ASTM D4161-2001(2010) Standard Specification for Fiberglass (Glass-Fiber-Reinforced Thermosetting-Resin) Pipe Joints Using Flexible Elastomeric Seals《使用挠性弹性体密封件的玻璃钢(玻璃 - 纤维 - 增强热.pdf

《ASTM D4161-2001(2010) Standard Specification for Fiberglass (Glass-Fiber-Reinforced Thermosetting-Resin) Pipe Joints Using Flexible Elastomeric Seals《使用挠性弹性体密封件的玻璃钢(玻璃 - 纤维 - 增强热.pdf》由会员分享，可在线阅读，更多相关《ASTM D4161-2001(2010) Standard Specification for Fiberglass (Glass-Fiber-Reinforced Thermosetting-Resin) Pipe Joints Using Flexible Elastomeric Seals《使用挠性弹性体密封件的玻璃钢(玻璃 - 纤维 - 增强热.pdf（4页珍藏版）》请在麦多课文档分享上搜索。

1、Designation: D4161 01 (Reapproved 2010)An American National StandardStandard Specification for“Fiberglass” (Glass-Fiber-Reinforced Thermosetting-Resin)Pipe Joints Using Flexible Elastomeric Seals1, 2This standard is issued under the fixed designation D4161; the number immediately following the desig

2、nation indicates the year oforiginal adoption or, in the case of revision, the year of last revision. A number in parentheses indicates the year of last reapproval. Asuperscript epsilon () indicates an editorial change since the last revision or reapproval.1. Scope*1.1 This specification covers axia

3、lly unrestrained bell-and-spigot gasket joints including couplings required for machine-made “fiberglass” (glass-fiber-reinforced thermosetting-resin)pipe systems, 8 in. (200 mm) through 144 in. (3700 mm), usingflexible elastomeric seals to obtain soundness. The pipe sys-tems may be pressure (typica

4、lly up to 250 psi) or nonpressuresystems for water or for chemicals or gases that are notdeleterious to the materials specified in this specification. Thisspecification covers materials, dimensions, test requirements,and methods of test.1.2 The values stated in inch-pound units are to be regardedas

5、the standard. The values given in parentheses are providedfor information purposes only.NOTE 1There is a similar but technically different ISO Standard (ISO8639).1.3 This standard does not purport to address all of thesafety concerns, if any, associated with its use. It is theresponsibility of the u

6、ser of this standard to establish appro-priate safety and health practices and determine the applica-bility of regulatory limitations prior to use.2. Referenced Documents2.1 ASTM Standards:3D883 Terminology Relating to PlasticsD1600 Terminology for Abbreviated Terms Relating toPlasticsF412 Terminolo

7、gy Relating to Plastic Piping SystemsF477 Specification for Elastomeric Seals (Gaskets) for Join-ing Plastic Pipe3. Terminology3.1 Definitions:3.1.1 GeneralDefinitions and abbreviations are in accor-dance with Terminology D883 or Terminology F412, andTerminology D1600 unless otherwise indicated.4. T

8、ypes of Joints4.1 This specification covers two types of axially unre-strained joints based on effecting soundness of the jointthrough compression of an elastomeric seal or ring:4.1.1 Bell-and-spigot or coupling joint with the gasketplaced in the bell in circumferential compression. An elasto-meric

9、gasket joint design featuring a continuous elastomericring gasket placed in an annular space provided in the bell orsocket of the pipe or fitting. The spigot end of the pipe or fittingis forced into the bell, thereby compressing the gasket radiallyto form a positive seal.4.1.2 Bell-and-spigot or cou

10、pling joint with the gasketplaced on the spigot in circumferential tension:Apush on jointdesign featuring a continuous elastomeric ring gasket placed inan annular space provided on the spigot end of the pipe orfitting. The spigot is forced into the bell of the pipe or fitting,thereby compressing the

11、 gasket radially to form a positive seal.NOTE 2A coupling joint of these types is a loose double-bell sleeveused to connect pipes which have spigots at both ends (see Fig. 1). Allreferences to bells in this specification are applicable to the sleevecoupling as well as to the integral bell of a bell-

12、and-spigot gasket joint.5. Materials and Manufacture5.1 The gasket shall be a continuous elastomeric ring ofcircular or other geometric cross section and shall meet therequirements of Specification F477, unless otherwise specifiedin this specification. When a splice is used in the manufactureof the

13、gasket, no more than two splices shall be made in anyone gasket.5.1.1 The chemical composition of the gasket shall becompatible with the type of environment to which it will besubjected. Selection of the gasket composition shall be inaccordance with a purchaser and seller agreement.NOTE 3Consult the

14、 gasket manufacturer for advice as to the suitabil-ity of specific rubber compounds for the intended service and joint1This specification is under the jurisdiction of ASTM Committee D20 onPlastics and is the direct responsibility of Subcommittee D20.23 on ReinforcedPlastic Piping Systems and Chemica

