U.S. patent application number 12/724924 was filed with the patent office on 2010-09-23 for pipe connection having staggered bolt configuration.
Invention is credited to Erik M. Howard, Rajeev Madazhy.
Application Number | 20100237613 12/724924 |
Document ID | / |
Family ID | 42736854 |
Filed Date | 2010-09-23 |
United States Patent
Application |
20100237613 |
Kind Code |
A1 |
Howard; Erik M. ; et
al. |
September 23, 2010 |
Pipe Connection Having Staggered Bolt Configuration
Abstract
A pipe connection having flange members which are configured so
that the bolts which secure the two flanges of the connection
together are staggered axially. One embodiment comprises a first
flange member, a second flange member and a set of bolts and
corresponding nuts. Each flange member has bolt holes sized to
accommodate the bolts. The bolts are positioned in the bolt holes,
and the nuts are tightened onto the bolts to secure the first
flange member to the second flange member. Each of the bolt holes
has a corresponding bolt seat against which one of the bolts' heads
or nuts is seated, and the bolt seats of adjacent bolt holes are
staggered axially (i.e., in the direction of an axis of symmetry
through the flange members) so that each bolt's corresponding nut
can be tightened without interference from the adjacent bolts or
the corresponding nuts.
Inventors: |
Howard; Erik M.; (Baytown,
TX) ; Madazhy; Rajeev; (Baytown, TX) |
Correspondence
Address: |
LAW OFFICES OF MARK L. BERRIER
3811 BEE CAVES ROAD, SUITE 204
AUSTIN
TX
78746
US
|
Family ID: |
42736854 |
Appl. No.: |
12/724924 |
Filed: |
March 16, 2010 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
61161302 |
Mar 18, 2009 |
|
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|
Current U.S.
Class: |
285/405 ; 285/24;
285/412 |
Current CPC
Class: |
F16L 23/0283 20130101;
F16L 23/032 20130101 |
Class at
Publication: |
285/405 ;
285/412; 285/24 |
International
Class: |
F16L 23/032 20060101
F16L023/032; F16L 55/00 20060101 F16L055/00 |
Claims
1. A pipe connection comprising: a first flange member; a second
flange member; and a plurality of bolts, wherein each bolt has a
corresponding nut threaded thereon; wherein each of the first and
second flange members has a plurality of bolt holes therethrough,
wherein each bolt hole is sized to accommodate one of the bolts
therethrough; and wherein each of the bolt holes has a
corresponding bolt seat, wherein in each flange member the bolt
seats of adjacent bolt holes are staggered in the direction of an
axis of symmetry through the flange members; wherein each of the
plurality of bolts is positioned through one of the bolt holes in
each of the first and second flange members, securing the first
flange member to the second flange member.
2. The pipe connection of claim 1, wherein the bolt seats of
adjacent bolt holes are axially displaced by a distance at least as
great as the thickness of one of the nuts.
3. The pipe connection of claim 1, wherein adjacent ones of the
bolts are oriented in opposite directions.
4. The pipe connection of claim 1, wherein for each flange member,
the bolt seats of a first half of the bolt holes lie on a first
plane and the bolt seats of a second half of the bolt holes lie on
a second plane which is displaced from the first plane in the
direction of the axis.
5. The pipe connection of claim 4, wherein the first and second
planes are orthogonal to the axis.
6. The pipe connection of claim 1, wherein at least one of the
flange members comprises a swiveling flange member.
7. The pipe connection of claim 6, wherein the swiveling flange
member comprises an inner portion and a collar, wherein the inner
portion includes a sealing face and a rear-facing shoulder, wherein
the collar includes the outer flange portion and a forward-facing
shoulder, wherein the collar is positioned around the inner portion
with the forward-facing shoulder of the collar contacting the
rear-facing shoulder of the inner portion.
8. A first flange member configured to be bolted to a second flange
member to form a pipe connection, the first flange member
comprising: an outer flange portion which is substantially
symmetric about an axis, the outer flange portion having a
plurality of bolt holes therethrough; wherein each bolt hole has a
corresponding bolt seat at an opening of the bolt hole, and wherein
the bolt seats are staggered in the direction of the axis.
