leg is suitabl e. tie rods may be installed spann ing the entire short leg so that no deflecti on is imposed on the longer run from th is source.

Where apprec iable amounts of lateral deflecti on are Imposed upon the Ex pansion Joint. some shortening of the Expansio n Joint resul ts from the di splacement of the tie rods as shown in Figure 2.1 1. Care should be taken to insure that sufficient piping flexibility ex ists to absorb this deflection and tha t adeq uate clearances are provided in the guide to permi t deflection of the piping. The amo unt of thi s deflection can be minimized by cold springing the Expansion Jo int in the latera l direction as shown in Figure 2. 12. The principal restri ction upon the usc of single Expansio n Joints for lateral deflection or combined axia l movement and lateral defl ection is the lim ited amount of lateral deflection whi ch such an Ex pansion Joint can absorb. The allowa ble lateral de flection is direct ly proportiona l to the ratio of convo luted length to diameter which. in turn. is restricted by considerations of stabili ty and manufacturing li mitations. While eminently suitable fo r applications such as Figure 1.9 where the principal mOvement is axial. the re lative ly sma ll avai lable laleral movement severely li mits the type of appl icati on illustrated in Figures 2.10. 2. 11 and 2.12. Where operating pressures and tempeT3tures arc high. or where avail ability of suitable structures precludes the use of main anchors and multiple g uides. the applicat ion shown in Fi gure 2.9 m~y no! be fe~sible and another type of Expansion Joint may result in far morc economical installation. 2.5

APPL I CATI ONS US I NG UNI VE RSAL EXPANSI ON J O I NTS

The uni versal Expansion Joint is particularly we ll adapted to the absorption of lateral de flection. In additio n. thi s design may be used to absorb ax ial movement, angu lar rotation or any combination of the three. A common app li cation of the universal Expansion Joint is its usc as a tied Expansion Joint in a 90 degree piping offset with the tie rods adjusted to prevent external axia l movement. Two slich applications are shown in Figures 2. 13 and 2. 14.

2-8

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STANDARDS OFT HE EXPANS ION JOINT MANUFACTURERS ASSOCIATION. INC.

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FIGURE 2.13 Figure 2.13 shows a tied universal Expansion Joint used to absorb lateral deflection in a single plane "Z" bend. Where dimensionally feasible, the Expansion Joint should be designed to filllhe entire offset leg so that its expansion is absorbed within the tie rods as axial movement. The tie rod should be extended to the e lbow cenler line when practical. The thermal movement of the horizomallines is absorbed as latera l deflection by the Expansion Joint.

Both anchors are intemlcdiarc anchors since the pressure loading is absorbed by the lie rods. Only directional guiding is required since the compress ive load on the pipe consists only oflhe force necessary to deflect the Expansion Joint. Any themlal expansion of the offset leg external to the tie rods. such as that of the elbows at either end. must be absorbed by bending of the horizontal pipe legs. Provision should be made in the design of the guides to allow for both this deflection and the reduced length of the Expansion joint in its deflected position. In addition, particularly in tbe case oflong universal Expansion Joints under high pressure, additional allowance may be necessary to compensate for stretching of the tie rods under load. The Expansion Joint manufacturer shou ld be consu hed for recommended minimum guide clearances.

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2·9

STANDARDS OF THE EXPANSION JOI NT MANUFACTURERS ASSOC IAT ION. INC.

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STANDA RDS O F T HE EX PANS ION JO INT MANUFACTU RERS ASSOC IATI ON, INC. 4.4

UNIVERSAL CIRC ULAR EXPANSION JOINT MOVEMENTS T he unrestrained non-cycl ic movements of a universal expa nsion joint centerspool due to dead weigh t should be considered in the design. T he movements applied to each be llows may be calc ul ated as fo llows: x

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,'fi D''"

T he above movemen ts should be comb ined with the ot her design move ments to confiml that the tota l movements per convol uti on e(' and e,. do not exceed the max imum value e,. (max) and e,. (max). In addition. the ca lculated tota l stress range (St) based on the above movements at the design pressure must be less than 1.5 CmS"h. The dead we ight of the centerspoo l may be supported by devices such as pa ntograph linkages and slotted hinges. 4.5

C OLD SPRINGIN G OF C IRCU LAR EXPANSION JOINTS The term "Cold Springing." as defined by the Piping Designer, entails pre-straining of the elements of a piping system at the time of installation. so that the thermal stresses in the piping in the operating pos ition are appreciably reduced . As applied to Expansion Joints. the purpose of cold spring ing may be considerably different, although the mechanism is basica ll y the same. "Cold Springing" is defined as the lateral or angular offset of the ends of an Expansion Joint when installed and should not be confused with Ihe tenns "pre-compressing." "pre-extending" or "presetting." These laner lernlS apply 10 the adjustment of an Expansion Joint in an axial direction to allow for specified amounts of axial compression or axial extension within the limits e. and er established by the manufacturer. In some cases it may not be practical to cold spring an Expansion Joint al the factory. The reasons for "Cold Springing" an Expansion Joint are described below. 4.5, I

FO RCE R EDUCTION In a wide range of present day applications. the force required to defleci an Expansion Joint is of significant importance. Where the Expansion Joint is used to relieve loading on sensi tive equipment. or anchor struct ures are limited to extremely small loads. cold springing the Expansion Joint at installation will effect a reduction in the maximum deflection force value of as much as 50°0. In other cases. 100°'0 co ld spring may be used 10 provide minimum lateral deflection forces at the operating position.

4,5.2

STA BILITY Figures 4.3. -lA. and 4.5 illustrate the positions assumed by bellows subjected to angular rotation and'or lateral deflection. In all cases, the movement is achieved by rotation of the convolutions. so that one side is extended and the other compressed. It has been noted previously thai a bellows displaced in this manner. when subjected to inlernal pressure. is

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4-5

STANDARDS OF T HE EXPANSION JOINT MANUFACTURERS ASSOC IATION . INC.

acted upon by an unbalanced pressure force or couple which. if su fficient ly large. cou ld result in distortion of rhe bellows. Beca use the magnitude of the unbalanced pressure force or cou ple is proportional to the inlcmai pressure and the displacement orlhe convol utions. a reduct ion in either of these va lues w ill improve the stab ili ty of the Expansion Joi nt. By cold springing the Expansion Joilll 50% al installation. the maximum disp lacement per convolu tion is reduced by half and. consequently, the Expansion Joint becomes far m OTC stable than wou ld be the case if it wcre deflected fully in one direction. For Ihis reason. where Expansion Joints are subject to large amounts of latera l deflection , or where opera ting press ures are relati ve ly high, the Expansion Joint manufacturer may require that the Expansion Joint be installed in a cold sprung condition. 4.5.3

C OMPON ENT C LEARANC ES

Where an Expansion Join! is furnished with internal sleeves, external covers. or tie devices spanning the bellows. these components mu st be designed with adequate clearances to 3ccommodate the lateral deflection or angular rotation of the Expansion Joint. The amOllnt of clearance requ ired is directly proportio nal to the di splacement and. if the Expansion Joint is cold sprung 50%, these clearances can be rcduced to a minimum. By co ld springing, internal sleeves of maximum diameter can be furnished. the overall diameter oran Expansion Joint inco rporat ing ex ternal covers or tie devices minimized. and the design of external structures si mplified. 4.6

FORCES AN D MOM EN T S (Sec App endix H) 4.6. 1

FORCE AN D M OMENT CALCU L A T ION

In order to eva luate the loads upon piping, supports. or equipmcnt. it is necessary to detemline the forces and moments requi red to move an Expansion Joint. For this reason . the catalogs of most Expansion Joi nt ma nufacturers contain force data for the sta ndard designs offered. T his data is expressed as th e fo rce required to move a convolution 10 the rated axia l move ment estab lished by the manufacturer. For convenience. it is desirab le to divide this force by the rated movement to obtain a be ll ows resi stance factor or worki ng spri ng rate , f .. . in pounds per inch of movement per convolu tion. (Refer to Section 4. 12. 1.7 for further discussion of J:,). Having determined this factor. the moments and forces required (0 move an Expansion Joi nt may be calculated as follows:

F"

=

MI

AI,

,., "

4-6

,

J" D.e, -

(4- 14)

1Me, 4

f .. D",ep 4 f " D",e ,

2(L,

±x)

f .. Dme, 2(L" ±x)

(for lateral movement)

(4-15)

(for angular rotation)

(4- 16)

(for lateral movement ofa single bellows)

(4-17)

(for lateral movement ofa universal bellows)

(4-1~)

&J Expansion Joint ManufaclUrers Association. Inc.

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STANDARDS OF THE EXPANSION JOINT MANUFACTURERS ASSOCIATION, INC.

Figures 4.2 tluough ·t5 show the forces and moments applied on the expansion joints produce stalic equilibrium for the various types ofmovcment.

[0

The preceding relationships are applicable to all Expansion Joints. It shou ld be noted. that every equation is dependent upon data which must be supplied by the Expans ion Joint manufacturer. For standard designs. all necessary data is available in the catalogs of the individual manufacturer. or can be obtained on requesl. IN 0 CASE. S HOULD DATA OF ONE MANUFACTURER BE APPLIED TO T HE PRODUCT OF ANOTHER SINCE. DUE TO FUNDAMENTAL DESIGN DIFFERENCES. THESE FACTORS MAY VARY. NOTE: "x". "y". and "9" are all to be expressed from the initial installed position of the Expansion Joint to the position under consideratioIl. When cold spring is involved or when there are several sets ofthennal conditions to be considered (system at operating temperature and system shutdown in a sub-zero ambient. for example), the x.y, and deflections should be determined for each condition and separate e,. e, . f!. e, ' e,_ . and e

e

calculations made for each condition as described in Section 5.4.

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4·7

STAN DA RD S OF T HE EX PA NSION JOINT MANUFACTURERS ASSOCIATION. INC.

...I

~ N·CONVOLUTIONS

f---Lb----Y

't---n,,-,--.., F.-+--:~--

I

t

::1. I

Om

I

-;--!'-T..J

Jq AXIAL MOVEMENT

(SINGLE EX PANSION JOINT )

FIGURE 4.2

•

ANG U LAR

ROTAT ION

SIN GLE E XPAN S ION JO IN T

FIGURE 4.3

S

4-8

POINT OF APPLICATI ON OF EXTERNAL FORCES AND MOMENTS

C Pinned/Pinned -.25Psc Fixed/Laterally Guided -.25P>l: Fixed/Free -.06Psc It should be noted that external pressure does not produce column squi ml. When a be llows is subjected to externa l pressure, its pressure capacity can be verified by the method d iscussed in Section 4.13.

FIGURE4.11

In-plane squi nll is defined as a shift or rotation of the plane of one or more convolutions such thai the plane of these convolutions is no longer perpendicular to the axis of an unreinforced bellows. II is characterized by tilting or warping of one or more convolutions as shown in Figure 4.11. This condition is predominantly associated with high meridional bending stress and the formation of plastic hinges at the root and crest of the convolutions. II is Illost common in bellows which have a relatively smalllength-to-diameter ratio. See Equation (436) for a method of evaluating an unrein forced bellows for in-plane squirm. To prevent bellows squiml under test conditions. the test pressure should be less than or equal to 1.5 times the limiting design pressure based on column or inplane instability using room temperature material properties. In addition. the test fixture should duplicate the as-installed condition as closely as possible. The equat ions given for squiml should only be used when the actual bellows metal temperature under operating condi tions is below the creep range. Squirm calculations for actual bellows metallemperatures in the creep range must be substantiated by high temperature lest data or history of successful operation of a similar bellows size and configuration for identical or more sc\·erc ser\'ice.

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,(' E>;pansion Joinl Manufacturer.. Association. Inc .

