Title of Invention

"CENTROIDALLY TWISTABLE COMPRESSION LOCKING RING FOR PIPE JOINTS"

Abstract A locking ring designed to work in a self restraining pipe joint. This locking ring is designed (which may include attention to a combination of shape and material properties) to twist when exposed to a concentrated bad and thereby distribute this load across broader area of the pipe joint to increase the thrust restraining capabilities of the joint.
Full Text Centroidally Twistable Compression Ring For Pipe Joints
Field of Invention and Basic Summary
A locking ring designed to work in a self restraining pipe joint. This locking ring is
designed (which may include attention to a combination of shape and material
properties) to deform when exposed to a concentrated load and thereby distribute this
load across broader area of the pipe joint to increase the thrust restraining capabilities of
the joint
Background and General
A current state of the art self restraining pipe joint is commonly known as the TR
FLEX® Pipe joiint as manufactured by U.S. Pipe and Foundry Co. Inc. This is described
in U.S. Patent 4,540,204 among others, which relies on individual locking segments
engaging a weld bead on the spigot (male) end of one pipe with a cavity formed into the
bell (female) end of the joining or mating pipe.
Several areas for improvement have been identified concerning the prior art involving
this concept. The first is that the individual locking segments may not fiilly engage the
weld bead placed on the spigot end of the pipe imder all assembly conditions (including
layout configujrations and dimensional variations). These conditions may be so severe
that the segments may, in fact, miss the weld bead entirely. This condition will greatly
affect the thrust restraining capability of the joint. The second issue is that when the
joint is deflected, the spigot approaches the bell at an angle instead of being concentric
and parallel. This condition alters the longituduial gap between the segment cavity (the
bell groove) in the bell of one pipe and the weld bead on the spigot end of the other
pipe. In short, the gap has a varying magnitude of separation. This gap is what is
typically bridged by the individual locking segments. Only the locking segment(s) in the

area of the smallest gap therefore will be engaged, creating a concentrated load on the
bell and spigot of the mating pipe. The tliird issue is that assembly may be difficult in all
but the most ideal circumstances since the individual locking segments must slide into
the gap between the spigot and bell of mating pipes and this gap must be kept small in
order to allow the segments to engage both halves of the pipe joint. The fourth issue is
that the joint is sensitive to manufacturing tolerances. If the tolerances are allowed to
vary too much, then the locking segments may not engage the spigot end of the matmg
pipe resulting in reduced joint performance.
OBJECTS OF THE INVENTION:
The following stated objects of the invention are alternative and exemplary objects only,
and no one or any should be read as required for the practice of the invention, or as an
exhaustive listing of objects accomplished.
Improve the state of the art restrained joint performance over a wide variety of
installation conditions, assembly conditions and manufacturing tolerances.
Make the joint easier and faster to assemble in a wide variety of assembly conditions
and manufacturing tolerances.
Allow larger meinufacturing tolerances to be used with no compromise in performance.
The above objects and advantages are neither exhaustive nor individual critical to the
spirit and practice of the invention, except as stated in the claims as issued. Other
alternative objects and advantages of the present invention will become apparent to
those skilled in the art from the following description of the invention.
SUMMARY OF THE INVENTION
A locking ring designed to work in a self restraining pipe joint. This locking ring is
designed (which may include attention to a combination of shape and material
properties) to twist whep exposed to a concentrated load and thereby distribute this load

across broader area of the pipe joint to increase the thrust restraining capabilities of the
joint.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 shows a cut-away view of a portion of a pipe joint using an embodiment of a
locking ring of the present invention, showing the locking ring in place between a pipe
bell and pipe spigot the axes of which are aligned radially and angularly.
Figure 2 shov/s a cross section of an embodiment of a locking ring of the present
invention.
Figure 3 shows an isometric view of an embodiment of a locking ring of the present
invention.
Figvire 4 shows a view of an embodiment of a locking ring of the present invention as
seen looking along the plane of the ring, with the ears to the side.
Figure 5 shows a view of an embodiment of a locking ring of the present invention as
seen looking along the plane of the ring, with the ears centered in the view to show a
split.
Figure 6 shows a side view of an embodiment of ears on an embodiment of a locking
ring of the present invention.
Figure 7 shows a top-down view of an embodiment of a locking ring of a the present
invention (i.e., seen as viewed from a position outside the plane of the locking ring).
Figure 8 shows a top-down view of an embodiment of ears on an embodiment of a
locking ring of the present invention.