9. The flange member of claim 8, wherein the bolt seats of adjacent
bolt holes are axially displaced by a distance at least as great as
the thickness of a nut.
10. The flange member of claim 8, wherein the bolt seats of a first
half of the bolt holes lie on a first plane and the bolt seats of a
second half of the bolt holes lie on a second plane which is
axially displaced from the first plane.
11. The flange member of claim 8, wherein the first and second
planes are orthogonal to the axis.
12. The flange member of claim 8, wherein the first flange member
comprises a swiveling flange member.
13. The flange member of claim 8, wherein the swiveling flange
member comprises an inner portion and a collar, wherein the inner
portion includes a sealing face and a rear-facing shoulder, wherein
the collar includes the outer flange portion and a forward-facing
shoulder, wherein the collar is positioned around the inner portion
with the forward-facing shoulder of the collar contacting the
rear-facing shoulder of the inner portion.
14. A pipe section configured to be coupled to another pipe
section, wherein the pipe section comprises: a tubular section of
pipe; and a flange member connected to an end of the pipe, wherein
the flange member includes an outer flange portion having a
plurality of bolt holes therethrough, wherein each bolt hole has a
corresponding bolt seat at an opening of the bolt hole, and wherein
the bolt seats are staggered in the direction of an axis of
symmetry that extends through the section of pipe and the flange
member.
15. The pipe section of claim 8, wherein the bolt seats of adjacent
bolt holes are axially displaced by a distance at least as great as
the thickness of a nut.
16. The pipe section of claim 8, wherein the bolt seats of a first
half of the bolt holes lie on a first plane and the bolt seats of a
second half of the bolt holes lie on a second plane which is
axially displaced from the first plane.
17. The pipe section of claim 16, wherein the first and second
planes are orthogonal to the axis.
18. The pipe section of claim 8, wherein the first flange member
comprises a swiveling flange member.
19. The pipe section of claim 18, wherein the swiveling flange
member comprises an inner portion and a collar, wherein the inner
portion includes a sealing face and a rear-facing shoulder, wherein
the collar includes the outer flange portion and a forward-facing
shoulder, wherein the collar is positioned around the inner portion
with the forward-facing shoulder of the collar contacting the
rear-facing shoulder of the inner portion.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application claims the benefit of U.S. Provisional
Patent Application 61/161,302, filed Mar. 18, 2009, which is
incorporated by reference as if set forth herein in its
entirety.
SUMMARY
[0002] This disclosure is directed to an improved design for a pipe
connection that can reduce the size and weight of large,
high-pressure pipe connections, thereby making the connections
smaller, lighter, less expensive, and easier to manufacture,
transport, install and assemble. The pipe connection incorporates
one or more flange members that are configured so that the bolts
which secure the two flanges of the connection together are
staggered axially.
[0003] One embodiment comprises a pipe connection having a first
flange member, a second flange member and a set of bolts and
corresponding nuts. Each of the flange members has a plurality of
bolt holes, each of which is sized to accommodate one of the bolts.
The bolts are positioned in the bolt holes, and the nuts are
tightened onto the bolts to secure the first flange member to the
second flange member. Each of the bolt holes has a corresponding
bolt seat against which one of the bolts' heads or nuts is seated,
and the bolt seats of adjacent bolt holes are staggered axially
(i.e., in the direction of an axis of symmetry through the flange
members) so that each bolt's corresponding nut can be tightened
without interference from the adjacent bolts or the corresponding
nuts.
[0004] In one embodiment, the bolt seats of adjacent bolt holes are
axially displaced by at least the thickness of one of the nuts.
Adjacent ones of the bolts may be oriented in opposite directions.
In one embodiment, the bolt seats of a first half of the bolt holes
lie on a first plane and the bolt seats of a second half of the
bolt holes lie on a second plane which is displaced from the first
plane in the direction of the axis. The first and second planes are
orthogonal to the axis of the flange members. The flange members
may be swiveling flange members which include, for example, an
inner portion and a collar. The inner portion has a sealing face
and a rear-facing shoulder, and the collar has an outer flange
portion and a forward-facing shoulder. The collar is positioned
around the inner portion with the forward-facing shoulder of the
collar contacting the rear-facing shoulder of the inner portion,
and the outer flange portion of the collar is bolted to the
opposing flange member to secure the connection.