STANDARDS OF THE EXPANSION JOI NT MANUFACTURERS ASSOCIATION. INC. These equations inc lude fac tors such that the ratio between the limiting design pressure and the critical squ irm pressure is approximate ly 2.25 for col umn squirm and 1.75 for inplane squiml. When a universa l rype expansion joint is subjected to lateral offset. the internal pressure produces a force that tends to rotate the ccnterspool. This force is res isted by the stiffn ess of th e bellows. Irthe force is suffi ciently high. instabi li ty can occur. A method for evaluating thi s mode of instability is given in Metallic Bel/oll's and Expansion Joinls· 1989. ASME PVP Vol. 168. Pgs 41-43. 4. 12.1.7 BELLOWS SPRING RATE The force req uired to deflect a bellows axially is a funct ion of the dimen sions of the bellows and the material from which it is made.. The curve of force vs. deflection for most bellows indica tes motio n extending into the plasti c range as shown by the solid line in Fi gure 4.12. The first porti on of the curve is a stra ight line as the be llows is deflected throug h its elastic range. As bellows deflection continues and extends into the plastic range, the force vs . defl ection re lati onsh ip becomes non-linear until the point of maximum deflection is reached. When the restrai ni ng force is released. th e curve aga in becomes linear umil the appl ied force is zero at which point the residua l de fl ectio n of the bellows still has a positive va lue. To return the bellows to its initial position. a restoring force must be appli ed in the oppos ite directi on as shown by the curve below the abscissa. Line A in Fi gure 4. 12 represents the bellows theoretical in itial elastic spring rate . be detennin ed anal yticall y w ith reasonable accuracy from eq uations based on e lastic theory. The bellows theoretical initial elasti c spring rate, Ji is cal culated in accordance with Equations (4-37), (4-50), and (4-61 ).

.!:. This value can

Lines Band C represent bellows resistance factors or working spring ra tes. for bellows w ith operating deflections in the plasti c range.

j~"

The use of the initial elastic spring rate in place of the working spring rate for a bellows whose deflection extends into the plastic range predicts forces whi ch can be cons iderably hig her than actua l. This is recogni zed to be a problem and various methods have been used to obtain more accurate results. Lme B, drawn from the orig in to the point of maximum force and deflection, is used as the bellows workin g spring rate..f~. but has the disad vantage of underestimating the actual force over the full range. Line C. drawn from the point of maximum fo rce and deflection to the va lu e of the restoring force required to rerum the bellows to zero deflection, becomes line C' when transferred to the o rigin . A working spring rate based on line C' can be used. Thi s reduces the discrepancy between the indicated and true va lues a lthough the difference can sti ll be sign ificant. For the g reat majori ty of applications. the manufacturers publ ished spring rates have proved sati sfac tory. However. whe n the critical nature ofa partic ular application warrants morc precise knowledge of the bellows working spring rate. the user should require the manufacturer to supply infonnation as to th e mea ns by which his data was deve loped. In special cases. prototype testing [Q determine the precise load vs . deflection characteristics ofa particular bel lows des ign may be necessary.

4-26

V I::xpanslOn JOint Manutacturers ASSOCiation. Inc.

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STA NDA RDS OF THE EX PAN SION JOINT MANUFACTURERS ASSOCIATI ON. INC.

//

///1 / I

FOR CE

DEFLECTIOH

/

/

GENERAL CURVE OF BE LLOW S FORCE

VS

DEFLE CTION

FIGURE4 .12 4.12.1.8 CORRELATION TESTING The equations in Sections 4. 13.1. 4.13.1. and 4. 13.3 can be employed to design a bellows if they have been correlated wi th actual test results to demonstrate predictability of nlplurc pressure_ meridional yielding. squinn and cycle life for a consistent series of bellows of the same basic design (unrcinforccd and reinforced bellows arc considered as separate designs). A minimum affive meridional yield-rupture leSIS on bellows of varying sizes. with not less than three convolutions. are required 10 vcrify Equations (4-29), (4-30), ('""-31). (4-28), (4-44), (445). (4-37), and (4-56), A minimum of len

squinn tests on bellows of\'arying diameters and number of convolutions are rcquircd to vcrify Equations (4-35). (4-49) and (4-60). A minimum oftwenty-fivc fatigue tests on bellows of varying diameters. thickncsses. convolution profiles arc required to construCt a fatiguc life versus combined stress plol. The eITects of pressure shall be considered in the fatigue tests. The test bellows must be representative of typical bellows design and manufacturing processes.

4.12.1.9 BE L LOWS I-I EAT TR EATMENT Heat trcatmcnt after forming can havc a dctri mental effect on bel lows prcssurc

capacity. If is not normally considered beneficial for fatigue life to either stress relieve or anneal after fomling. The necessity for this form of heat treatment is the responsibility of the purchaser and shall be considered individually.

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4--:!7

STAN DARDS OF THE EXPANS ION JOINT MANUFACTURERS ASSOC IA TlON. INC. 4.13

DESIGN EQUATIONS 4.13. 1 DESI GN EQUATIONS FOR UN REINFORCE D BEllOWS

Bel lows Tangent Circumferential Membrane Stress Due to Pressure

SP(D, +I1I)'L,£, k ,- 2( ntE/r L,( D,, +f1/)+f, kE , L, D. )

(4-27)

Co ll ar Circumferential Membrane Stress Due to Pressure PD', L,£ , k

S',

(4-28)

2 (11I£, L, (D, +111) +I,k£, L, D, )

Be llows Circum ferential Membrane Stress Due to Pressure S~ = PD~t K~ q .

(4-29)

2.4,

Bellows Meridional Membrane Stress Due to Pressure Pit' S,= - -

(4-30)

-'111 "

Bellows Meridional Bending Stress Due to Pressure

S, =

!:...(~)' C 211

Ip

(4-31 ) P

Note : The above stresses should be eval uated for pressure capacity as fo ll ows:

5, & S! :s: C...f, S,,J,

5', s e. ,s",

S.l +S~$CmS 1.33KS"b Sf)::::: 1.55"" 511 ::::: 1.5S,,1> In the creep ran!!e S~I

57/+ - -

andS~,

1.25 59::::: 1.255""

S~f

+ - ' - 55"" 1.25

511 ::::: 1.255,,1> Bellows Meridional Bending Stress Due To Deflection 5Eh le

3",' (1.0+31~ ".)

(5-30)

Note: Modulus of elasticity. En. in equation (5-30) is at room temperature.

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r bpansion Joint Manufacturers Association. Inc.

5-7

STAN DA RDS OF TH E EX PA SION JOINT MANUFACTU RERS ASSOCIAT ION. INC. Bellows Deflect ion Due To Pressure (beam mode) At Center of Span and Midpoint of Bellows Length PNqL/

v

.

~ml"

(5-31 )

384£, 1 P(Nq + 2L, )'

(5-32)

32£/,1, J If 58lu '::;: 1 .33K~lIh. the n YhmJ= If

S 8111:>

-"b",llI

1.33K,S"". then Ybmf = Y"mlb

PNqL,"

(5-33)

384£,1 P(Nq + 2L, )'

(5-34)

32£/,1,1 If SH,,,,::: 1.33K.,S"h. then Ybms = )""",...1

If 5 /(." > 1.33K,S"", then Y bms = Yl>m~b OICS:

Irthe tangent is flill y supported against the pressure, sel Lt = O.

If N- I . set ),1>",1 and )'hm.• = O. Fat igue Life (5-35)

w here a, b. and (' arc material and manu facturin g constan ts. Fati gue data must be fumi s hed by indi vidual manu fac turers. 5,= C l' S9 ~ S/(J

c.,

1

Bellows T heoret ica l Axial Elastic Spring Rate E~11I 1 (LI + LJ

(5-36)

The effect of comer configuration (see Figure 5.10) is not considered equation 5-36. Corn er config uration will not signifi cantly effec t the spri ng rate perfo nnance w hen the length of the shortest side exceeds l Ow: L, / H' > [0 . When this va lue is less than 10. consult the bellows manu facturer for information. longitudinal bending stress and mid-poim deflec lion can be reduced by the addition of intermediate supports along the span .

5·8

.:: E;\.pansiull Juint ManufactuTt!1"S Association. Inc.

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STAN DARDS OF TH E EXPANS IO N JOINT MANU FA CTURERS ASSOCIATIO . INC.

SINGLE MITER CORNER

ROUNDED CORNER

CAMERA CORNER

DOUBLE MITER CORNER

TYP ICAL CORNER CONFIGURATIONS

FIGU RE 5. 10

( Expansion loint

Manufaclure~

Association. Inc.

5-9

STANDARDS OF T HE EXPA SION JOINT MA UFACTU RERS ASSOCIA TI ON, I C.

This page intentionally blank.

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STANDARDS OF THE EXPANS ION JOI NT MANUFACTURERS ASSOCIATION. INC. SECTION 6 - Q ALITY ASSURANCE AN D BELLOWS FORMING METHODS

This section describes the minimum quality control program requirements for a manufacturer of metallic bellows type expansion joints inclusive of the product design and compli ance to customer specifications. These requirements pertain to th e inspections and tests necessary to substantiate product confonnance to drawings. specifications and contrac t requirements. The program shall assure systemat ic and adequate qual ity control throughout all areas of contract perfonnance: for example. product deve lopment. material selection. fabrication. processing. assembly. inspection. testing, delivery preparation and shipment. storage and maintenance. for which comprehensive written procedures shall be used and maintained and made available for customer review ifrequesred. These quality control program requirements shall apply when a customer specification identifies an expansion joint to be "designed and manufactured to The Standards of the Expansion Joint Manufacturers Association". These section requirements shall be in addition to and shall not conflict with any other contractual agreements. 6.1 GENERAL An effective and economical quality cOnlrol program shall be developed. considering the manufacturer's faci li ties and products. The necessary scope and detail of the program shall depend upon the complexity of the work being perfonned and on the size and capabilities of the manufacturer. All supplies and services under the contract. whether manufactured or performed within the manufacturer's plant or al any other source. shall be controlled at all points necessary to assure conformance to the contractual requirements. The program shall provide for the prevention and prompt detection of non-confonnities and for timely and positi ve corrective action . The following is a guide to the features which sha ll be included in the written description of the manufacturer's quality control program and shall be peninent to both shop and field work. 6.2 AUTHORITY AND RESPONSIBILITY

Effective management for quality shall be clearly prescribed by the manufacturer. Personnel in charge of th e design, manufacturing. testing. and quality functions shall have sufficient and well defined responsibilities. the authority. and organizational freedom to identify and evaluate quality problems and to initiate. recommend, or provide solutions. Management shall regularly review the status and adequacy of the quality control program. The quality program shall be certified and monitored by an intemationally recognized standards authority. 6.3 QUALITY ASSURANCE ORGANIZATION An organization chan showing the relationship between management. engineering, purchasing. manufacturing. inspection. and quality control is required to reflect the actual organization. The purpose of this chan is to idemify and associate the various organizational groups within the particular function for which they are responsible. 6..1 ORA WINGS, DESIGN CALCULATIONS, AND SPECIFICATION CONTROL The quality control program shall establish comprehensive wrinen procedures which will assure that the latest applicable drawings. design calculations. specifications. and manufacturing processes required by the contract. as well as authorized changes. are in use for manufacture. examination. inspection. and testing. The manufacturer shall assure that requirements for tbe effectivity poiut of changes are mer. and that obsolete drawings and cbange requirements are recalled and replaced from all points of issue and use. The manufacturer shall maintain a record of all customer approved drawings. specifications. and all drawing re\·isions pertinent to the contract provi sions.

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6,]

STANDARDS OF THE EXPA SION JOINT MANUFACTURERS ASSOCIATIO . INC. 6.5 MATERI ALS Al'l D MATERIALS CO NTROL

A. Supplier's material s and products shall be subject to receiving inspection to the extent necessary to assure that the malerial is properl y iden tified and has documentation including requ ired certi ficates of compliance or material test' report's showing conformance to the manufacturer 's contractua l specifications. The quality control program shall assure that raw materials to be used in rabricat-ion or processing of produc(s con rom, to the applicable physical. chemi cal, and other tech nical requirements. B. Raw material awaiting testing must be separately identified or segregated fro m already tested and approved material but can be released for initial production providing that identification and control call be mailliaillt:d.