15、l Equipment.Current edition approved Sept. 1, 2010. Published October 2010. Originallyapproved in 1982. Last previous edition approved in 2005 as D4161 01(2005).DOI: 10.1520/D4161-01R10.2An ISO equivalency statement was added.3For referenced ASTM standards, visit the ASTM website, www.astm.org, orco

16、ntact ASTM Customer Service at serviceastm.org. For Annual Book of ASTMStandards volume information, refer to the standards Document Summary page onthe ASTM website.1*A Summary of Changes section appears at the end of this standard.Copyright ASTM International, 100 Barr Harbor Drive, PO Box C700, We

17、st Conshohocken, PA 19428-2959, United States.configurations. Items such as cold set when the joint is deflected underlow-temperature conditions and maximum and minimum stretch in thegasket may be dependent upon the specific chemical compounds used.5.2 Materials in the bell and spigot of the joint s

18、hall meetthe requirements of the applicable ASTM specification for thepipe or fitting of which the joint is a part.6. Requirements Requirements6.1 Joint SurfacesAll surfaces of the joint upon or againstwhich the gasket may bear shall be smooth and free of cracks,fractures, or other imperfections tha

19、t would adversely affect theperformance of the joint.6.2 Joint GeometryThe design of the joint shall include ameans to retain the gasket and prevent it from being uninten-tionally displaced, either during assembly of the joint or duringoperation of the completed pipe system.6.3 Dimensions and Tolera

20、ncesThe provisions of 6.3.1.1apply only to a joining system utilizing a gasket of circularcross section retained in a rectangular groove. Manufacturersmay submit to the purchaser detailed designs for joints utilizinggaskets or grooves, or both, of other geometric shape or forjoints not meeting the c

21、riteria of 6.3.1. Joints not meeting therequirements of this section shall meet the test requirements ofSection 7; such joints shall be acceptable, provided the designis approved by the purchaser prior to manufacture and providedthe test pipe complies with the specified test requirements. Testresult

22、s may be extended to other diameters with the same jointconfiguration, gasket shape and gasket composition providedsubstantially similar gasket compressions and gasket hardnessare maintained. Gasket dimensions may be increased or de-creased provided joint geometry is also appropriately propor-tioned

23、 so that critical relationships like gasket confinement areequal or superior to the tested joint. Design submissions shallinclude joint geometry, tolerances, gasket characteristics, pro-posed plant tests, and such other information as required by thepurchaser to evaluate the joint design for field p

24、erformance.6.3.1 Joints Using Circular Gasket Cross Sections:6.3.1.1 The volume of the annular space provided for thegasket, with the engaged joint at normal joint closure inconcentric position, and neglecting ellipticity of the bell andspigot, shall not be less than the design volume of the gasketf

25、urnished. For a rectangular gasket groove, the cross-sectionalarea of annular space shall be calculated for minimum bellinside diameter, maximum spigot outside diameter, minimumwidth of groove at surface of spigot, and minimum depth ofgroove. The volume of the annular space shall be calculated atthe

26、 centerline of the groove and considering the centroid of thecross-sectional area to be at the midpoint between the surfaceof the groove on which the gasket is seated and the surface ofthe bell, if the groove is on the spigot, or the surface of thespigot, if the groove is in the bell.6.3.1.2 When th

27、e design volume of the gasket is less than75 % of the volume of the annular space in which the gasket isconfined, the dimensions and tolerances of the gasket, bell, andspigot shall be such that, when the outer surface of the spigotand the inner surface of the bell come into contact at somepoint in t

28、heir periphery, the deformation in the gasket shall notexceed 40 % at the point of contact nor be less than 15 % at anypoint. If the design volume of the gasket is 75 % or more of thevolume of the annular space, the deformation of the gasket, asprescribed above, shall not exceed 50 % nor be less tha

29、n 15 %.The cross-sectional area of annular space shall be calculatedfor average bell diameter, average spigot diameter, averagewidth of groove at surface of spigot, and average depth ofgroove. The volume of the annular space shall be calculated atthe centerline of the groove and considering the cent

30、roid of thecross-sectional area to be at the midpoint between the surfaceof the groove on which the gasket is seated and the surface ofthe bell, if the groove is on the spigot, or the surface of thespigot, if the groove is in the bell.NOTE 4It is recognized that a relationship exists between the wat

31、er-tightness of a joint, the gasket deformation, and the ratio of gasket volumeto space volume. For high-pressure applications, it may be necessary toprovide a very high-volume ratio to obtain a sound joint. Some manufac-turers also have developed satisfactory joints with very little gasketdeformati

32、on, but meet the requirements of Section 6 by utilizing a veryhigh-volume ratio.6.3.1.3 When determining the maximum percent deforma-tion of the gasket, the minimum depth of groove and thestretched gasket diameter shall be used and calculations madeat the centerline of the groove. When determining t