[0005] An alternative embodiment comprises a flange member
configured to be bolted to another flange member to form a pipe
connection. The flange member has an outer flange portion which is
substantially symmetric about an axis of the flange member and has
a plurality of bolt holes through it. Each bolt hole has a
corresponding bolt seat, and wherein the bolt seats are staggered
in the direction of the axis.
[0006] Another alternative embodiment comprises a pipe section that
is configured to be coupled to another pipe section. The pipe
section includes a tubular section of pipe and a flange member
connected to the end of the pipe. The flange member has an outer
flange portion with a set of bolt holes through it. Each bolt hole
has a corresponding bolt seat, and the bolt seats are staggered in
the direction of the axis that extends through the section of pipe
and the flange member.
BRIEF DESCRIPTION OF THE DRAWINGS
[0007] Other objects and advantages of the invention may become
apparent upon reading the following detailed description and upon
reference to the accompanying drawings.
[0008] FIG. 1 is a perspective view of an exemplary pipe
connection.
[0009] FIG. 2 is an end view of the pipe connection of FIG. 1
showing the bolt configuration of the connection.
[0010] FIG. 3 is a cross-sectional side view of a pipe connection
in accordance with one embodiment.
[0011] FIG. 4 is a detail view of the hub and weld neck area of one
of the flange members of the pipe connection of FIG. 3.
[0012] FIG. 5 is a detail view of the hub and weld neck area of a
flange member having a positive hub in accordance with one
embodiment.
[0013] While the invention is subject to various modifications and
alternative forms, specific embodiments thereof are shown by way of
example in the drawings and the accompanying detailed description.
It should be understood, however, that the drawings and detailed
description are not intended to limit the invention to the
particular embodiment which is described. This disclosure is
instead intended to cover all modifications, equivalents and
alternatives falling within the scope of the present invention as
defined by the appended claims.
DESCRIPTION OF EXEMPLARY EMBODIMENTS
[0014] An improved design for a pipe connection is disclosed
herein. This design can reduce the size and weight of large,
high-pressure pipe connections, thereby making the connections
smaller, lighter, less expensive, and easier to manufacture,
transport, install and assemble.
[0015] Embodiments of the pipe connection may incorporate two
distinct, unique features. First, the connection may incorporate a
reverse spline hub between the outer portions of the flanges and
the corresponding weld necks. Second, the connection may be
configured so that the bolts that secure the two flanges of the
connection together are staggered.
[0016] Pipe connections that are secured by bolts are only as
strong as the bolts that hold the flanges together. The strength of
the bolts is directly related to the cross-sectional area of the
bolts. There are well-known calculations that are conventionally
used to determine the bolt area that is required to meet the design
goals of the connection. The bolt area drives the size and number
of the bolts that are required to secure the connection.
[0017] Large, high-pressure connections normally require many bolts
to secure the flanges of the connection to each other.
Conventionally, the bolts are arranged in a circular pattern around
the flanges. This is referred to as the "bolt circle".
[0018] In a conventional connection, the flanges of the connection
have all of the bolts at symmetric positions. That is, the bolts
are identically positioned axially (i.e., in the direction of the
connection's axis), but they are angularly displaced (with respect
to the axis of the connection) on the bolt circle. Because it is
necessary to provide some spacing between the bolts in order to
maintain the flanges'integrity and to provide enough space to
tighten the bolts, it is typically necessary to increase the size
of the flanges (i.e., increase their diameters) in order to
increase the bolt circle and thereby accommodate all of the
necessary bolts. This increases the weight and the cost of the
connection.
[0019] Increases in the size of the bolt circle also affect the
stresses on the flanges. The connection typically includes a gasket
that is positioned between the flanges. The gasket is normally
positioned near the inner diameter of the connection. Because the
bolt circle is larger than the gasket diameter, the tightening of
the bolts causes the outer portions of the flanges to flex,
rotating or pivoting around the gasket. The ratio of the bolt
circle to the gasket diameter is referred to as the "moment arm" of
the connection.