Figvire 9 shows a pipe joint incorporating an embodiment of a locking ring of the
present invention, in which the axes of the pipe bell and the pipe spigot are angularly
displaced from one another.
Figure 10 shows another view as in Figure 9, with stronger angular displacement.
Figure 11 shows a view of an embodiment of a locking ring of the present invention,
demonstrating a twist occurring along the centroidal axis.
DETAILED DESCRIPTION OF THE INVENTION:
The following is a detailed exemplary description of an embodiment of the invention, in
a number of its various aspects. Those skilled in the art will xmderstand that the
specificitjf provided herein is intended for illustrative purposes with respect to an
exemplarj,^ embodiment, only, and is not to be interpreted as limiting the scope of the
invention or claims.
Turning to Figure 1, a cross-sectional view of a joint of the present invention is shown,
with the locking ring 2, a substantially ring-shaped body in place to prevent extraction
of the pipe spigot 6 from the bell I. In Figure 1, the locking ring 2 is shown in a resting
state (intlie absence offerees exerted upon it in an angularly or radially displaced joint).
As is apparent from the depiction in Figure 1, particularly to those of ordinary skill in
the art, in the joint the pipe spigot 6 is partially disposed within the pipe bell 1 in sach a
manner tiiat there is some aimular gap 20 between the two, but locking ring 2 has a
greater radial height than the aimular gap 20. Accordingly, locking ring 2 cannot pass
through tlie annular gap 2. The shown embodiments used by the inventors are pipes and
bells of metal, specifically, ductile iron. Those in the art will understand that in normal
assembly the locking ring 2 is inserted into the pipe bell 1, and disposed in the bell
groove 12 prior to insertion of the pipe spigot 6 into the pipe bell 1. bell groove 12 may
approximate the configuration of locking ring 2 as shown in Figure 1, but in any event
the size of the bell groove 12 is greater than the size of the locking ring 2, so as to allow

some freedom of movement of the locking ring 2 within the confines of bell groove 12
(until the locking ring 2 is clamped in place or the joint is subjected to thrust loads).
Because of this freedom of movement, the pipe spigot 6 can be inserted until at least the
position showTi in Figure 1 by passing the weld bead 5 under the locking ring 2, such as
occurs when locking ring 2 is held away from the pipe spigot 6 (e.g. by spring tension
of the ring) or otherwise is not held firmly against pipe spigot 6. It will be appreciated
from the drawing in Figure 1 that the weld bead 5 is axially inward (to the right in the
drawmgs) of bell thrust face 4. Sealing, rmgs, such as gaskets, may be disposed at
locations in tlie joint to provide fluid seal in addition to the restraint effected by the
locking ring 2 of the present invention. By way of example, bell groove 12 in Figure 1
is shown radially outward of (to the left of, in the drawings) such a seaUng area.
As shown, pipe Bell 1 engages lockmg ring 2 via ring thrust face 3 and bell thrust face
4. These surfa approximately 30 degrees to a radial projecting from the centerline of the pipe bell. This
mating angle dletermines the relationship of thrust load (restraint) to radial (locating)
load. Restraint of the thrust load is ibe objective, but a minimal radial load is required to
locate and retaiin the locking ring. The relationship of these two forces influences the
overall restraint of the joint, and is addressed by the invention. The locking ring 2 is
located between bell thrust face 4 and the weld bead 5. The locking ring is clamped to
the outside surface of the pipe spigot 6 during assembly such that the inside comer 7 of
the locking ring engages the weld bead 5, such engagement occurring at least when the
pipe spigot 6 is idrawn outward of the pipe bell I. The load patii is thus complete. Thrust
is transferred from the pipe bell 1 to the locking ring 2 via the thrust faces (3 and 4) and
then to the pipe spigot 6 via the inside comer 7 and weld bead 5 interface. After initial
assembly, the action of the bell groove 12 around the locking ring 2 may render
continued use of the clamping force unnecessary in some embodiments. As shown in
the Figures, ring spigot face 9, and m fact locking ring 2, is not mtended to bite into or
cause deformation of the pipe spigot 6, as the resistance to movement is imparted by the
weld bead 5. In the shown embodiments it is therefore devoid of teeth adapted to bite
into pipe spigot 6.