C. Material tested and approved must retain its identity until such time as ils identiry is necessarily obliterated by processing. 6.6 M ANU FACT URJ NG PROCESS CONTROL The quaJiry control program must assure that al l basic prod uction operations (i.e. purchasing, handling, machin ing, assemb ling. fabricating. processing. inspection. testing. etc.) of any rype shall be describcd in com prehensive and comp lete written documented instructions. Such instructions shall provide the criteria for perfonning the work functions and Lhey sha ll be compatible with acceptance cri teria for workmanship. The instructions are il1lended to also serve for supervising. inspecting and managing work. The preparation and maintenance of and compliance with work instructions shall be monitored as a function of the qual ity control program. 6.7 I N-PROCESS I NS PECTION AND EXAMINATION PROGRAM

A. The qua liry control program shall describe the fabrication operations. including inspections and examinat ions. suffic iently to pennit a customer or designated inspector to de tennine at what stages specific inspections and examinations are to be perfonned. and to positively identify the current inspection status of the product. The manufacturer shall prepare. maintain and use comprehensive written procedures addressing the in.process and final inspection operati ons that are to be perfonned in the course ofmanufacntre and testing. These procedures sha ll specify the dimensiona l checks. visual inspection. nondestructive tests, and other pertinent operations that are to be perfonned to determine that the product meets contractua l specifications. The procedures shall spec ify the app li cable acceptance standards and shall provide for a means to document that key operations have been pClfomled and the results delennined to be satisfactory. B. The qualiry control program shall assure there is a system for final inspec ti on and test of completed produc ts. Such inspection and testing sha ll provide a measure of overall quality of the completed product. When modifications. repairs or rep lacements are required afler final inspection or testing, there shall be re·inspection and test ing of any characteristics affected. C. The inspector represent mg the customer shall have access at all limes. whi le work on the contract is being performed. 10 all parts of the manufacturer's plant that concem the manufacture of the product ordered. The manufacturer shall afford the inspector reasonab le facilities to satisfy the inspector that the product is being fumished in accordance with the contract spec ifications. In ~pection sha ll be made at the place of manufacture prior to shi pment. unless othenvise specified. and sha ll be sc hedul ed not to interfere unnecessarily with the operat ions of the manufacturer. This requirement also applies 10 all subcontractors and vendors.

6-2

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STANDARDS OF THE EXPANSION JOINT MANU FACTURERS ASSOCIATION. INC. 6.8 MEASURING AN D TEST EQU IPME NT CONTROL The manufacturer shall have at his di sposal gages and other measuring and testing equipment necessary to assure that material s and supplies COnf0n11 to the technical requirements specified. A system of comprehensive written calibration procedures shall be maintained. In order to assure continuous accuracy. the procedures shall include a schedule for equipmem ca libration against certified measurement standards which have known valid relationships to National Reference Standards. Defect ive equipment must be repaired. replaced. or fe-calibrated as appropriate to the techni cal requirements specified. This requ irement also applies to all subcontractors or vendors. 6.9 MATE RIAL NON-CONFO RMAl\CE CONTROL The manufacturer shall estab li sh and maintain an effective and positi ve system for promptl y detecting and correcting materials or conditions ad verse to quality. in cluding comprehensive written procedures for theiT identifi cation. segregation. and disposition. All non-collfonn ing materials shall be pos itivel y identified and segregated in a unique holding locat ion to prevent unauthorized use, shipment, or the intermingling with acceptable conforming materials. Repair or rework of non-conform ing materials shall be in compliance wi th comprehens ive written procedures. 6.10 CO RRECTIVE ACTION (SUPPLIES AND SERVICES) Des i&'ll. purchasi ng. manufacturing, inspection. testing or other operat ions wh ich cou ld result in. or have resulted in non-con[onning supplies. services, facilities, technical data, standards or other e lemems of comract perfonnance must be identifi ed and changed as a resu lt of the quality control progra m. Corrective action shall extend to the performance of all suppliers and vendors. Corrective action shall include as a minimum: a.) analysis of data and exa mination of product scrapped or reworked to determine extenl or causes. b.) analysis of trends in processes or pcrfonnance of work to prevent recurrence of non-confonnances. c.) introduction of required improvements and corrections. initial review of the adequacy of stich measures and the cont inued monitoring of the corrective action effectiveness. 6.11 WELDING Unless otherwise specified by contractual agreement. the welding personnel and procedures shall be qualified in accordance with the applicable sect ions of Sec lion IX of the ASME Boi ler & Pressure Vessel Code or equivalent for all pressure containing welds. 6.12 HEAT TREATMENT Unless otherwise speci fied by contractual agreement. heat treatment. when required. shall be perfomled in accordance \"ith the ASME Boiler & Pressure Vessel Code requirements or equivalent or the recommendations of the material manufacturers. 6.13 PA C KAGING. PRESE RVATION, SHIPPING AND STORAGE The manufacturer shall utilize standard commercial practices in packaging. preservation. shipping and storage to assure protection of the product during shipmen!. unless superseded by contractual agreement. These commercial practices shall bc adequate to prolect the quality of the products fabricated from deterioration to the point of final destination.

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6-3

STANDARDS OF THE EXPANSION JOINT MA UFACTURERS ASSOClATION. INC. 6.14 CUSTOME R Q UA LITY ASSURANCE AUDITS

Documents. procedures. and processes sha ll be comprehensively written and ava ilable for review by the customer specify ing their implementation. or a third party inspection agency authorized to act in the customer's behalf. 6.15 RECO RDS RETE NTION

The manufa cturer sha ll use and maintain all adequate records or data essential to the economical and effective operation of this quality con trol progra m. The records shall. as a mini mum, indicate the nature and number of observations made. the number and type of deficiencies found. the quantities approved and rejected and the nature of the corrective actions taken . The quality cont rol program sha ll assure the records are complete and reliable. Also. the records for monitoring work perfonnance and for inspection and testi ng shall indicate the acceptability of work or products and the corrective action taken in connection with defic iencies. The quality con trol program sha ll provide for th e analysi s and use of these records as a basis for managemel1l rcv iew. 6.16 METHODS OF FORM I NG METAL BELLOWS

The following are examples of commonly lIsed bellows fomling methods. Only seamless tubes or longitudinall y welded mcta l tubes are all owed tor use w ith fomling methods 6. 16.1 Ihru 6. 16.6. 6. 16. 1 ELASTOMERI C FORMI NG

A rube is inserted over a mandrel containing a rubber torus. Axial force on the mandrel expands th e torns, fo mling a bulge in the tube. The torus is then relaxed and the bulge is axiall y compressed into a convolution by external dies. Convolu tions arc formed one at a time. The rube is free to shorten as the convolution is fomlcd.

. 1

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2

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i;. Expansion loint Manufacturers Association. Inc.

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STANDARDS OF THE EXPANSION JOINT MANUFACTURERS ASSOCIATION. INC. 6.16.2 EX PANS ION (EXPANDI NG MANDREL) FORM ING

Indi vidual convolutions are fomlcd in a nlbe by an expanding intemalmandrel. Flat spots are minimized by ex pand ing the mandrel partiall y. and rotating the rube slightly. This process is repeated until all intennediate cOin-olution height is achieved . Each convo luti on is subsequently sized by means of speciall y contoured inner and Olltcr rollers.

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3

6.16.3 HYDRAULIC FORMING

A rube is placed in a hydrau li c press or bellows fanning mach ine. Circu lar external die rings of sui table contour are placed ou tside the tube at longitudinal intervals approximately equal to the deve loped length of the completed convo lutions. The tube is filled wi th a medium such as waler and pressurized until circumferential yield ing occurs. This forming operati on con tinues with a simultaneous circu mferen tial yield ing and controlled longitudinal shortenin g of the tube until the proper config uration is obtained. Indi vidual or multi ple convo luti ons may be fonned by this method. Depending on the bell ows configu ration, several partial-forming steps with inrennedi atc hear treatment may be required. Reinforced be ll ows may be formed by utilizing external reinforcing rings that act as part of the forming dies. After com pl etion. when the dies are removed. the rings rema in as an integral part of the bellows.

P~ESSURE

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Expansion Joint ManufaclUrers Association. Inc.

6-5

STANDARDS OF THE EX PANSION JOINT MANUFACTURERS ASSOCIATION. INC. 6.1 6.4 PNEUMATIC T

BE FORMI NG

This method is identical (0 "Elastomeric Forming" excepllhat the initial bulge is fomlcd by pressuriz ing a rubber " inner rube"",

.. 2

1

3

.

6. 16.5 ROLL ED CONVOL UTED SH EET

A flat sheet is mechanically convoluted by either the press-brake method or the roll forming method modified to produce straight secti ons. ThI s pre-fo nned rail is then rolled imo a tube . The bellows is completed by longitudina ll y welding the convoluted ends of the rail together.

2

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6-6

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Expnnsion Jo int Manll facturers Associu;ion. Inc.

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STAN DA RDS OF THE EXPANSION JOINT MANUFACTURERS ASSOC IATION. INC. 6.1 6.6 ROLL FORMING A tube is placed in a fenning machine and individual or mu lt iple convol uti ons are fo nned by means of pressure exerted by fonning wheels. Generally. the wheels are on both the in side and outside of the rube . Controlled longitud inal shortening of the bellows rube occurs during the fo nni ng operation. The tube may rotate about fixed-s haft fanning whee ls. or the rube may be fi xed and the wheels rotated about the rube's circumference. The exnmple below shows the fixed-shaft method .

3

2

1 6.16.7 ROLLED RING

A fTa! sheet is fomlcd into a single convolution and then ro ll ed into a ring . The ring is completed by a longitudinal weld across the convo lution. If more than one convolution is desired. the bellows is bui lt up by a series of circumferential welds joining the convo luti ons together.

1

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( Expan:.ion Join! /l.lanufaclurt=n; Association. Inc,

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6-7

STANDARDS OF THE EXPANSION JOI NT MANUFACTURERS ASSOC IAT ION, INC. 6.16.8 PRESS-BRAKE FORMING A flat sheet is convoluted using a press· brake die to form the individual convo lutions. This method is used primarily in the manufacture of be llows for rec lan gular Ex pansion Joints described in Sec tion 5. Many convolution profi les can be ach ieved using this method. The 1110St com mon slyies are the "U" profile and "V" profiles shown in Figure 5.9. Materia l availabi li ty and press-b reak Too li ng lim it the length of lhe rail. Longer lengths can be manufactured by spli cing the rails together with longi tudina l welds.

2

3

6.16.9 C OMB INE D FORM ING Some of the methods described in previous sect ions can be combined. One procedure for fonnin g a toroidal be ll ows (Figure 4. 15) combines two methods. A convo lUlion is expa nsion FOfmed with a convo lution height grealer than the fi nal desired torus height. The convolution is loca ted betwee n Forming rings si milar to hydmulic forming. The rings are thell pushed rogcther and the toroid is hydrau lically formed.

1

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(" Exp:msiull Joint i\:lanutb clurcrs Associ:.IIion. Inc.

PRESSURE

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STANDARDS OF THE EXPANS ION JOI NT MANUFACTURERS ASS OCI ATION. INC. 6. 17

FABRICATION TOLERANCES This Section covers standard manufa cruri ng tolerances for fabricated assemblies containi ng Expansion Joinls. Ifrequired. closer IOleranees than those indi cated may be ob tai ned but must be subject 10 agreement between the purchaser and the manufacturer of the Expansion Joint. Flanges for Round Expansion Join ts (U p to 96 in. Nominal Diameter)

Standard Flanges: Flanges 10 standards such as ANSI 816.47. 816.5. MSS S P44. A WW A C207

Dimensions and tolerances confonn to the standard.

Non-Stal1dard Machined Flanges: Including plate fl anges wi th standard drilling

Flanges to be faced and drilled. Drilling tolerance for bolt, c ircle and hole location same as standard. Min imum thickness to be specified All dimensions arc nomina l.

NOI1-Swndard Unmachined Flanges: Rolled angle, roll ed bar. flame cut plate fl anges. etc.

LENGTH TOLERANCE (Measured between working points):

± 118 in. up through 3 fl. ± 1/4 in. above 3 ft. through 12 ft. ± 3/8 in. over 12 fL TH IS SYMBOL DESIG NATES WORKING POINT:

~

Flanges must be installed so that bolt boles straddle a common centerline within 1/ 16 in .. NOTE: Good practice suggests that one mating flange in the piping system remain unwelded until the Expansion Joint has been located in position.

