ASTM D4161-24 采用柔性弹性密封件的 “玻璃纤维”（玻璃纤维增强热固性树脂）管道接头标准规范

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Designation: D4161 −24
Standard Speciﬁcation for
“Fiberglass” (Glass-Fiber-Reinforced Thermosetting-Resin)
Pipe Joints Using Flexible Elastomeric Seals
1
This standard is issued under the ﬁxed designation D4161; the number immediately following the designation indicates the year of
original adoption or, in the case of revision, the year of last revision. A number in parentheses indicates the year of last reapproval. A
superscript epsilon (´) indicates an editorial change since the last revision or reapproval.
1. Scope*
1.1 This speciﬁcation covers axially 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 156 in. (4000 mm), using
ﬂexible elastomeric seals to obtain soundness. The pipe sys-
tems include pressure (typically up to 250 psi) or nonpressure
systems for water or for chemicals or gases that are not
deleterious to the materials speciﬁed in this speciﬁcation. This
speciﬁcation covers materials, dimensions, test requirements,
and methods of test.
1.2 The values stated in inch-pound units are to be regarded
as the standard. The values given in parentheses are provided
for information purposes only.
NOTE 1—There is a similar but technically different ISO Standard (ISO
8639).
1.3 This standard does not purport to address all of the
safety concerns, if any, associated with its use. It is the
responsibility of the user of this standard to establish appro-
priate safety, health, and environmental practices and deter-
mine the applicability of regulatory limitations prior to use.
1.4 This international standard was developed in accor-
dance with internationally recognized principles on standard-
ization established in the Decision on Principles for the
Development of International Standards, Guides and Recom-
mendations issued by the World Trade Organization Technical
Barriers to Trade (TBT) Committee.
2. Referenced Documents
2.1 ASTM Standards:
2
D883 Terminology Relating to Plastics
D1600 Terminology for Abbreviated Terms Relating to Plas-
tics (Withdrawn 2024)
3
F412 Terminology Relating to Plastic Piping Systems
F477 Speciﬁcation for Elastomeric Seals (Gaskets) for Join-
ing Plastic Pipe
3. Terminology
3.1 Deﬁnitions:
3.1.1 General—Deﬁnitions and abbreviations are in accor-
dance with Terminology D883 or Terminology F412, and
Terminology D1600 unless otherwise indicated.
4. Types of Joints
4.1 This speciﬁcation covers two types of axially unre-
strained joints based on effecting soundness of the joint
through compression of an elastomeric seal or ring:
4.1.1 Bell-and-spigot or coupling joint with the gasket
placed in the bell in circumferential compression. An elasto-
meric gasket joint design featuring a continuous elastomeric
ring gasket placed in an annular space provided in the bell or
socket of the pipe or ﬁtting. The spigot end of the pipe or ﬁtting
is forced into the bell, thereby compressing the gasket radially
to form a positive seal.
4.1.2 Bell-and-spigot or coupling joint with the gasket
placed on the spigot in circumferential tension: A push on joint
design featuring a continuous elastomeric ring gasket placed in
an annular space provided on the spigot end of the pipe or
ﬁtting. The spigot is forced into the bell of the pipe or ﬁtting,
thereby compressing the gasket radially to form a positive seal.
NOTE 2—A coupling joint of these types is a loose double-bell sleeve
used to connect pipes which have spigots at both ends (see Fig. 1). All
references to bells in this speciﬁcation are applicable to the sleeve
coupling as well as to the integral bell of a bell-and-spigot gasket joint.
5. Materials and Manufacture
5.1 The gasket shall be a continuous elastomeric ring of
circular or other geometric cross section and shall meet the
requirements of Speciﬁcation F477, unless otherwise speciﬁed
1
This speciﬁcation is under the jurisdiction of ASTM Committee D20 on
Plastics and is the direct responsibility of Subcommittee D20.23 on Reinforced
Thermosetting Resin Piping Systems and Chemical Equipment.
Current edition approved Aug. 15, 2024. Published August 2024. Originally
approved in 1982. Last previous edition approved in 2019 as D4161 – 14(2019).
DOI: 10.1520/D4161-24.
2
For referenced ASTM standards, visit the ASTM website, www.astm.org, or
contact ASTM Customer Service at www.astm.org/contact. For Annual Book of
ASTM Standards volume information, refer to the standard’s Document Summary
page on the ASTM website.
3
The last approved version of this historical standard is referenced on
www.astm.org.
*A Summary of Changes section appears at the end of this standard
Copyright © ASTM International, 100 Barr Harbor Drive, PO Box C700, West Conshohocken, PA 19428-2959. United States
This international standard was developed in accordance with internationally recognized principles on standardization established in the Decision on Principles for the
Development of International Standards, Guides and Recommendations issued by the World Trade Organization Technical Barriers to Trade (TBT) Committee.
1