Non-exhaustive examples of ways to clarnp the locking ring 2 to the outside surface of
pipe spigot 6 include use of a ring with a resting configuration having a smaller
diameter than the pipe spigot 6 (which Ciui be manually expanded to allow passage of
the weld bead 5 thereunder) or use of csdipers or other mechanisms to draw the split
ends of the locking ring 2 together after weld bead 5 has passed by the locking ring 2 on
its passage into the pipe bell 1. As shown in Figures 3 through 8, a particularly shown
embodiment of the invention uses ears ("tabs") at the split ends of the locking ring 2,
which tabs extend axially of the locking ring 2 (i.e., they are perpendicular to the plane
of the locking ring 2). These tabs in tlie shown drawings are configured to extend
outside of the pipe bell 1 even while locking ring 2 is within the bell groove 12,
allowing them to be gripped, ratcheted together, bolted in place, or otherwise acted on
in a way to diraw the split ends of locking ring 2 together, or to press locking ring 2 into
clamped association with the pipe spigot 2. In one configuration used by the inventors,
the pipe bell 1 includes a slot or cut-out at some point along its outer face 13, which slot
or cut-out is big enough to allow passage of the tabs therethrough. Alternatively, the
tabs could be configured to pass through the annular gap 20 to become accessible
outside of the pipe bell 1. As seen from the immediately preceding paragraph, when the
locking ring 2 is clamped to the pipe spigot 6, either by way of a clampmg force
generated as discussed in this paragraph, or by the action of the pipe bell 1 around the
locking ring 2, the locking ring 2 caimot slide outward of pipe bell 1 because it is
greater in radial height than the height of annular gap 20, and weld bead 5 cannot slide
past locking ring 2 because of its abutment with pipe spigot 6. As suggested in the
preceding panagraph, and as would be understood from the drawing in Figure 1, the
abutment of locking ring 2 and pipe spigot 6 is furthCT ensured (during movement of the
pipe spigot 6 outward of pipe bell 1, which is movement of the pipe spigot 6 to the left
in Figure 1) by the feet that bell thrust face 4 and ring thrust face 3 meet at an angle
which results in a "sliding wedge" action. In other words, for every imit of movement
of locking ring 2 in an outward direction of the pipe bell 1 (i.e., to the left in Figure 1),
the locking ring 2 is also urged radially inwardly, which is toward more forced contact
with the pipe spigot 6.

When the centerHnes of the two halves of the mating joint (e.g. the pipe bell 1 and the
pipe spigot 6) are concentric, and ignoring manufacturing imperfections, the thrust load
is evenly distibuted annularly around the mating surfaces of the locking ring 2. If the
joint is deflected such that the centerline of one half of the joint (e.g. bell or spigot) is no
longer concentric with the centerline of the other half of the joint (i.e. one centerline is
offset by an angular or radial displacement), then the load is no longer evenly
distributed annularly around the locking ring, but is concentrated in a specific region of
the ring. This region of concentrated load is generally located at the closest longitudinal
point between the bell thrust face 4 and the weld bead 5. Current state of the art
restrained joints would suffer reduced performance (e.g. a reduced ability to withstand
full thrust loads) due to this concentrated loading condition. In this invention, the one
piece locking iring 2 distributes this concentrated load by twisting (deforming) about its
centroidal axis. This twisting alters the apparent longitudinal length of the locking ring,
and allows the locking ring to bridge a constantly varying gap between the bell thrust
face 4 and the weld bead 5 Where the joint is not displaced, the locking ring 2, as
shown in Figure 1, does not twist See, for example, Figure 9, which shows a locking
ring 2 in position ia an angularly displaced joint. As shown in Hhe Figure 9, locking ring
2 is twisted about its centroidal axis (see that the ring spigot face 9 is essentially
horizontal, or parallel to the bell axis, in the upper locations at location x and at the
same time is at an angle essentially parallel to the axis of the Spigot 6, at location y,
which can only occur if the locking ring 2 is twisting along its length). By way of
example, the action of this twisting causes the ring to rotate about the centroidal axis at
one location to a greater degree (or even in a different direction) than at another location
along the locking ring 2, such as would occur if a rubber ring stretched over a tube were
held in place in one location, and were rolled along the surface of the tube at another
location. Figure 10 shows a more extremely deflected joint, also depictiug twisting.
Figure 11 shov/s a cut-away of the locking ring 2, depicting the twisting by showing a
cut-away of the locking Ring 2 resting on a flat surface, to exemplify the twisting that
can occur. This ability of the locking ring to twist is affected by the shape of the cross
section of the locking ring and the material properties of the ring.