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~-~

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,. iL ___ JijI ~ be

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FIGURE 6.1

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STAN DARD S OF THE EXPANSION JO INT MANUFACTURERS ASSOC I ATIO . INC

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For bevel detail see Figure 6. t2

1 ~---1fl1

=="""I"1~---1 ~

--.J...IM ___

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Penni ssib le varialion of 5pecificd diam eler and ou t of roundness at the weld bevel sha ll be in accordance with the rollowing : 24 in. diameter or less in accordance wi th pipe spec ification. Over 24 in. diameter: Outs ide diameter 0.5% of the specified outside diameter based on circum fere ntial measurement. Out-of-roundness: Difference between major and minor diameters not to exceed I % of nominal d iameter. FIGURE 6.2

For bevel detail sec Figure 6.12 . ___-"

f}i-'U]

rr ---, -

I I I

--'-- Permissible variation of specified diameter and o ut of roundness at

7

I .1

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BASE

the weld bevel shall be In accordance with the following:

_1

•

I I

f::t - - -- -l

24 in. diameter or less in accordance with pipe spec ification. Over 24 in. d iameter: Outside diameler 0.5% of the specified outside diameter based on circumferential measurement. Out-of-roundness: Difference between major and minor diameters not to exceed 1% of nomillal diameter. FIGURE 6.3

6- 10

ltoJ'/~

> ]1 '2 102 >2 C onvolution Heioht (w) 3 toJl~ > 31/z 104 >4 C om'oluti on In side Dia meter (D b) < 8 58 > 8 5.8 to 24 > 24 to 48 > 48 1060 > 60

+ 1'4

± 932 • •

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± 5 16

BEL LO WS MANU FACTU RI NG TOL ERANCES FIGURE 6.1 3

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Expansion Joint Manufacturers Association. Inc.

6- 17

STANDARDS OF THE EXPANSION JOI NT MA UFACTURERS ASSOC IAT IO '. INC. It is imponam that the fit of the bellows tangent be tight to the duct. nUllge. or other method of end attachment being used. Figure 6.14 shows two examples with the bellows tangent attached using a preferred method and a non· prefcrrcd method. Ha mm er in g of th e bell ows l a ngenl 10 ac hieve t h e no n-

prefe rred attac hm ent is nol accepta ble.

Weld end with preferred tangent attachment.

Flanged end with preferred tangent attachment.

Weld end with acceptable but not preferred tangent

Flange with acceptable but not preferred tangent

Tangent is angled and not tight to the duct

TANGENT ATTACHMENTS FIGURE 6. 14

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STANDARDS OF THE EXPANSION JOINT MANUFACTURERS ASSOCIATION. I C. SECTION 7 - EXAM INA TlON AND TESTING

To ass ure a purchaser that the product has been properly designed and manufactured requires some method of examinat ion andfor testi ng of the product. It is not the intenti on of these sumdards to give detailed procedures for performing any examinat ion or test. but rather to give a general descripti on of some examinations and tests used to evaluate bellows Expansion Joints. Any of the following examinations/tests may be perfonned on Expansion Joints when specifi ed. It is primarily the responsibil ity of the purchase r to specify which methods wi ll be required and the acceptance cri teria. Unless otherwise spec ified. in spection methods. acceptance criteria and inspector qualification should be in accordance with the la test edition of the ASMEIANS I Piping Codes and the ASM E Boiler and Pressure Vessel Codes. 7. 1 NON-DESTRUCT I VE EXAM.INATION 7.1.1 RADIOGRAPHI C EXAMINATION

Radiographi c examination is based on the principle that extremely high freq uency light waves. usually x-ray or from a radioacti ve sou rce such as Cobalt 60. will penetrate so lid material s and. when projected onto a photose nsiti ve film , will reveal vo ids. areas o f discontinuity. and lack of homogeneity . Thi s exami nati on is wide ly used in evaluating the soundness of welds and in ge neral. is limited to eva luating butt welds of parts of substantiall y the sa me thi ckness and material. In the case of beHows. this is nonnally limited to the evalua ti on of longitudinal seam welds before forming. Unless requi red by the purchaser, radiographic examination of the longitudinal seam ofa bellows need not be specified. Examination of the longitudinal seam ca n be accomplished by some other means, such as liquid penetrant examinat ion. Ifa radiographic examinati on is required 011 the longitudinal seam of a bellows then it should be performed before the bellows is convoluted. After the forming operation. it is usua ll y not possible for the source or the film to be placed to yield a meaningfu l radiograph . Radiograpbic examinati on of the bellows artacJunent weld sho uld not be specified. Interpretation of such radiographs is impractical due to the weldment geometry, differences in thickness and penetrability. In view of tile above. and recogniti on of the attachment weld as a sea l weld, non-destmctive examination of th is weld shou ld be accomp lished by some other means such as liquid penetrant exa minatioll. 7.1.2 LIQUID PENETRANT EXAMlNATION

Liquid penetrant examination consists of cleaning a surface, coati ng it with a dye. wiping the dye off and coating the surface with a developer which after sufficient time wi ll draw the dye from the cracks. pin holes. and make them apparent to the observer. Liquid penetrant examination is limited in scope to detecting surface indications such as fine hairline cracks. pin holes and we ld roU-over. With the tbin material used in be ll ows. the probability of any defect remaining subsurface is unlikely. This examination is frequently used in evaluating be llows welds. The bellows base mate rial may also be inspected by Lbis method but shall be perfonned prior to convo lution form ing. The developer used in thi s procedure acts as a blotter: therefore. when rechecking a questionable indication it is absolutely essential to reclean tbat area and reapply dye and developer. Unless otherwise specified, examination procedures sha ll coufoml to the requ irements of ASTM-E 165.

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Expansion Joim MnnufaclUrers Association. Inc.

7-1

STANDARDS OF THE EXPANS ION JOINT MA NU FACTURERS ASSOCIATION. INC. 7.1.3 FLUORESCE 'T PENETRANT EXAM I NAT ION

Fluorescent penetrant examination is similar in purpose to the liquid penetrant examina tion but is accompli shed by the use of a dye which con tains a fluorescent materi al and developer. The parts be ing in spected are examined in subdued light under an ultraviolet light SOUTce. Pans mu st be thoroughl y cleaned prior to lesting. Sca n the parts wi th the ultraviolet light before appl ying the flu orescent material since hydrocarbons. greases and oi ls. and lint may give mi slead ing indicati ons. Depending on the fl uorescent material llsed in the exec ution of Ib is examination, there are varyi ng leve ls of sensiti vity. and the purc haser must state the material to be used. Fluorescent penetrant exami nat ion is lim ited to determining the presence o f surface defects. It wou ld be a dup li cation to require both th e liqui d penetrant and flu orescen t penetrant examination fo r the same components of an Expansion Joint. 7. 1.4 MAGNETIC PARTI CLE EXAMINATION

Magnetic particle examinal-ion consists of coating a surface with fi nely powdered iron and establi sh ing a magnet ic fie ld in the materi al being examined. The presence of discontinuities or irregulari ties in the magnetic fi eld, as indicated by the lines of powdered iron. will indicate surface and a lso subsurface defects, cracks, slag inclusions. and lack of we ld pen etration . Thi s examination is limited to magnetic material and wi ll not indicate deep subsurface defects. Although generally used for exa minati on of we lds. it is poss ible to exami ne base material if there is reason to suspect materia l defects such as lam inated plate. 7.1.5 ULTRASONIC EXAMINATION

Ultrasoni c examination uses high frequenc y sound waves to detect fla ws. and is uscful in determining thi ckness. depth. and exact location of defects. Interpre tation of in di cations in sections of sharply varying thi ckness is difficult. The examination is not limited 10 any group of materia ls. 7.1.6 HALOGEN LEAK EXAMINATION

Halogen leak examination utilizes a probe of suitable design which selective ly indi cates the presence of halogen gases. This examination is more sensi ti ve than a hydrostatic test o r air jet leak examination but since it is done at low pressures. it can on ly dcteml ine the presence of a lea k and can not validate the structu ral in tegrity of tht item being exami ned. A halogen leak examinati on must be performed in a suitable area since many gases common to manufacturing plants will give indications. Thi s examination is helpful in not onl y detemlining the presence ofa leak. but a lso in locating that leak. The acceptance criteria is failure to detect lea kage in excess of that specified by tbe purchaser.

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STANDARDS OF THE EXPANSION JOINT MANUFACTURERS ASSOCIATION. INC. 7.1.7 MASS SPECT ROMETER EXAMINATION

Mass spec trometer examination is an extremely sensiti ve means of dClcmlining the presence of a leak. The gas lI sed is he lium. The examination is more sen sitive than would be required for common commercial installations and is normall y specitied where Expansion Joints are for lethal gas service. explosive environment service. or high vacuum serv ice. 10 Mass spectrometer exami na tions are capab le of detecting leakage rates to 10. standard cubic centimeters per second. The Expansion Joint may be examined for the sum total of leakage or with a probe to locate indi vidual leaks. When the probe method is employed. se nsiti vity is limited to between 10-6 and 10' s standard cubic centimeters per second . The acceptance criterion is the absence of leakage rates in excess of that specified by the purchaser. 7. 1.8 A IR J ET LEAK EXAM INAT ION

Air jet leak examination utilizes compressed air is directed through a nozz le on lO a small area between 1\1,10 we lded parts. A leak detector solution is app li ed on the opposite side of the welded connection which will bubble up if the compressed air is able to pass through the weld. TIli s examination is useful on low pressure Expansion Joint bell ows end connection welds where other fonlls of exam ination and testing are nO! practical. 7.2 NON-DESTRUCTIVE TESTING 7.2. 1 PRESS URE TESTING

Hydrostati c and pneumatic are two types of pressure tests that can be perfomlcd on an Expansion Joint. Hydrostatic pressure testing invol\es filling the Expansion Joint with a liquid. usuall y potable water. while pneumatic pressure testi ng involves fillin g Lhe Expansion Joint with air or other gas. After the Expansion Joi nt is filled it can then be pressurized to the required test pressure. Pneumatic pressure testing is hazardous and it is recommended that specia l precautions be taken. Nonnally. the required test pressure is a multiple of the design pressure. Expansion Joints placed in high temperature service may require the pressure test be performed at an adjusted pressure. It is imperative that the test pressure does not produce a membrane stress in excess of yie ld strength or cause permanent defommtion or instability (squi nn) of the bellows at rest temperature. It may be necessary to reduce the test pressu re adjusted for tem perature. to the maximum pressure that will not exceed yield or cause instability: An Expansion Joint shou ld not be subjec ted to a tesl in the field at a higher pressure than was used in the manufacturer's shop without the manufacturer's knowledge. All anchors and guides must be installed (See Seclion 2.10) and shipping devices removed prior 10 such testing. In the case of large Expansion Joints. addit ional su pports may be required to support the we ight of the water used during hydrostatic testing. A pressu re test is not only useful for detecting leaks but is also a way to test for bellows squ iml. meridional yie ld and rupture. (See Sections 7.3.~ and 7.3.3)