in this speciﬁcation. When a splice is used in the manufacture

of the gasket, no more than two splices shall be made in any

one gasket.

5.1.1 The chemical composition of the gasket shall be

compatible with the type of environment to which it will be

subjected. Selection of the gasket composition shall be in

accordance with a purchaser and seller agreement.

NOTE 3—Consult the gasket manufacturer for advice as to the suitabil-

ity of speciﬁc rubber compounds for the intended service and joint

conﬁgurations. Items such as cold set when the joint is deﬂected under

low-temperature conditions and maximum and minimum stretch in the

gasket may be dependent upon the speciﬁc chemical compounds used.

5.2 Materials in the bell and spigot of the joint shall meet

the requirements of the applicable ASTM speciﬁcation for the

pipe or ﬁtting of which the joint is a part.

6. Requirements

6.1 Joint Surfaces—All surfaces of the joint upon or against

which it is possible that the gasket will bear shall be smooth

and free of cracks, fractures, or other imperfections that would

adversely affect the performance of the joint.

6.2 Joint Geometry—The design of the joint shall include a

means to retain the gasket and prevent it from being uninten-

tionally displaced, either during assembly of the joint or during

operation of the completed pipe system.

6.3 Dimensions and Tolerances—The provisions of 6.3.1.1

apply only to a joining system utilizing a gasket of circular

cross section retained in a rectangular groove. It is acceptable

for manufacturers to submit to the purchaser detailed designs

for joints utilizing gaskets or grooves, or both, of other

geometric shape or for joints not meeting the criteria of 6.3.1.

Joints not meeting the requirements of this section shall meet

the test requirements of Section 7; such joints shall be

acceptable, provided the design is approved by the purchaser

prior to manufacture and provided the test pipe complies with

the speciﬁed test requirements. Test results are applicable to

other diameters with the same joint conﬁguration, gasket shape

and gasket composition provided substantially similar gasket

compressions and gasket hardness are maintained. Increased or

decreased gasket dimensions are permitted provided joint

geometry is also appropriately proportioned so that critical

relationships like gasket conﬁnement are equal or superior to

the tested joint. Design submissions shall include joint

geometry, tolerances, gasket characteristics, proposed plant

tests, and such other information as required by the purchaser

to evaluate the joint design for ﬁeld performance.

6.3.1 Joints Using Circular Gasket Cross Sections:

6.3.1.1 The volume of the annular space provided for the

gasket, with the engaged joint at normal joint closure in

concentric position, and neglecting ellipticity of the bell and

spigot, shall not be less than the design volume of the gasket

furnished. For a rectangular gasket groove, the cross-sectional

area of annular space shall be calculated for minimum bell

inside diameter, maximum spigot outside diameter, minimum

width of groove at surface of spigot, and minimum depth of

groove. The volume of the annular space shall be calculated at

the centerline of the groove and considering the centroid of the

cross-sectional area to be at the midpoint between the surface

of the groove on which the gasket is seated and the surface of

the bell, if the groove is on the spigot, or the surface of the

spigot, if the groove is in the bell.