In practice, in a deflected joint wherein tlie locking ring 2 has twistid, the ring spigot
face 9 may eiojoy a range of angular relationships to the pipe spigot 6. That is, varying
angles may be presented between the ring spigot face 9 and the pipe spigot 6 along the
ring's inner circumferential length. By way of example, it may be substantially flat
(parallel) abutoent to pipe spigot 6 at some locations, while the ring outside comer 11
or the inside comer 7 (or both at different locations) rise to varying degrees along the
length.
In the shown embodiments, for instance, the cross sectional shape of the ring is
generally a trapezoid (if ring top 10 is considered a "side"; otherwise, consistent with
the dravmg shown it could be considered a triangular cross section) with a horizontal
bottom surface:, a ring thrust fece 3 of about 30 degrees (measured from the vertical), a
ring back face 8 of about 10 degrees (measured firom the vertical) and overall
dimensions of approximately about 1 inch high by about 1 inch wide (as seen from the
figures, the edges may be rounded, rather than coming to precise points). The material
in the shown instance is 65-45-12 Ductile Iron. The weight for a ring as shown in the
embodiment depicted in the drawings, assuming an inner diametCT of 44.3 inches and
ear length of 4.5 inches has been seen to be approximately 27.8 lbs. As shown from
Figures 3, 4, 5, and 7, the locking ring 2 in its resting state is essentially flat along its
plane (i.e., is not yet twisted, the twisting occurring, as discussed above, in response to
radial or particularly angular displacement).
The ring thrust face 3 angle in the shown embodiment matches the angle of the bell
thrust face 4, though precise matching is not required. This angle typically is between
about 10 and about 45 degrees from a direct radial line (vertical) and is dependent on
the desired ratio between thrust (longitudmal) load and radial load. Overall length and
width of the cross section can be any desired value corresponding to the strength and
stiffiiess desired. The back fece can be any angle between 0 and 60 degrees depending
on the desired stiffness (resistance to twist) and location of the centroid. The material
may be any material of suitable ductility and resistance to bearmg stress.

In some embodiments the invention allows the joint to maintain substantially its full
thrust restraint rating over substantially the full range of assembly conditions (including
layout configurations and dimensional variations) whereas joints of the prior art may
exhibit reduced performance in some assembly conditions.
Likewise, in some embodiments, the invention allows quicker and easier assembly in
the field over the prior art. Some embodiments of the invention may allow the use of
larger manufacturing tolerances in the pipe bell without risk of losing contact with the
mating pipe's Aveld bead. Some embodiments of the invention allow the potential
reduction of mjanufacturing cost of the joint through reduced material requirements
compared to rigid rings or individual segments.
The foregoing represaits certain exemplary embodiments of the invention selected to
teach the principles and practice of the invention generally to those in the art so that
they may use tlieir standard skill in the art to make these embodiments or other and
variable embodiments of the claimed invention, based on industry skill, while remaining
within the scopes and practice of the invention, as well as the inventive teaching of this
disclosure. The inventor stresses that the invention has numerous particxilar
embodiments, tihe scope of which shall not be restricted further than the claims as
issued. Unless otherwise specifically stated, applicant does not by consistent use of any
term in the detailed description in connection with an illustrative embodiment intend to
limit the meaning of that term to a particular meaning more narrow than that understood
for the term generally. Moreover, stated advantages are exemplary and alternative,
only, and shoxild not be interpreted as required in all cases.
The figures shown are of illustrative embodiments, only. Notes, finishing, and
measurements va such images are precise for such embodiments shown, but variation
may be made as would be aqppreciable to one of ordinary skill in the art.