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7-70

STAN DA RD S OF T HE EXPANS ION JO INT MANU FACTURE RS ASSOCIATIO N. INC. 7.3 DESTR UCT IVE TESTING Destructive tesling wi ll rende r the Expansion Join t or at least the be ll ows unsuitab le fo r insta llati on in an o perati ng syste m. These tests then must be perfonned on a prototype Expansion Join!. A prototype Expansion 10int is deti ned as one having the same pressure and temperatu re rat ing as produ ction models. iden tical diameter. heig ht , pitch, and general shape of the convolution . the thi ckness and rype afbeHews materi als. be ll ows reinforcement. method of man ufa cture, and maxi mum movement per convolution. Si nce it is more pract ical to test an Expansion Join! under axia l movement rather than combined movement it is acceptable to use equivalent max imum ax ial move ment as calcu lated in Section 4. 7.3. 1 FATIGUE LIFE T ESTI NG Fat igue life testin g is a verifica tion of the ability of a be ll ows to wi th stand a gi ven number of tlex ing cycl es. It is reco mmended that the be ll ows subjected to fa ti gue life testing be ident ified by the parameters in Table I. With all olher shape fa ctors remaining constant, cycle li fe wi ll generally increase with di ameter: fo r prototype testing, it may be acceptable to cycle tes t the smallest size Expans ion Joint being fu m ished fo r a given series fo r identical servi ce conditioll . It is also acceptable to cycle test at room temperature any Expansion Joint which will be fu mi shed for opera ti ng temperatures up to the active creep range. For Expansion Joints o perati ng above thi s range. consideration shoul d be gi ven to testing at elevated temperatures. Fat igue testi ng Illay be performed at cons tant pressure or at varying pressure. Thi s latter conditi on more closely approx imates the service to whi ch the Expansion Joint will be subjected. When the system designer spec ifics the mi nim um number of cycles. th is number shoul d be consistent wi th the li fe of the system in which the Ex pansion Join t is to be installed. Excessive cyc le li fe req uirements will LlOt necessa rily cnsure desired results. 7.3.2 SQU IRM TESTING The obj ective ofa squinn test is to determine the intem al pressure whi ch will cause a be ll ows to become unstable. Squi rm is de fin ed on the basis ofa change in pi tch of [he bell ows cOll vo luti ons un der in terna l pressure. Identificat ion of the bellows should be establi shed using the parameters in Table II. The fo ll owing is a recommended test procedure: The Ex pansion Joint should be placed in a suitable fi xture with the bell ows fixed in the stra igh t position wh ich will effectivel y seal the ends duri ng pressuri zati on and mosl importan tly. will prevent any movement of the ends during testi ng . The be llows may be tested with its axis in ei ther the horizontal or vertica l positi on. The testi ng mediu m shall be water for purposes of safery. If the expan sion joint's operating cond itio n is 10 be in the horizontal pos ition and the bell ows e lement is of an extreme ly tlexible nature then a tesl in the horizonta l position may be preferred. The convolutions o f the be llows during testing should nOI be restrain ed by ex temal means. unless such restra ints fo ml an integral part of Ihe fi nal assembly. T he test spec imcn should be in strumented. such that th e resultant latera l deflecti on of lhe center one or two convol utions. and the change in pitch of a ll of the convol Uliol1s. c~m be accurately detennined. The former may be obtained by vectorially adding the deflections measured by two mutuall y perpendicular dia l gauges. Pitch measurements should be made ill the plane of maximu m convolution defl ection.

7-'

..0 Expansion Juin! Man ufd..:imCI:'

A:>~m;j sp tt > sp tt=sp ttln < sp B-2.5.2 B-2.5.3 B-2.5. 1

Circumferential Membrane (S~ )

Same

Decreases

Decreases

Decreases

Meridona l Bending (SJ

Increases

Decreases

Decreases

Usually Decreases

Fat igue Li fe

Nomina l Change Increases

Decreases

Increases

Spring Force

Usuall y Increases Decreases

Increases

In-plane Stability

Decreases

Increases

Inc reases

Column Stabili ty

Decreases

Lncreases

Increases

Usually Increases Usua ll y Increases Usua ll y Increases

tt =

total thickness

sp = sing le pl y construction I

n = num be r of pli es

FIGURE 9. 1 Multi- Pl y Response when Compared to an Equ iva lent ly Designed Single Ply Bell ows 9. 1.4

M ULTIPLE MATERIAL USAG E Corrosion conSiderations may indicate the desirability of different materials for the inner and outer bdlows plies to suit the internal I external environment. In this manner the primary ply specified to resist corrosion can be supplemented by less costly add itiona l plies.

9-2

C E;\.pan"ivII Juiul MUlIUf.u.;lurt'l!> A:.:.ocialion. Inc.

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STANDA RDS O F THE EXPANS ION JOINT MANUFACTURERS ASSOCIATI ON. INC. 9.1.5 RED UN DANT PLY CONSTR UCTION WITH THE SAME T HI CKNESS FOR EAC H PLY AS A S ING LE PLY CONST R UCTION Redundant (\\'0 ply be llows arc used when it is desired to continue Ilomlal system operation ifone ply should fail. until suc h rime as a suitab le replacement can be made. 9. 1.5. 1 PRESSURE CA PA C ITY The pressure capacity of each bellows ply is the same as an equivalent single ply des ign since the redundan t plies have been designed to withstand the system design pressure independently. 9. 1.5.2 FAT IGUE LIF E The effect on fatigue life over that of a single pl y construction will be nominal. 9.1.5.3 S PRI NG FORCES An increase in tbe spring forces will result since the spring rate w ill be higher due to the greater total material th ickness. 9.1.5.4 BELLOWS STA BILIT Y In-plane and column stability are increased due to the greater total material thickness. 9.1.5.5 MONITORED PLY BELLOWS The annular space between plies can be monitored for leakage to detect a ply failure. This will serve as a warning of an impending problem. reducing the chances of a costly unscheduled shutdown.

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( E.... pansion Joint Manufaclurers Association. Inc.

9-3

STAN DAR DS OF T HE EX PANSION JO INT MANUFACTU RERS ASSOCIATIO , I C. 9.2

Ti E RO DS, HI NGES AND S IM ILA R ACCESSO RI ES In a piping syste m containing Expansion Joints. it is frequent ly impractica l to use main anchors to absorb the pressure thrust o r to transmit th is force to the connected equipment. In such cases, the proper lise of tied. hinged. or gimbal Expansion Joints can solve the problem. The u::.t: of sut.:h Expansion Joints requires that the tie rods. hinges or gimba ls and their anachment to the piping be properl y designed to absorb the imposed forces. 9.2. 1 FO RCES AN D LOA DS The thrust absorbing members of an Ex pansion Joi nt are nonna ll y designed to restrain on ly the pressure thrust devel oped within the pi ping system and the force requ irerl to compress or extend the be ll ows due to themla l g rowt h. Ifo ther fo rces are to be cons idered in the Expansion Joi nt design, th is fac t, along with infonna tio n regarding the magn itude and direction of these forces, must be prov ided to the Expa nsion Joint des igner. The addit iona l fo rces to be cons ide red may incl ude the fo ll owing: a. Unsupported we ight of connect ing pipe and insu lati on between a pair of be ll ows. b. Weight of contai ned fluid under operation andlor test conditi ons. c. Wind. earthq uake andlor impact loads. d. Torsion abo ut the longitudi nal ax is. Th'e effects of tempera lure and flow conditions (transient and steady state) must be accounted for in conjunction with the above forces and loads. 9.2.2 MET llODS OF ATIAC H 'I E i\'T T ie rods, hinges or gimbals are artached to the pipe in two basic ways: a. By structures whose pri mary functions arc to transmi t the loads 10 the pipe. b. By di rect alla chment to pi pe fl anges in the piping nm . In th is met hod, the load is transmitted from the ti e rods, hinges or gimbals to the connecting pipe throug h [he fl ange bolts and mating flan ge. 9.2.3 DES IGN C O NS ID ERA nONS 9.2.3. 1 TI E RODS, HIi\'GES AN D GIMBA LS T he major design fac to rs to be considered arc: 3. TI E ROD S Tensile andlor compressive forces due to pressure thru st and other longitud inally applied loads: the bending stresses result ing from connecting the tie rod to its attac hment: the stress concen tra ti on effects in threaded areas. For genera l structura l rigidity to withstand ex traneous loads duri ng handling and installation. it is recommended Ihal minimum lie rocl ditlmelers as a func tion of the size of the expansion joint be in accordance with Figure 9.2. b. HIN GES Hinge plate tensile and/or compressive forces due to pressure thrust and other longitudinall y appli ed loads: bending forces such as those resulti ng fro m weight loads or torsion applied about the longitudinal axis of the expansion joint: shear and bearing forces at the hinge pin hole. Evaluation of the shear. bearing and bending forces in the hinge pin i[se lfi s also required. The bending and ~hcar dTects in the hinge piI: Expansioll Joinl M :1IIlIrm;!UH:r ~ A~~Ul,;i;!llurr. luI,;.

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STANDARDS OF THE EXPANSION JOINT MANUFACTURERS ASSOC IATION. INC. c. G IM BALS Bending and torsional effects in the gimbal ring due to pressure thrust and other longitudinally applied loads. Gimba l rings may be circu lar or square and may be evaluated using the concept of a ring under four point loading and torsionally unrestrained. The hinge plate and pin portions of the gi mbal assembly. as well as the shear and bearing effects at the gi mbal ring pin holes. may be evaluated similar to paragraph 9.2.3. I-b. 9.2.3.2 ATTAC HMENTS TO P IP ING A variety of structural attachments may be used [0 connect tie rods and hinge plates 10 the piping portion of an expansion joint. These may be simple lugs. lugs with gussets or solid single or double plates (or rings) extending comp letely around the pipe circumference. See Figures 9.3 and 9.4 for typical examples. In all such arrangements the stress in the pipe must be evaluated as well as the stress in the structura l member. In the case of lugs or lugs with gussets it may be necessary to evaluate local deflection of the pipe which could impose undesirable stresses in the bellows attachrnem weld and cy lindrical tangent. In high temperature applications involving so lid plate or ring structures, the effects due to differen tial thermal expans ion should also be considered. The published literature provides various methods for evaluating the structure and the pipe stresses individually rather than in combination. Also. most published work assumes that the loads on the pipe occur on infinitely long cylinders. This is not true when the structural attachment is located adjacent to the bellows and dose to an open pipe end. It is. therefore. customary to perfonn the necessary evaluation by means of approximations based on published literature su pplemented by empiri cal methods wh ich experience has shown provide sa tisfactory results. 9.2.3.3 COM PONENT DESIGN STRESS LIMITS Expansion joint load bearing component stress limits are required to compl y with pressure vessel. piping. and structural codes and standards. The stress limits in Table II apply for load bearing component design .

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STANDA RDS OF THE EXPANS ION JOINT MANUFACTURERS ASSOCIATION, I C.

TABLE II Componen t Design S tress Limits T vpc of Stress Co n~~o n ent Tie or Lim it Rods ( Pipe or Tension Round Bar) Compression

K~ x

Max. Membrane plus Bendin!! Max. Shear A verage Shear

0.8 x S 0.6 x S

Max. Shear A veraf.!C Shear Max. Membrane plus Bending A verage Bearin g

0.8 x S 0.6 x S K.~ x S 1.5 x S

Tension or Compression Tension or Compression plus Max . Bending Avcra!!c Bcaring (hole)

S K. x S

Gimbal Rings (Square or Round)

Ma x. Membrane pJus Bend ing Max. Shear (round on ly) A vera!.!.c Shear Average Bearing (hole)

K.' {._

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2

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S.

M

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M 6, = 0

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f:i

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V£/--J.. L../e"- , IbS .

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J.t e M 8J = .. .,,8, ,ill .lbs.

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u

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Z 0 C

~~ ,il1.

-i

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AlLI=O

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e(J. =

,.'"z

n c r

n

",Q

4

Mil ",, 0

. (.,n

~; ,ill.

=

0

Cl

F. =/",c.. ,11I V/.t= O

.c

LATERALANDAXlAL (UNTVERSALBELLOWS)

e~ = N , ill. X

V,, = O

V/ _ ," D.. e, , 1'Wi.

r-== .'r(lJ

E

F" =i.c"ill.

M ,= O

',',_,,_ ,

c C

/~l') ~ ,'. 1it L~ .!i(3L,+!.,) 3 L, + L,

E

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LATERAL (S INGLE BELLOWS)

~

~IIII,IT) I 'V L. · !:L(~l ,, H 3 L, + L, : 't II

F. = f. ,e, , ill . Y;=O

.

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Tempera ture (0C) eF)

460 480 500 520 540 560 580 600 620 640 660 680 700

238 249 260 271 282 293 304 316 327 338 349 360 371

Satu rated Stea m (psig) (barg) 451.3

550.3 664.3 795.3

945.3 1115.0 1308.0 1525 .0

1768.0 2041.0 2346.0 2705.0 3080.0

31.124 37.952 45.814 54.848 65. 193 76.897 90.217 105.172 121.931 140.759 161.793 186.552 212.414

CONV[ RSIO~S

t kPa = 0.145 psig I kPa = 0.01 bar t bar = 10 Nfsq. mm I psig'" U.06895 bar

i. Expansion Joint Manufacturer!> Association. Inc.