[0020] As the moment arm of the connection increases, the stresses
that are placed on the flanges increase. Conventionally, it is
necessary to increase the thickness of the flanges in order to
withstand the increased stress. Thus, according to conventional
design principles, increased bolt area leads to an increased bolt
circle, which increases the moment arm, leading to increased
thickness, weight and cost.
[0021] In one embodiment of the present connection, the bolts are
staggered axially (in the direction of the axis of the connection)
so that when a bolt extending through the flanges is tightened, the
positions of the adjacent bolts do not interfere with the
tightening of the first bolt. This allows the bolts to be
positioned more closely to each other than would be possible using
conventional design principles. Then, because the bolts can be
closer to each other, the bolt circle can be reduced. The reduced
size of the bolt circle results in a reduced flange diameter, a
reduced moment arm, reduced flange thickness, reduced weight, and
reduced cost in comparison to a conventional flange with comparable
performance.
[0022] Referring to FIG. 1, a perspective view of an exemplary
connection is shown. It can be seen that the two flanges (110, 111)
are secured to each other by a plurality of bolts (e.g., 120-124).
It can also be seen that the flanges incorporate recesses which
allow alternate ones of the bolts to be displaced axially with
respect to their neighbors. Thus, the head of a bolt (e.g., 130)
can be positioned within a recess (e.g., 140) so that it does not
interfere with the tightening of a nut (e.g., 151) on an adjacent
bolt. In this embodiment, the seats for half of the bolts are on a
first plane, while the seats for the remainder of the bolts are on
a second plane.
[0023] In this embodiment, successive bolts are oppositely oriented
so that, for a first bolt, the head is seated against a first one
of the flanges and the corresponding nut is seated against the
second one of the flanges, while for the adjacent bolt, the head is
seated against the second flange and the corresponding nut is
seated against the first flange. It should be noted that adjacent
bolts need not be oriented in opposite directions if they can
nevertheless be tightened on opposite ends (e.g., a wrench tightens
the nut on a first bolt, and tightens the heads of adjacent
bolts).
[0024] Referring to FIG. 2, an end view of the connection is shown.
In this figure, the axis of the connection is orthogonal to the
page. It should be noted that, while the bolt heads are depicted in
FIGS. 1 and 2 as being round, they may also be hexagonal or
otherwise shaped to prevent the bolts from rotating when seated in
the recesses. It can also be seen that the bolts are regularly
spaced on bolt circle 210. The connection is substantially
symmetric about its axis (160 in FIG. 1).
[0025] Because adjacent bolts are staggered axially and oriented in
opposite directions, the bolts can be placed closer together than
conventionally configured bolts. In other words, the need to be
able to position tools between adjacent bolts in order to tighten
them is removed as a design constraint, so the bolts can be closer
together, resulting in a smaller bolt circle. The smaller bolt
circle, in turn, results in smaller-diameter flanges, reduced
moment arms for flexion/rotation of the flanges, reduced flange
thickness, reduced weight and reduced cost.
[0026] It should be noted that the flanges of FIGS. 1 and 2 may be
of various different types and may include many different features
that are independent of the staggered bolt configuration that is
illustrated in the figures. For instance, the flanges may be solid
or they may contain multiple pieces, they may be swivel or
misalignment flanges, they may have positive or reverse hubs, and
so on.
[0027] Referring to FIG. 3, a cross-sectional side view of an
exemplary connection is shown. The illustrated connection is a
swiveling connection that employs a solid bolted flange member 310
and a swiveling flange member 320. Swiveling flange member 320
includes an inner flange portion 321 and a swiveling collar portion
322. Swiveling collar portion 322 rotates around inner flange
portion 321 to facilitate alignment of the bolt holes in the collar
with the bolt holes in solid flange 310. Swiveling collar 322 is
bolted to solid flange 310 to secure the connection. A
forward-facing shoulder 323 on swiveling collar 322 contacts a
complementary rear-facing shoulder 324 on inner flange portion 321
to secure the inner flange portion against solid flange 310. (Here,
"forward-facing" means facing toward the sealing face of the
flange, while "rear-facing" means facing away from the sealing face
of the flange.) Gasket 340 is positioned between the sealing faces
of the flange members to ensure a good seal.