CLAIMS
I Claim:
1. A locking ring for use in restraining a pipe joint between a first pipe and a
second pipe, said locking ring comprising a substantially ring-shaped body, that
a. is in a resting shape that is maintained in the joint during the absence of a
force tending to separate the joint, and
b. is adapted to twist in response to said force when an axis of the first pipe
is displaced radially or angularly from an axis of the second pipe.
2. A locking ring as in Claun 1, wherein the resting shape is not twisted.
3. A locking ring as in Claim 1, wherein in the resting shape a radially inner
surface of the locking ring is substantially parallel to the second pipe, and
wherein after twisting at least a portion of the radially inner surface is off-
paraJUel with respect to the second pipe by an angle that varies along the locking
ring.
4. A locking ring as in Claim 3, -wdierein the radizilly irmer surface is substantially
flat.
5. A locking ring as in Claim 1, comprising
a. a radially inner surface adapted to be placed in contact with the second
pipe,
b. a ring thrust surface adapted to contact a bell thrust surface located
within a bell groove of the first pipe
Virherein an angle between the ring thrust surface and the radially inner
surface is between 45 degrees and 80 degrees.
6. A locking ring as in Claim 1, comprising 65-45-12 ductile iron.

7. A iocldng ring as ia Claim 1, comprising a cross section substantially as shovvTi
in Figure 2.
8. A locking ring as in Claim 1, which is devoid of teeth capable of substantially
biting into a pipe spigot of the second pipe.
9. A locking ring as in Claim 1 wherein by said twisting the locking ring is adapted
to bridge a gap of varying magnitude between a bell thrust face of the first pipe
and a weld bead on a pipe spigot of the second pipe.
10. A locking ring for use in restraining a pipe joint between a first pipe and a
second pipe, said locking ring comprising a substantially ring-shaped body with
loQgitudioal length, wherein the locking ring is adapted to change the
longitudinal lengtii by twisting.
11. A locking ring as in Claim 10 wherein said change in axial length varies in
magnitude between a first location on the locking ring and a second location on
the locking ring.
12. A locking ring as in Claim 10 wherein by said twisting the locking ring bridges
a gap of varying magnitude between a bell thrust face of the first pipe and a
wdd bead on a pipe spigot of the second pipe.
13. A locking ring as in Claim 10, wherein in a resting state the locking ring is not
tv/isted.
14. A locking ring as in Claim 10, wherein in a resting state the locking ring
possesses a radially inner surface that adapted to be substantially parallel to the
second pipe, and wherein after twisting at least a portion of the radially inner
surface is off-parallel with respect to the second pipe by an angle that varies
along the locking ring.
15. A locldng ring as in Claim 10, comprising a radially inner surface that is
substantially flat.
16. A locking ring as in Claim 10, comprising
a. a radially inward surface adapted to be placed in contact with the second
pipe,
b. a ring thrust surface adapted to contact a bell thrust surface located
within a bell groove of the first pipe
wherein an angle between the ring thrust surface and the radially inward
suirface is between 45 degrees and 80 degrees.
17. A locking ring as in Claim 10, comprising 65-45-12 ductile iron.
18. A locldng ring as in Claim 10, comprising a cross section substantially as shown
in Figure 2.
19. A locking ring as in Claim 10, which is devoid of teeth capable of substantially
biting into a pipe spigot of the second pipe.
20. A pipe joint comprising
a. A first pipe comprising a pipe bell and a bell groove disposed annxilarly
within the pipe bell, said bell groove being bounded on an axially
outward side by a bell thrust surface,
b. A second pipe comprising a pipe spigot and a weld bead located on the
pipe spigot, said pipe spigot located partially within the pipe bell in a
position in which the weld bead is further, by an axially measured
distance, within the pipe bell than is the bell thrust surface, wherein the
pipe spigot is radially separated from the pipe bell at a location around
the pipe spigot periphery by an aimular gap, and
c. A locking ring being located between and in substantially continuous
contact vv^ith the bell thrust surface and with the weld bead, which bell
thrust surface and weld bead are separated by a gap having different
measurements when measured at different locations in the pipe joint.
21. A pipe joint as in Claim 20, wherein the locking ring comprises at least one
cross-sectional dimension greater than a distance of the annular gap.
22. A pipe joint as in Claim 20 in which the locking ring twists in response to
angular displacement of an axis of the first pipe from an axis of the second pipe.
23. A pipe joint as in Claim 20 in which the locking ring twists in response to radial
displacement of an axis of the first pipe from an axis of the second pipe.
24. A pipe joint as in Claim 20 in which the bell thrust surface is disposed at an
angle of between 10 degrees and 45 degrees oflF of radial.
25. A pi|:>e joint as in Claim 20 in which the locking ring comprises a ring back face
that is disposed at an angle of approximately 10 degrees off of radial


A locking ring designed to work in a self restraining pipe joint. This locking ring is
designed (which may include attention to a combination of shape and material
properties) to twist when exposed to a concentrated bad and thereby distribute this
load across broader area of the pipe joint to increase the thrust restraining capabilities
of the joint.