D-3

STAN DARDS OF THE EXPANS ION JOINT MANUFACTURERS ASSOCIAT ION, INC APPENDIX D

L, 'I;" l

I' ,-.JJ

!

f I'

.:.------i

t

!

'I"'l I' [~i ~ f I '"-+--' ~ , r=~ ~

WELDING NECK

SLIP -ON

j

~~

:

~----J

I

LAP J OIN T

CLASS 150 FORGED FLANGE DIM EN SIONS (ASM E 165) NOM

FLG

FLG

RF

PIPE SIZE

01A. (00)

THICK (a )

OIA.

WN

SO

LJ

DRILLING

NO. OF

01A.

HOLES

HOLES

BOLT CIRC LE 01A.

OF

Y,

3.500

.438

1.375

1.875

.625

.625

4

.625

2.375

"

3.875

.500

1.688

2.063

.625

.625

4

.625

2.750

1

4.250

.563

2.000

2.188

.688

.668

4

.625

3.125

1Yo

4.625

.625

2.500

2.250

.8 13

.813

4

.625

3.500

1'h

5.000

.688

2.875

2.438

.875

.875

4

.625

3.875

2

6.000

.750

3.625

2500

1.000

1.000

4

.750

4.750

2'h

7.000

.875

4.125

2.750

1.125

1.125

4

.750

5.500

3

7.500

.938

5.000

2.750

1.188

1.188

4

.750

• .000

3Y.

8.500

.938

5.500

2.813

1.250

1.1.25

8

.750

7.000

4

9.000

.938

6.188

3.000

1.313

1.313

8

.750

7.500

5

10.00

.938

7.313

3.500

1.438

1.438

8

.875

8.500

•

11.00

1.000

8.500

3.500

1.503

1.563

8

.875

9.500

8

13.50

1.125

10.625

4.000

1.750

1.750

8

.875

" .750

10

16.00

1.188

12.750

4.000

1.938

1.938

12

1000

14.250

12

19.00

1.250

15.000

4 .500

2.188

2.188

12

1.000

17.000

14

21.00

1.375

16.250

5.000

2.250

3.125

12

1.125

18.750

16

23.50

1.438

18.500

5.000

2.500

3.438

16

1.125

21 .250

18

25.00

1.563

21 .000

5.500

2.688

3.8 13

16

1.250

22.750

20

27.50

1.688

23.000

5.688

2.875

4.063

20

1.250

25.000

24

32 .00

1.875

27.250

6.000

3.250

4 .375

20

1.375

29.500

AU dimensions are In Inches

D-4

(Fl

HUB LENGTH (Y)

Referenc:e Sec:tion 9.3

'1:J E:'I( p.:msion Joint Il.'lnnufnClUrcrs Associmion, inc.

www.cjm

sUlmlcss steels)

1.MOI

XKrN;MoI7. 12~2

\:!-I03ItoL

I.-N 10028·7 (Flu! product';

~taln 1cSl> ~rccb I

l+tW

X1CrNiMoI7-11-!

\2-W 321

E:-.1 IO()!It· 7

~tall1kSsMccl~)

L-I~I

X6Cr"iTi Ill-I ()

(1'101

product>

Name

E:>.r 1110211-2 Al05eS

Flat proouels made of slcl.'l~ fur r~ssurc P"I"jX>IoI:"' Pun 2: Non..allo\' and 0110\ sleels wnh spcci rkd ck\~!cd tcmpomItun:

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BI 10222-5 (sll."!.:1

forgll1g~

55 "IC. )

(~!ccl forgiu!;~

SS etc.)

ropcmc~

14301

X5Crr..:il~-IU

,\1821'316

EN lU:::22 -5

lor ck~.ued

lemrcrnlU~sl

'I.7ns """"

X~Cr~IMoli

"Iccl~

(~tcd forgifl~

~I~cb

lor ck:\aI~" tuW tor pressure pu~s r3n 2, Noo-alio,' and allo\' ~[~'Cltubc~ wl1h M"lCcificd C1cllll,J tern

~aIUn'

12·':

IKr\l~-5

roOl.'n"."",

J~

El\ IU2L7-2

(\\~ld~-d

,tceltub.,..,,)

I·UOI

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1\\~IJcd ~1~ellUbcsl

1.-1-101

XKr'iMoI7-12-2

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1,733:-

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.1~""'IIJb:

0.2f>

046

100

125

0,42

0..10

0.62

0.58

0.52

0.56

0.62

0..17

0.52

0.41!

0.85

125

150

0.61

05~

0.90

0.8-1

0.75

O.S:!

0.90

0.'"

0.76

0.70

1.23

150

-')4.

50

115

0.80

0.76

1.1 ~

1.10

0.99

1.07

1.18

0.92

0.99

0.92

1.('2

175

100

0.99

0.94

1.~6

1.37

L22

UJ

1..18

1.15

L23

1.15

2.00

100

225

121

1.13

1.75

1.64

1.-16

159

1.77

1.38

1..19

1.38

1.-11

225

250

l AO

1.33

2.03

1.91

1.7 1

LX6

2.05

1.61

L76

1.6 1

1.83

25 0

275

1.61

1.52

~.Jl

~ .JJ

2.3-1

1.1\5

2.03

1.85

3.2-1

275

300

1.82

1.71

:::: ,61

2AO

1.62

::.Ol!

::.30

2.09

3.67

300

32S

2.o.t

1%

1,90

n2

2A-I

2.Mt

2.91

2.J2

2.59

2,32

4 .09

325

350

2.26

1.10

320

~_99

2.68

2.96

3.19

2.56

2.88

2.56

-152

350

J75

2.411

:Ull

J50

3.~6

2.9 1

3.24

JA8

1.W

3.1X

2.1(0

-1.95

J75

400

1.70

2.50

HO

353

3.25

3.52

3,llg

3.05

JAR

3.05

539

400

3.80 -1.07

1.52

4.17

3.30

3.76

3 .29

5.83

3.79

1.17

1.55

1.01

J.5~

425

1.93

2.72

~.IO

450

3.16

1.93

~AI

4 15

3.39

3.14

~.71

476

3.80

·.1.31

3.78

6.72

3.62

3.35

5.01

'.J.< -1.6 1

HJ6

500

·Ul

H)t>

~ .05

459

4.02

7.17

5:5

3.S6

3.58

5.3 1

4.88

~ .6 1

5.35

~.31

4.87

-1,2 7

7.63

525

""

-1.11

3.80

5.6J

'.64

~_56

5.16

~,j2

~.IO

550

575

4 ..'5

4.02

5.93

5.18

4.83

5.44

4,77

8.56

575

600

'60

-1.14

6.1-1

5.69

5..16

'.09

5.n

5.02

9.0J

600

·U:(,

W

6.55

5.35

625

6J!7

b.Oj

5.62

'"

5.27

4.69

''''

5.75

5. 11

553

650

65'

D-12

5.15

6.23

4.90

630

© E.xpansion Join! Manufaclurers Association, Inc.

425 -ISO

www.~JJna.org

STAN DARDS OF T HE EX PANSION JOINT MA NUFACTURE RS ASSOC IATI O N. INC. A PPENDI X D

TABLE IV (continued) Thermal Expansion of Pipe ill Inch es per 100 Feet r r mp. ~rH'S

.-.

Cul>on ('"-\ 10. JCr -,\ I " $ I(''116

11411

10.25

10042

9,-19

IOA9

9.37

'"

1015

9.17

K30

11.82

10.55

10.75

9_77

10.80

9.66

1025

11,09

10.05

1111

9,94

1050

1075

1000

1050

9.-16

8.55

12. If.

10_115

1075

9.75

!tllU

1250

1115

II

~3

1034

1142

10.23

1100

10.04

9.05

12.R4

1145

11,77

10.6J

11,74

1051

1100

1115

10.)1

9.28

13. III

11.78

12, II

10.92

12.05

10_80

11:!5

1150

10.57

13.52

1211

1247

I 1.2 I

12.3M

1109

1150

I liS

IO,Kl

9.52 9.7{,

13.Rn

12_44

12.111

II.SO

12.69

IU7

1175

1100

11.10

10.00

14.20

12.77

13_15

tum

13.02

11,66

I:!OO

II,)R

10.26

14.5~

IJ.LO

13.50

12,0'/

13.3(,

11_91\

II.M

1053

!-1.88

1]A3

13.116

12.J9

IVI

12..:'9

1250

1275

1250 L!75

11.94

10.79

13_76

14.22

12,69

IHI4

12_ftl

1300

12.22

11.06

15.56

I~.O'/

14.58

12,99

I·U9

12,93

130()

13~5

1250

1130

15.90

HJ9

1~.94

13.29

1~_74

13.25

13~5

1350

12.711

11 55

16.24

1~,69

15.30

13.59

13.511

l_UO

1375

I:Ult>

11 XO

16.511

1-1,99

15_66

11.90

15.10 15_44

13.1I~

1375

1400

13.34

12.05

16.92

15,29

16.02

14.10

IHO

14.20

1400

1-125

Ino

14.51

16_[(.

14_51

1425

I.-50

17.69

1~_82

16.53

14,113

1~50

J·HS

18.0ll

15.IJ

16,~8

15_14

1475

1500

1847

15,44

17.25

15.-15

1500

1525

15.76

17.61

15_r

1525

1550

16,07

17,911

16_08

1550

1575

16.~9

111_35

11>.40

1575

"00

Ib 71

UU)

lri_71

1600

l\OIClo 2_ .,_

Table .h(>\\) o;xpansion !'Clouh,"); from "hanS'- In tempo;r.llure !'rom 70" F 10 indiC3l~d Icmrcrmurc Thl~ ut>le I' lor mformatlon onl~ and II i;;; nol 10 be Implied Ihal m:llen31~ arc sullable for .. lithe temp in thi~ ubI )Y.

Alloy

Alloy

800

82l

31.4 30.8 30.3 29.4 28.8 28.3 27.9 27.3 26.5 25.5 24.2 22.5 20.4 18.0

-

31.2 30.6 30.1 29.2 28.6 28.1 27.7 27.1 26.4 25.3 24.0 22.3 20.2 17.9 15.4

-

-

30.5 29.9 29.3 28.5 27.9 27.5 27.1 26.7 26.2 25.8 25.4 24.9 24.4 23.8 23.2 22.6 21.9

30.0 29.3 28.8 28.0 27.4 27.0 26.6 26.2 25.8 25.4 24.9 24.4 23.9 23.4 22.8 22.2 21.6

---- -- - - -

Aluminum

11.3 11.1 10.9 10.6 10.4 10.2 9.5 8.5 .

-

-

-

-

Alloy

Aust. Stainless Steel

Alloy

Alloy

Alloy

400

200

600

62l

27.8 27.2 26.8 26.0 25.s 25.1 24.7 24.3 23.9 23.6 23.1 22.7 22.2 21.7 21.2 20.6 20.0

30.3 29.7 29.2 28.3 27.5 27.0 26.4 25.9 25.3 24.8 24.1 23.5 22.8 22.0 21.2 20.3 19.2

32.2 31.4 30.9 30.0 29.4 28.9 28.5 28.1 27.6 27.2 26.7 26.2 25.7 25. 1 24.5 23.8 23.1

33.3 32.5 31.9 31.0 30.3 29.9 29.4 29.0 28.6 28.1 27.6 27.1 26.5 25.9 25.3 24.6 23.9

32.2 31.4 30.9 30.0 29.4 28.9 28.5 28.1 27.6 27.2 26.7 26.2 25.7 25.1 24.5 23.8 23.1

-

Notes: Thi s tab le is 1"01' information only. It i ~ nollO be impl ied Iha t materials nrc su itable for alllcmpcrallirc nlllgcs showlI. Data all Al loy 600. 625 ,mel Al loy 800 and 825 arc frolll Special Metals. Inc. Balance of data from AS ME Section VIII - Di y. I, ASME 8 31.1. and ASME OJ 1.3.

o > o V>

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is Z

> ~

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"Z

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Qs:

X> c ." > ~

O Z

C

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V>

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V>

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STANDARDS OF THE EXPANS ION JOINT MANUFACTURERS ASSOCIATION, INC AP PENDIX E

Preparation ofTcchnicallnquirics Introducti on The EJMA Technical Committee wi ll consider written requests for interpretations and revisions of tile EJMA Standards. The Committee's activities in this regard. are limited strictl y to imerprerations of tile Slandards. EJMA does not approve. certify. rate or endorse any item. cons truction. proprietary device or activity. EJMA does not act as a consuhant OLl speci fi c engineering problems or on general application or understanding of the EJMA Standards. Inquiries requiring such considera tion will be retumed . Requirements lnquiries shall be limited strictly to interpretations of the Standards or to the consideration of revisions to the present Standards on the basis of new dam or technology. Inquiries sha ll meet the following requirements: ((I) Scope. Invo lve

a single subjec t or closely related subjects in the scope of the Standard. An inquiry

letter concerning unrelated subjects will be returned.