[0028] It can be seen in FIG. 3 that the seats for the bolts (e.g.,
315, 316) are staggered axially by an amount that is sufficient to
eliminate overlap between the nut on one bolt (e.g., 381) and the
adjacent bolt (e.g., 382). It can also be seen in FIG. 3 that
flange member 310 does not have a conventional hub between the body
370 of the flange member and the weldneck 360. Solid flange member
310 instead employs a reverse spline hub 330 to minimize stresses
on the flange resulting from flexion of the flange around gasket
340. This is shown in more detail in FIG. 4.
[0029] In a flange having a conventional hub (e.g., as shown in
FIG. 5), a positive hub 510 is formed between the outer, bolted
portion of the flange 520 and the weldneck 530. The purpose of the
hub is to reduce stress on the weld neck when the flange is secured
to another flange, causing it to flex, rotating the bolted portion
of the flange 520 (counterclockwise in the figure) around the
gasket 540. In the absence of hub 510, the resulting stresses tend
to cause the flange to fail where the bolted portion of the flange
520 meets weldneck 530. Hub 510 is intended to reinforce this
failure point, but the hub may simply transfer the stresses,
causing the flange to fail at the junction between the hub and the
weldneck.
[0030] In the connection of FIG. 3, flange 310 uses what may be
referred to as a reverse hub. Rather than tapering from a larger
diameter to a smaller diameter as the distance from the face 380 of
the flange increases (a "positive" hub), the diameter of the flange
tapers from larger to smaller as the distance from the face 380 of
the flange decreases (a "reverse" hub). The conventional, positive
hub is shown in FIG. 5, and is illustrated by the dashed line in
FIG. 4 for purposes of comparison to the reverse hub.
[0031] Reverse hub 330 is referred to above as a reverse spline
hub. This indicates that reverse hub 330 follows a spline curve
which minimizes the stress caused by the rotation of the bolted
portion of the flange about the gasket. In this case, the spline
curve has been empirically determined to minimize the stress
resulting from rotation of the flange about the gasket.
[0032] It has been found that the reverse spline hub reduces
stresses induced by the rotation of flange 111 so effectively that
the flange can be made thinner (i.e., thickness T can be reduced),
as a greater amount of rotation of the flange can be tolerated
without exceeding stress limits at the junction between the hub and
the weldneck. Thus, the reverse spline reduces the size and weight
of the connection, both by eliminating the material that would form
the hub in a conventional connection, and by eliminating material
when the thickness of the flange is reduced.
[0033] It should be noted that the embodiments described above are
exemplary, and are intended to be illustrative of the many
embodiments that are possible. Alternative embodiments may
incorporate only selected ones of the features described above, or
they may have variations of these features. For example,
alternative embodiments may or may not include swiveling flange
members or reverse hubs. The various embodiments of the invention
may be connected (e.g., welded) to pipe sections, or they may be
separate from the pipe sections.
[0034] The benefits and advantages which may be provided by the
present invention have been described above with regard to specific
embodiments. These benefits and advantages, and any elements or
limitations that may cause them to occur or to become more
pronounced are not to be construed as critical, required, or
essential features of any or all of the claims. As used herein, the
terms "comprises," "comprising," or any other variations thereof,
are intended to be interpreted as non-exclusively including the
elements or limitations which follow those terms. Accordingly, a
system, method, or other embodiment that comprises a set of
elements is not limited to only those elements, and may include
other elements not expressly listed or inherent to the claimed
embodiment.
[0035] The preceding description of the disclosed embodiments is
provided to enable any person skilled in the art to make or use the
present invention. Various modifications to these embodiments will
be readily apparent to those skilled in the art, and the generic
principles defined herein may be applied to other embodiments
without departing from the spirit or scope of the invention. Thus,
the present invention is not intended to be limited to the
embodiments shown herein but is to be accorded the widest scope
consistent with the principles and novel features disclosed herein
and recited within the following claims.
* * * * *