Documents:

00272-kolnp-2006-abstract.pdf

00272-kolnp-2006-claims.pdf

00272-kolnp-2006-description complete.pdf

00272-kolnp-2006-form-1.pdf

00272-kolnp-2006-form-2.pdf

00272-kolnp-2006-form-3.pdf

00272-kolnp-2006-form-5.pdf

00272-kolnp-2006-international publication.pdf

272-KOLNP-2006-(05-03-2012)-CORRESPONDENCE.pdf

272-KOLNP-2006-(24-10-2011)-ABSTRACT.pdf

272-KOLNP-2006-(24-10-2011)-AMANDED CLAIMS.pdf

272-KOLNP-2006-(24-10-2011)-DESCRIPTION (COMPLETE).pdf

272-KOLNP-2006-(24-10-2011)-DRAWINGS.pdf

272-KOLNP-2006-(24-10-2011)-EXAMINATION REPORT REPLY RECIEVED.pdf

272-KOLNP-2006-(24-10-2011)-FORM 1.pdf

272-KOLNP-2006-(24-10-2011)-FORM 2.pdf

272-KOLNP-2006-(24-10-2011)-FORM 3.pdf

272-KOLNP-2006-(24-10-2011)-FORM 5.pdf

272-KOLNP-2006-(24-10-2011)-OTHERS.pdf

272-KOLNP-2006-(24-10-2011)-PA.pdf

272-KOLNP-2006-(24-10-2011)-PETITION UNDER RULE 137.pdf

272-KOLNP-2006-(25-01-2012)-CORRESPONDENCE.pdf

272-kolnp-2006-abstract.pdf

272-kolnp-2006-assignment.pdf

272-kolnp-2006-claims.pdf

272-KOLNP-2006-CORRESPONDENCE 1.2.pdf

272-KOLNP-2006-CORRESPONDENCE-1.1.pdf

272-kolnp-2006-correspondence.pdf

272-kolnp-2006-description (complete).pdf

272-kolnp-2006-drawings.pdf

272-KOLNP-2006-EXAMINATION REPORT.pdf

272-kolnp-2006-form 1.pdf

272-kolnp-2006-form 18.pdf

272-kolnp-2006-form 2.pdf

272-kolnp-2006-form 26.pdf

272-KOLNP-2006-FORM 3 1.1.pdf

272-kolnp-2006-form 3.pdf

272-kolnp-2006-form 5.pdf

272-KOLNP-2006-GRANTED-ABSTRACT.pdf

272-KOLNP-2006-GRANTED-CLAIMS.pdf

272-KOLNP-2006-GRANTED-DESCRIPTION (COMPLETE).pdf

272-KOLNP-2006-GRANTED-FORM 1.pdf

272-KOLNP-2006-GRANTED-FORM 2.pdf

272-KOLNP-2006-GRANTED-LETTER PATENT.pdf

272-KOLNP-2006-GRANTED-SPECIFICATION.pdf

272-KOLNP-2006-OTHERS.pdf

272-KOLNP-2006-REPLY TO EXAMINATION REPORT.pdf

272-kolnp-2006-specification.pdf

abstract-00272-kolnp-2006.jpg


Patent Number 252234
Indian Patent Application Number 272/KOLNP/2006
PG Journal Number 18/2012
Publication Date 04-May-2012
Grant Date 02-May-2012
Date of Filing 06-Feb-2006
Name of Patentee UNITED STATES PIPE & FOUNDRY COMPANY, LLC
Applicant Address 3300 FIRST AVENUE NORTH BIRMINGHAM, AL
Inventors:
# Inventor's Name Inventor's Address
1 COPELND, DANIEL A 5020 SOUTH SHADES CREST ROAD BESSEMMER AL 35022-4123
PCT International Classification Number F16B
PCT International Application Number PCT/US2004/031595
PCT International Filing date 2004-09-24
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 60/508,081 2003-09-25 U.S.A.