(b) Background. State the purpose of the inquiry, which may be either to obtain an inrerpretation of the Standard or to propose consideration of a revision to the present Standard. Provide concisely the infomlation needed for the Committee's understanding of the inquiry. being sure to include reference to the applicable Standard Section. Edition. Addenda, paragraphs. figures and tables. If skeCch ed are provided. they shall be limited to the scope of the inqui ry. (c) Inquiry Strucfllre (I) Proposed QlIesfion(s). The inquiry shall be stated in a condensed and precise question

fonnat, omitting superfluous background infomlation and where appropriate. com posed in such a way that "yes" and "no" (perhaps with provisos) would be an acceptable reply. The inquiry statement should be technically and editorially correct (2) Proposed Rep(r(ies). Provide a proposed reply stating what it is believed that the Standard

requires. If in the inquirer's opinion, a re\'ision to the Standards is needed. recommended wording shall be provided in addition to infonnation justifying the change. Submitlal Inquiries should be submitted in rypewr1uen fonn: however. legible handwritten inquiries will be considered. They shall include the name and return address of the inquirer and be emailed.mailed. or faxed (Q the following address: EJMA Technical Inquiry 25 North Broadway Tanytown. NY 1059 I Fax: 914-332-1541 E-mail: [email protected]

\\ \\ w.cJma.org

l

Expansion Joint ManufaclUrers Association. Inc.

E-l

STAN DA RDS OF THE EXPANSIO

JOI NT MA NU FACTURERS ASSOCIAT ION. INC. APPENDIX E

This page intentiona lly blank.

E-:2

\ Expan!>ion Joinl Manufacturers Associalion. Inc.

www.eJma .org

STANDARDS OF THE EXPANS ION JO INT MANUF ACTURERS ASSOCIATION. INC. A PPEN DI X F BELLOWS FATIGUE TEST REQU IR EMENTS F-I INTROD UCTION The Expansi on Joint Manufacturers Assoc iation has adopted the following minimum requirements for bellows fatigue testing. It is the intention lilal the test results will accurately represent perfomlance of typical production bellows. The results may be used to prepare fa tig ue curves for use with be ll ows in tended for service below the active creep temperature range. F-2 TEST SPECIMENS F-2.1 MANUFACTU RI NG

~ I ET H ODS

The bellows used for fatigu e testing shall be representati ve of the bellows manufactured for nomlal production purposes. The same shearing. rube rolling, welding. planishing, convolution fonning. fe-rolling, final sizing. and thennal treatment methods sha ll be empl oyed for the test speci mens. The detailed steps of manufacruring sha ll be recorded for each test spec imen. The finished test specimens shall have the same typical varia tions in dimensions. surface fi ni sh. and condition of cold work as nonna l production bellows. Multi-ply bellows sha ll have provisions for a leak path throu gh the outer plies. 1'-2.2 DIMENSIONAL

~IEASUREMENTS

Test spec imen as-built dimensions shall be measured and recorded. The nomenclature is as follows:

r

I

N

2

i=1

D•.

+

1-1-jL, I I -----

+

N-'

2

/=1

L, - - - - - - - - -

where D Vi = Outside diameter of convolution crest. i (I to N). as detennined by circumferential measurement. D b! = Inside diameter of convo lution roOt. j (I (0 N-I). as determined by circum ferentia l measurement. " I.k = Convolution heigh!. j (I to N-I). al k (1 to 4) locations equally spaced around the circumference I,., Bellows material thickness at the tangent. m (1 to n) Lb = BeI!O\'v's con\'oluted length

L, = Bellows tangell! length N = Number of convolutions in the bellows 1/

\\ \\ \\ .ejma.org

=

Number of bellows material plies

i::

Expansion Joinl Manufacturen; Association. Inc.

F·l

STANDA RDS OF TH E EXPANSION JOINT MA UFACTURERS ASSOC IATION. INC. APPENDIX F

The tolerances fo r measurement accuracy of each di mens ion are as follows:

Do. D b)

wi.! 1m

L, L,

± 0.005 in. ± 0.005 in. ± O.OOS in . ± 0.00 1 in . ± 0.03 1 in. ± 0.063 in .

F-2.3 DIM ENS IONAL R EQU IREM ENTS

Test specimens shall meet the following requ irements : a. Min . cOllvo lution inside d iameter (D,,) =6.63 in . ~ 2D, b. Max. bellO\\ls convo luted length (L II) ~L, / N c. Min . convo lution he ight (1\') ~3 d. Min. number of con volutio ns (N) c. Min. bell ows tangent length (L f )

~

Jr(D=-,""')(I-.c-)/"'2

1'-2.4 BELLOWS MATERIALS

Test specimens sha ll be manufaCll lred frolll typi ca l production quality material. Any specia l treatments o r fini shing of the be ll ows material must be recorded . F-2.5 BELLOWS ATTAC HMENT S

The bellows sha ll be auached to the test apparatus in a manner that duplicates namml production be llows attachments. 1'-2.6 BELLOWS H EAT T REATMENT

Ifheat treatmen t is performed on lest speci men s, the following infomlatioll sha ll be recorded: a. Atmosphere b. Heat ing rate c. Holding temperature d. Holding time c. Coo li ng rale

F-:

If ' .

expansion Jo int ManllflldUlcl!I

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STANDARDS OF T HE EXPANS ION JOINT MANUFACTURERS ASSOCIATION. INC. AP PEND IX F F-3 TEST APPARATUS F-3.1 GENERAL REQ UI RE ~I ENTS

The test apparatus sha ll be construc ted and controlled so (hat the test specimens can be rig idly held in position and cycled repeatedly with the specified movement. Bellows failure shall be defined as a leak through the materia l which causes a reduction of the internal pressure below a se t minimum limit andlor allows for penetrating liquid to bec.omc visible on the outer surface of the bellows. F-3.2 CYCLE COUNTERS

The apparatus shall provide for reliable cycle counters which record the total number of cycles to failure for eac h test bellows. F-3.3 TEST MEOlA

Testing shall be completed using an internal pressurizing media andlor an internal penetrating liquid. A liquid or gas media may be used to pressurize the test specimens internally during the fat igue test. The test media shall not be detrimental to the bellows ma terial. The pressure may be constant or variable during the test. The apparatus sha ll be constructed so that the loss of media through a leak wi ll result in a rapid reduction in pressure. The reduction in pressure below a set minimum limit may be used to iden ti fy the presence of a leak. Controls shall assure that a reduction in pressure below the set minimum limit results in a recording of the total number of movement cycles shown on the bellows cycle counters. The pressure during the movement cycles sha ll be constant but may differ from as low as possible up to the allowable pressure but. shall in no case cause bellows instability or convolution defbnnation during the test. An internal penetrating liquid in contact wi th the inside surfaces of the test specimens may be used during the fatigue test. The liquid shall nO[ be detrimental to the bellows material. When a leak develops during the test, the penetrating liquid shall rapidly become visible on the outer surface of the bellows and the total number of movement cycles shall be recorded. F-3A TRA YEL SPEED

The apparahis shall control the motion to be smooth over the length of trayel. The travel speed shall not exceed 60 in / minute. F-3.S BELLOWS' MOVEMENT

The bellows test specimens shall be cycled with a:'{ial movement only. One cycle is defined as movement through the full movement range (amplitude) and return to the starting position. The bellows movements for the test specimens shall be selected to produce cycles to failure that cover the desired range for the fatigue curve. The movements shall not be excessive and shall not cause detrimental convolution defomlation. The bellows movement range shall be measured and recorded at the beginning and end of the test. The tolerance for the measured movement range is +...- 0.5%).

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Expansion Joilll Manufacturers Association. Inc .

F-3

STANDARDS OF THE EXPANSION JOI NT MANUFACTURERS ASSOC IA TION, INC. AP PENDIX F F-I

FA TI GUE CU RVES F-4. 1 CALCULAT IONS

Total stress range (S, ) calculations for each bellows shall be in accordance with the EJMA performance equations using the measured movement range and the room temperarure Modulus ofElaslicity for the material. The stresses due to tesl media pressure shall not be included in the calcu lation for total stress range. The variables in the performance equations shall be found using the tesl specimen measurements and the fo llowing equat ions: a. Bellows Ou tside Diameter ( D,, ) I ' D,, = N LD",

,-,

b. Bellows Inside Diameter (D/o I

"-I

(N_ I )~D.

D,

c. Convolution Height Less Bellows Material Th ickness ( \I' ) I

'"

'-I

.j

LL wjk 4(N -I) t ~1

fo r D" < 10.75 in.

1"'1

=(D" -D, ) ! 2 d. Bellows Nominal Thickness orOne Ply (I)

fo r D" ~ 10.75 in.

1 '

1= -

n

L 1m

m= 1

e. Convolut ion Pitch (q )

q = L.! N f. Mean Diameter of the Bellows ( Duo )

D", =

D~

+ 1I ' +nt

F-5 TEST DOCUMENT A TI ON

The following documents are required: a. Certified mill test reports for lhe bellows material b. Heat treat charts (where applicab le ) c. Photographs of the test

d. Test log sheets and records e. Final report of the results

F-4

i.C E .... pansion Joint l'vlanuraclurer.> Association. Inc.

www.cjm oft

A-

M

~F,Z-F.

.r

~O

M

~F

X-F,)'

~ (4658)(~.5)-0 ~

11645 fi.lbs.

" Expansion Joint Mnnulacturer.. AssociatIOn. Inc

-

2

STAN DARDS OF THE EXPANSION JOI NT MANUFACTURERS ASSOC IATION, INC. AP PEND IX J Forces and moments acting on directiona l main anchor. OMA, "8" F, =-F, - F"

=-63838 - 1253 = -65091 Ibs. F, = 0 (DMA does nOI support in Y direction) ~

= 0 (no forces exist in Z direction)

At , =F, Y -F,Z

Where

=0

Y=Z = O X -

L~- +.!:..t. - 2.5ft. 2

M , = FZ .• - FX =

=0 M , = F, X - F,Y

=0 Forces and momen ts acti ng on main anchor, MA,

"e"

Fr = F., + Fa = 63838 + 1253 = 65091 Ibs. F, = -4658 Ibs.

F:

=

0 (no forces ex ist in Z direction)

Mr

=

F: )' - F, Z

Where Y =Z= O

X =-( L,

=0

+;

) =- 12.5fl.

=0 M,= F, X - F,. Y

= (-4658)( - 12.5)-0 = 58225 ft. lbs.

J-6

C [xpans.ion Joim Manufacturers A:.so.:ialioll. 1m:.

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Ibs.lin. per convolution

111.

N~12

J- !O

-Ll e xpansion Joilli Manufa':luto:t ::. A::,::,ul:ialiutl. ilJl.:.

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STANDARDS OF T HE EXPANS ION JOINT MANUFACTURERS ASSOCIATION. INC. APPEND IX J SOLUTION: Equivalent axial movement per convolution. Equation (4-2) and (4-6), Section 4.1.

x e =• 2N .248 (2)(12) =.010 in.

(e, ),

K"D",Y,

2N(L" -L" -x/2) (1.285)(25.5)(.788)

NOTE: First subscript applies to direction related to the bellows ax is. second subscript system coordinate axis. Where x = thennal growth occurring between tie rod plates

(2)(12)( 48 -12 - .248/2) -illOi~

-~+~+~

- .079 + .090 + .079

=.248 in.

K"-1.285at ,LL" -2

-,

(e, )

.r , = .788 in.