33、he mini-mum percent deformation of the gasket, the maximum belldiameter, the minimum spigot diameter, the maximum depth ofgroove, and the stretched gasket diameter shall be used andcalculations made at the centerline of the groove. For gasketdeformation calculations, if the gasket is placed on the s

34、pigotin circumferential tension, the stretched gasket diameter shallbe determined as being the design diameter of the gasketdivided by the square root of (1 + x) where x equals the designpercent of gasket stretch divided by 100. If the gasket is placedin the bell in circumferential compression, the

35、design diameterof the gasket shall be used.6.3.1.4 The taper on all sealing surfaces of the bell andspigot on which the elastomeric gasket may bear after closureof the joint and at any degree of partial closure, except withinthe gasket groove, shall form an angle of not more than 2 withthe longitudi

36、nal axis of the pipe. If the joint design does notincorporate a mechanical locking feature, the joint shall bedesigned and manufactured in such a way that at the positionFIG. 1 Typical Coupling Joint DetailD4161 01 (2010)2of normal joint closure, the parallel surfaces upon which thegasket may bear a

37、fter closure will extend not less than 0.75 in.(20 mm) away from the edges of the gasket groove.6.3.1.5 Circular Gaskets:6.3.1.5.1 In a joint in which the gasket is placed in the bellin circumferential compression, the circumferential length ofthe gasket shall be such that, when inserted into the ga

38、sketgroove, the amount of circumferential compression will be lessthan 4 %. In larger pipe diameters, an adhesive may be requiredto hold the gasket in place prior to installation.6.3.1.5.2 In an elastomeric joint in which the gasket isplaced on the spigot in circumferential tension, the circumfer-en

39、tial length of the gasket shall be such that, when installed inthe gasket groove, the amount of stretch shall not exceed 30 %.6.3.1.5.3 Compute the amount of compression or stretch bycomparing the circumferential length of the centroid of therelaxed gasket with the circumferential length of the cent

40、roidof the compressed or stretched gasket after installation in thebell or on the spigot.6.3.1.5.4 Each gasket shall be manufactured to provide thevolume of elastomer required by the pipe manufacturers jointdesign, with a tolerance of 61 % for gaskets of 1.0-in.(25-mm) diameter and larger. The allow

41、able percentage toler-ance shall vary linearly between 63 % and 61 % for gasketdiameters between 0.5 and 1.0 in. (13 and 25 mm).6.3.2 The tolerances permitted in the construction of thejoint shall be those stated in the pipe manufacturers design asapproved.6.3.3 DrawingsThe manufacturer shall furnis

42、h drawingsof the joint and gasket, including dimensions and tolerances, ifrequested by the purchaser.7. Laboratory Performance Requirements7.1 General:7.1.1 The gasket shall be the sole element depended upon tomake the joint leakproof. The assembled joints shall pass theperformance tests listed in t

43、his section. The tests shall beperformed with components selected to provide minimumcompression in the gasket. The internal hydrostatic pressuresrequired in 7.2 and 7.3 shall be two times the rated pressure, ifthe pipe is manufactured for pressure service, or 29 psi (200kPa), if the pipe is manufact

44、ured for nonpressure service.7.1.2 Laboratory hydrostatic pressure tests on joints shall bemade on an assembly of two sections of pipe properlyconnected in accordance with the joint design. Suitable bulk-heads may be provided within the pipe adjacent to and oneither side of the joint, or the outer e

45、nds of the two jointed pipesections may be bulkheaded. Restraints may be provided at thejoint to resist transverse thrust. No coatings, fillings, orpackings shall be placed prior to the hydrostatic tests.7.2 Pipes in Angularly Deflected PositionUsing a pipeand joint system as described in 7.1.2, the

46、 test sections shall bedeflected angularly, as shown in Fig. 2, and subjected to theappropriate internal hydrostatic test pressure for 10 min with-out leakage. The angle defined by the joint openings given inFig. 2 is the angle between the axis of the two joined pipes.7.2.1 Joints intended for use o

47、f pressures greater than 250psi may have lower allowable angular deflections than thosegiven in Fig. 2 by manufacturer purchaser agreement. Thejoints shall be tested at the manufacturers maximum allowedangular deflection.7.2.2 Determine the joint opening by scribing a circumfer-ential index mark on

48、the outside of the pipe a sufficient distancefrom the spigot end to be visible when the pipe is joined.Measure the maximum and minimum distance from the end ofthe bell to the mark. The difference equals the joint opening.Fig. 2 illustrates a typical joint in closed and deflected positionsand the ind

49、ex mark.NOTE 5This test is a laboratory performance test of joint integrity andis not indicative of allowable angular deflections in field installations. Inactual installations, deflections greater than the manufacturers recom-mended maximum should be avoided, and elbows, bends, or specialfittings should be used in such cases.7.3 Pipes in Laterally Offset Position (Shear Loading)Using a pipe and joint system as described in 7.1.2, the testsections shall be deflected while the pipe units are in ahorizontal position, as shown in Fig. 3, by applying a perpen-dicular loa