6.3.1.2 When the design volume of the gasket is less than

75 % of the volume of the annular space in which the gasket is

conﬁned, the dimensions and tolerances of the gasket, bell, and

spigot shall be such that, when the outer surface of the spigot

and the inner surface of the bell come into contact at some

point in their periphery, the deformation in the gasket shall not

exceed 40 % at the point of contact nor be less than 15 % at any

point. If the design volume of the gasket is 75 % or more of the

volume of the annular space, the deformation of the gasket, as

prescribed above, shall not exceed 50 % nor be less than 15 %.

The cross-sectional area of annular space shall be calculated

for average bell diameter, average spigot diameter, average

width of groove at surface of spigot, and average depth of

groove. The volume of the annular space shall be calculated at

the centerline of the groove and considering the centroid of the

cross-sectional area to be at the midpoint between the surface

of the groove on which the gasket is seated and the surface of

the bell, if the groove is on the spigot, or the surface of the

spigot, if the groove is in the bell.

NOTE 4—It is recognized that a relationship exists between the

water-tightness of a joint, the gasket deformation, and the ratio of gasket

volume to space volume. For high-pressure applications, it may be

necessary to provide a very high-volume ratio to obtain a sound joint.

Some manufacturers also have developed satisfactory joints with very

little gasket deformation, but meet the requirements of Section 6by

utilizing a very high-volume ratio.