K"D",y~

2N(L,,-L,-x/2j

Y:

=

1.463 in.

(1.285)(25.50)(1.463) (2)( I e)( 48 -12 - .248/2) = .056 Ill.

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(. Expansion Joint Manufacturers Association. lne.

HI

STANDA RDS OFTHE EXPANS ION JOINT MANUFACTURERS ASSOCIATION, INC. APPEND IX J Calculation for V, . Equation (4-18). Section 4 .6. 1.

r De 2L,

1'- -'" 1 -

WI

NOTE: First subscript refers to bellows Intent l

I'

movement, second subscript to system co-ordinate axis.

(3 6840)(25.50)(.030) (2)( 48) = 294 Ib,.

(36840)(25.50)( .U56) (2)( 48) = 548 Ibs. Forces and moments acting o n intenncdiate anchor lA, "A"

where X = L, + L, / 2 = 5.5 ft.

F, = -(V,) ,

Y = -35 ft .

= -294 Ib,. ~ = 0 (Force due to axial be llows

Z=0

movements. e, is restrained by tie rods)

F,

= (V,),

= 548 Ib,. M , =F,Y-F,Z = (548)( -35) - 0 =-1 91 80 ft.lb,. M, =

f~Z

-F,X

= 0 -(548)(5.5) = -3014 ft. Ibs. M,

=

F,.X -F,Y

=-294(5.5)-0 =-16 17 ft. lb,.

J-12

{' Cxpansion Joint ManUra.. lulcl!l

A:'~l)1.:ialiull.

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STANDARDS OF T HE EXPANS ION JOINT MANUFACTURERS ASSOCIATION. INC. AP PEND IX J Forces and moments acting on intennediate anchor IA. "8"

\\ here X = -( Ll + L" 2) = -5.5 f1.

F = 294 Ibs. F, =0

)' =0

F =548 Ibs .

Z = -65 fl.

.If = F.Y-FZ = 0-294(-65) = 19.110 fI.lbs.

M , =F,Z-F,X

=0-(548)(-5.5) = 30 14 ft. Ibs.

M ,= F,X - F,Y = (294)(-5.5)-0 = -1617

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fl. Ibs.

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E'pansion JOint ManufaclUrer:-. _-\ssocialion. Inc.

J-13

STANDARDS OF THE EXPANSION JO INT MANUFACTU RERS ASSOC IAT ION, INC. A PP END IX J Example 5: Universal press ure balanced Expansion Joint located behl'cen two pi eces of equipment with movement s a l end p Oi nts.

FIGURE J6 A 66 in. diameter turbine exhaust duct system. shown in Figure J6. is fabricated of stee l and operates at full vacuum and 2500 F. Movements at the turbine ex hau st out let fl ange and condenser inlet are determined to be (for the direct ion shown): Axis

y 0. 11 in. 0.18 in

X

0.07 in. 0.26 in . (Directions shown in Figure J6) Thennal growth calcu lations for the 66 in. diameter piping are: Point A

Tl JRRI NE

Po int B

CON Dl:.NSER

L, = 10 ft. L l =6 ft.

I1L, = .084 in.

L. = 5 ft .

M . = .070 in.

L,

6L~ =

=

o in.

0.12 in.

M e =. 140 in.

28 fl.

.392 in.

ilLh =.OI4 in.

L. =lft .

J- 14

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Expansion Joint ManufacILlfers A:.:.o.::iulioll. Inc.

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STANDARDS OF THE EXPANS ION JOINT MANUFACTURERS ASSOCIATION. INC. A PPEN DI X J

L, ~ 3

L5 = 1 F1. 8.6 in.

tt.

6.L_, = .042 in. 6L .~ = .02-t in.

Detennine the forces and moments due to the bellows stiffness at the condenser and turbine connections. Data pro\'ided by the Expansion Joint manufacturer: = 68.00 in. I~ = 35425 Ibs ./in. per convolution

.0", N,

=

Nh

= 6 (N umber of convol ut ions in balancing bellows)

6 (Number ofconvolulioLlS in one flow bellows)

SOLUTION: Ca lcu late the total movement rhe Expansion Joint must absorb. Flow bellows: x=l1L J +Mu +6L-t +&\'j +~rl1 ~

.084+ .070+ .392 + .07 +.26

~

.876 in.

X,· =~

+~y~

+liYB

~

.140+0.12+ 0.18

~

.440 in.

,", = flZ I +ilZg

=0+.12 =.12 in.

x ~ (ill,

Balancing bellows: -ill, )-ill, +&1' < + fiX,

~

.392 - .024 - .042 + .07 + .260

=

.656 in.

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~.

E'pansion Joint Manufacturers Association, Inc.

J-15

STAN DARDS OF T HE EXPA SION JO I T MA ' UFACTURERS ASSOC IATION, I C. AP PE DIX J Calcu late equivalcm movement per convolution.

x e .: --

(Flow Bellows)

?_ 1V {

,

.876 =-(2)(6)

= .073 in.

x

e = , N, =

(Balancing Bellows)

.656

6

=. 109 in . K D ,(e, ), = P I (L "- "L'- ~ / ?) _ 1\ I

"

/ . .\

I,

w here K = 1.22 at _ " = 2.5

"

...

-,

?L

(1.22)(68)(.44) (2)(6)(60 - 12 - .876 / 2)

=. 064 in. KD l'

(e ,. ): =

"

m·

=

2N , (L" - L, - x / 2)

= :-,(.:,:1.:::22::.)(",6"" 8),,,(..:,:12=,)~ =

(2)(6)(60-12-.~76 / 2)

= .017 in .

Calculation of F, _ (V,) , and

( '~ ) , .

Equations (4- 14) and (4-18) Sect ion 4_6.1.

F.f =1.(e +eX,",,/._.,"I( ) . . . . II".. = 35423(.073 + .109) = 6447 Ibs.

J- 16

C" Expansion Joint Manufaclurers Associallon. Inc.

STANDARDS OF THE EXPANS ION JOINT MANUFACTURERS ASSOCIATION. INC. APPE DIX J

1L

"

(3541 5)(68)(.064 ) (2)(60) = 1285 Ibs. ("D.(e ), 2L"

(35415)(68)(.017) (2)(60) =341Ibs. Forces and moments acting on turbine flange "An

F, = -6447 Ibs. F, =(1;), = 12851bs.

F, =-(1';), =-341Ibs. L

where: X =1., + ~' =8.5

M=F)"-FZ \ = ,

=(-341)( - 10)-0

n

Y=L,=-lOft.

Z=O

=3410 ft. Ibs. M, =F,Z-F,X =0-(-341)(8.5) = 1899 ft. Ibs. M =F,X-F,Y

= (1285)(8.5) - (-6447)( -10) = 10923-64470 = -53547 ft. Ibs.

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( Expansion loillll\lanufacturers Association. Inc.

J-17

STANDARDS OF THE EXPANS ION JO INT MANUFACTURERS ASSOCIATIO , INC. APPENDIX J Forces and moments acting on condenser con nection "8"

F, - F,

F, M

~

6447 Ibs.

~ - (V,), ~ - 12 S5Ibs.

~( I~ ) , ~34 1Ibs. ~FY-~- Z

.'

-

~3 41(0)

w here:

I

- (-1285)(0)

x=-(~' +L~ ) =-30.5

ft.

Y~ Z~ O

~O

M,

~ F, Z-F, X ~0-(341)(-30.5) ~

M;

J·I S

10400 ft. Ibs.

~FX-Fl'

,

..

~

(-1285)(-30.5)-0

~

39193 ft. Ibs.

~ E.'pa[):o,ivlI Juiul MaJlufaduIl':rs A!>soci:iiion. inc.

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STANDARDS OF T HE EX PANS ION JOINT MANUFACTURERS ASSOCIATION. INC. AP PEN DI X J

Example 6: Single Expan sion Joint. attached to vesseillozzle, subj ected to axial and lateral movement.

'c'

.-

+My

FIGURE J7

A large vert ical vesscJ which operates at 150 psig at 500 0 F is equipped with a 24 in. diameter outlet line as shown in Figure J7. The outlet line contains a single bellows Expansion Joint which is designed to absorb the thennal growth ofIhe vessel and pipe line. The lengths and calculated Ihemlai growths for the all-carbon steel system are as follows: L,=15f1.

6.L , = .543 in.

L.=6ft.

IlL.

L,,=lfl.

Mn =.036 in. M , -.507 in.

LJ ,-14 ft.

= .217 in.

( Expansion Joint ManufaclUren; Association. Inc.

STANDARDS OFTHE EXPANS ION JOINT MA UFACTURERS ASSOCIATION. INC. APPEND IX J De tennine the forces and moments act ing on the nozzle flange "8"

Data provided by the Expansion Join t manufacturer: D. = 25.50 in. .... , - ·111 . D1 -~? - -'--) f~

:::: 36840 lbs./ill . per convolution

N= 12 SOLUTION : Calcu late the equi va lent movements per convolution:

e.

=-

x

where:

N

= .2 17 + .036+.507

.760 12 = .063 in.

=.760 in.

=

e,

x = t1L~ + M " + L,

3D",.\'

y = IlL, = .543

N(L, -x)

L,. = 12 in.

(3)(25.50)(.543) (12)(12-.76) =.308 in.

J-20

f'"

Expansion Joini

ManUra';luref~ A~~u\':ialiull.

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STANDARDS OF THE EXPANSION JOINT MANU FACTURERS ASSOC IAT ION. INC. APPEND IX J Calculate F.,. F... Fp and " . F" ~ (/. )(e,) ~

(36840)(.063)

:::: 2321 Ibs.

F.

~(A, )(~)

w here:

A, ~;r(D 4 m' ) --

~

(510.7)(150)

~

76605 Ibs.

=510 . 7in.~

Pol :::: 150 psig

A, ~:(D,')

F" ~ (A , )(P, ) ~

(424.6)(150)

~

63690 Ibs.

,

~ .:c(23.25)'

4 = 424.6 in.!

I'

2L" (36840)( 25.50)( .308) (2)(12) ~

~(O.. ) . )-)' 4

L" = [2 in.

12056 Ibs.

Forces and moments acting on vessel anchor "A"

F, ~ F" + F, ~ 2321 + 76605 ~

78926 Ibs.

F

~- I ; ~- 12056Ibs.

F:

= 0 (no forces exist in Z direction)

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Expansion Joint Manuracturers Association. Inc.

J-21

STAN DARD S OF T HE EX PANSI ON JO INT MANU FACT URER S ASSOCIA TION, INC. APP EN DIX J

where: X = ~(L. + L~ 12) = -6.5 ft.

M -' = FY-FZ = , =O ,11 , =F,Z - F, X=O

Y=L, =15 fl.

M , =F,X-FJ

Z=O

= (- 12056)(- 6.5) - (78926)(15) =

-1.1 05. 526 1"1. Ib,.

Forces and mom ents acting on noZzle flange face "Btl

F, = F" + F, -

F"

F, _

= 232 1+ 76605 - 63690

= 15236 Ibs.

F,. = - 12056 Ibs.

F =0

F,

F,

---

M , = F,Y - F,Z= O

-- --Fp

Fp - (Fa • F,l

FIGU RE J8

where: X

=

L" 12 = -0.5 ft.

y=z=o

,11 ,. = F,Z -F,X =0

M , = F, X - F,Y = (- 12056)(-0.5)- 0 =

6028 rt. Ibs.

Forces and m oments acting on ma in an chor "C"

F"

= -I-~, - r~ = =

F,

-232 1- 76605

-78926 Ibs.

= 12056 Ibs.

F =0 Where X = L] + L~ 12 = 14.5 ft.

M , =FY-F,Z=O

: y=Z=O

M , =FZ - FX=O : \

M,

= F, X =

J_'l "

F, Y = (12056)(14.5) - 0

174812 fl. Ibs.

~

Expansion Join. Manufaciurers Associalion. mc.

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STANDARDS OF THE EXPANSION JOINT MANUFACTURERS ASSOCIATION. INC. A PPENDIX J Example 7 : Ca lculation of Angular Rotation in a 3 I-linge Piping System A 24" diameter stai nless steel line runs between intemlcdiatc anchors