6.3.1.3 When determining the maximum percent deforma-

tion of the gasket, the minimum depth of groove and the

stretched gasket diameter shall be used and calculations made

at the centerline of the groove. When determining the mini-

mum percent deformation of the gasket, the maximum bell

diameter, the minimum spigot diameter, the maximum depth of

groove, and the stretched gasket diameter shall be used and

calculations made at the centerline of the groove. For gasket

deformation calculations, if the gasket is placed on the spigot

in circumferential tension, the stretched gasket diameter shall

be determined as being the design diameter of the gasket

divided by the square root of (1 + x) where xequals the design

FIG. 1 Typical Coupling Joint Detail

D4161 − 24

percent of gasket stretch divided by 100. If the gasket is placed
in the bell in circumferential compression, the design diameter
of the gasket shall be used.
6.3.1.4 The taper on all sealing surfaces of the bell and
spigot on which the elastomeric gasket contacts after closure of
the joint and at any degree of partial closure, except within the
gasket groove, shall form an angle of not more than 2° with the
longitudinal axis of the pipe. If the joint design does not
incorporate a mechanical locking feature, the joint shall be
designed and manufactured in such a way that at the position
of normal joint closure, the parallel surfaces upon which the
gasket contacts after 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:
(1) In a joint in which the gasket is placed in the bell in
circumferential compression, the circumferential length of the
gasket shall be such that, when inserted into the gasket groove,
the amount of circumferential compression will be less than
4 %. If needed, it is acceptable to use an adhesive to hold the
gasket in place prior to installation.
(2) In an elastomeric joint in which the gasket is placed on
the spigot in circumferential tension, the circumferential length
of the gasket shall be such that, when installed in the gasket
groove, the amount of stretch shall not exceed 30 %.
(3) Compute the amount of compression or stretch by
comparing the circumferential length of the centroid of the
relaxed gasket with the circumferential length of the centroid
of the compressed or stretched gasket after installation in the
bell or on the spigot.
(4) Each gasket shall be manufactured to provide the
volume of elastomer required by the pipe manufacturer’s joint
design, with a tolerance of 61 % for gaskets of 1.0-in.
(25-mm) diameter and larger. The allowable percentage toler-
ance shall vary linearly between 63 % and 61 % for gasket
diameters between 0.5 and 1.0 in. (13 and 25 mm).
6.3.2 The tolerances permitted in the construction of the
joint shall be those stated in the pipe manufacturer’s design as
approved.
6.3.3 Drawings—The manufacturer shall furnish drawings
of the joint and gasket, including dimensions and tolerances, if
requested by the purchaser.
7. Laboratory Performance Requirements
7.1 General:
7.1.1 The gasket shall be the sole element depended upon to
make the joint leakproof. The assembled joints shall pass the
performance tests listed in this section. The tests shall be
performed with components selected to provide minimum
compression in the gasket. The internal hydrostatic pressures
required in 7.2 and 7.3 shall be two times the rated pressure, if
the pipe is manufactured for pressure service, or 29 psi
(200 kPa), if the pipe is manufactured for nonpressure service.
7.1.2 Laboratory hydrostatic pressure tests on joints shall be
made on an assembly of two sections of pipe properly
connected in accordance with the joint design. Use suitable
bulkheads within the pipe adjacent to and on either side of the
joint, or bulkhead the outer ends of the two jointed pipe
sections. If necessary, provide restraints at the joint to resist
transverse thrust. No coatings, ﬁllings, or packings shall be
placed prior to the hydrostatic tests.
7.2 Pipes in Angularly Deﬂected Position—Using a pipe
and joint system as described in 7.1.2, the test sections shall be
deﬂected angularly, as shown in Fig. 2, and subjected to the
appropriate internal hydrostatic test pressure for 10 min with-
out leakage. The angle deﬁned by the joint openings given in
Fig. 2 is the angle between the axis of the two joined pipes.
7.2.1 Joints intended for use at pressures greater than
250 psi are permitted to have lower allowable angular deﬂec-
tions than those given in Fig. 2 by manufacturer purchaser
agreement. The joints shall be tested at the manufacturers
maximum allowed angular deﬂection.
7.2.2 Determine the joint opening by scribing a circumfer-
ential index mark on the outside of the pipe a sufficient distance
from the spigot end to be visible when the pipe is joined.
Measure the maximum and minimum distance from the end of
the bell to the mark. The difference equals the joint opening.
Fig. 2 illustrates a typical joint in closed and deﬂected positions
and the index mark.
NOTE 5—This test is a laboratory performance test of joint integrity and
is not indicative of allowable angular deﬂections in ﬁeld installations. In
actual installations, deﬂections greater than the manufacturer’s recom-
mended maximum should be avoided, and elbows, bends, or special
ﬁttings 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 test
sections shall be deﬂected while the pipe units are in a
horizontal position, as shown in Fig. 3, by applying a perpen-
dicular load. The load shall be 100 lb ⁄in. (17.5 kN ⁄m) in
diameter. The load shall be uniformly applied over an arc of not
more than 120° along a longitudinal distance equal to one pipe
diameter or 12 in. (300 mm), whichever is the smaller, at the
unsupported spigot end of the pipe immediately adjacent to the
bell of the assembled joint. The pipe in the test shall be
supported on adequate blocks placed immediately behind or on
the bells, as indicated in Fig. 3. If necessary, use bands to
Pipe Size Joint Angle
#20 in. 3°
>20 in. #33 in. 2°
>33 in. #60 in. 1°
> 60 in.
1
⁄
2
°
NOTE 1—Joint opening shall not exceed the maximum unstressed limit
permitted by dimensional clearance between spigot and bell.
FIG. 2 Typical Bell-and-Spigot Gasket Joint Detail
D4161 − 24
3

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标签： #接头 #管 #增强

摘要：

ASTM D4161-24 是一项专门针对采用柔性弹性密封件的“玻璃纤维”（玻璃纤维增强热固性树脂）管道接头的标准规范，旨在为这种广泛应用于市政排水、工业输水及腐蚀性介质输送领域的复合材料管道系统提供统一的接头设计与性能测试要求。该标准由美国材料与试验协会（ASTM）发布，2024年版本更新了密封件的材料特性、安装间隙、压力测试及泄漏率限制等关键参数，确保接头在承受内外压力、温度变化及地面沉降等动态载荷时仍能保持可靠密封。通过遵循该规范，工程方可在选用玻璃钢管道及弹性密封接头时获得一致性、耐久性

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ASTM D4161-24 采用柔性弹性密封件的 “玻璃纤维”（玻璃纤维增强热固性树脂）管道接头标准规范

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