U.S. patent application number 15/924986 was filed with the patent office on 2018-07-26 for apparatus for tightening threaded fasteners.
This patent application is currently assigned to HYTORC Division UNEX Corporation. The applicant listed for this patent is HYTORC Division UNEX Corporation. Invention is credited to Michael F. Dolan.
Application Number | 20180209469 15/924986 |
Document ID | / |
Family ID | 45559876 |
Filed Date | 2018-07-26 |
United States Patent
Application |
20180209469 |
Kind Code |
A1 |
Dolan; Michael F. |
July 26, 2018 |
APPARATUS FOR TIGHTENING THREADED FASTENERS
Abstract
According to a first aspect of the invention we provide an
apparatus for coupling a shank of a threaded fastener and a torque
device including: --a first coupling member having an external
surface portion defined by more than two steps that forms a taper;
a second coupling member having an inversely tapered internal
surface portion non-rotatably engagable with the tapered external
surface of the first coupling member; wherein the steps of the
first coupling member and the second coupling member are shaped
either as angled cylinders, frustums of an angled stepped cone or
frustums of an angled curved solid; and wherein the diameters of
the steps of the first coupling member and the second coupling
member are less than the diameter of the shank. Advantageously,
this aspect of the invention allows for an increased load bearing
surface area between the coupling members without increasing the
overall diameter of the apparatus; a three dimensional load bearing
surface area rather than a conventional two dimensional plane; more
efficiently and evenly distributed load stress distribution over
the load bearing surface area; higher torsion strength; and
apparatus with lower mass, dimensions and volume.
Inventors: |
Dolan; Michael F.;
(Kenilworth, NJ) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
HYTORC Division UNEX Corporation |
Mahwah |
NJ |
US |
|
|
Assignee: |
HYTORC Division UNEX
Corporation
Mahwah
NJ
|
Family ID: |
45559876 |
Appl. No.: |
15/924986 |
Filed: |
March 19, 2018 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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13814229 |
Mar 27, 2013 |
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PCT/US2012/023693 |
Feb 2, 2012 |
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15924986 |
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PCT/IB2011/002658 |
Aug 2, 2011 |
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13814229 |
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61370015 |
Aug 2, 2010 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
B25B 15/008 20130101;
B25B 23/0085 20130101; F16B 39/36 20130101; F16B 37/00 20130101;
F16B 31/027 20130101; F16B 31/02 20130101 |
International
Class: |
F16B 37/00 20060101
F16B037/00; F16B 39/36 20060101 F16B039/36; F16B 31/02 20060101
F16B031/02; B25B 15/00 20060101 B25B015/00; B25B 23/00 20060101
B25B023/00 |
Claims
1. An apparatus for coupling a shank of a threaded fastener and a
torque device including:-- a first coupling member having an
external surface portion defined by more than two steps that forms
a taper; a second coupling member having an inversely tapered
internal surface portion non-rotatably engagable with the tapered
external surface of the first coupling member; wherein the steps of
the first coupling member and the second coupling member are shaped
either as angled cylinders, frustums of an angled stepped cone or
frustums of an angled curved solid; and wherein the diameters of
the steps of the first coupling member and the second coupling
member are less than the diameter of the shank.
2. An apparatus according to claim 1 wherein the steps of the first
coupling member and the second coupling member are shaped as solids
not limited to particular step quantities, dimensions, geometries,
angles and/or intervals.
3. An apparatus according to claim 1 wherein the internal surface
portion of the second coupling member substantially surrounds the
external surface portion of the first coupling member.
4. An apparatus according to claim 1 wherein the first coupling
member is non-rotatably engagable with an action portion of the
torque device.
5. An apparatus according to claim 1 wherein the second coupling
member, when rotated by an action portion of the torque device,
applies a load to the threaded fastener.
6. An apparatus according to claim 1 wherein the first coupling
member is formed on a reaction shaft of the torque device and
wherein the second coupling member is formed on the shank of the
threaded fastener.
7. An apparatus according to claim 6 wherein the first coupling
member is formed as an axial protrusion and wherein the second
coupling member is formed as an axial bore.
8. An apparatus according to claim 1 wherein the first coupling
member is formed on a shank of the threaded fastener and wherein
the second coupling member is formed on a reaction shaft of the
torque device.
9. An apparatus according to claim 8 wherein the first coupling
member is formed as an axial bore and wherein the second coupling
member is formed as an axial protrusion.
10. An apparatus according to claim 1 having an infinite number of
steps such that the external surface portion of the first coupling
member is smoothly tapered and the inversely tapered internal
surface portion of the second coupling member is smoothly
tapered.
11. A system for fastening objects including a combination of a
torque power tool either pneumatically, electrically, hydraulically
or manually driven and a threaded fastener having an apparatus
according to either claim 1-10.
Description
CROSS REFERENCE TO RELATED APPLICATION
[0001] This Application is a divisional application of co-pending
U.S. application Ser. No. 13/814,229, having Filing Date of 27 Mar.
2013, entitled "Apparatus For Tightening Threaded Fasteners", an
entire copy of which is incorporated herein by reference and from
which the present application claims its priority under 35 USC
119(a)-(d).
[0002] Innovations disclosed in this Application advance technology
disclosed in the following commonly owned issued patents and patent
applications, entire copies of which are incorporated herein by
reference: U.S. Pat. No. 5,137,408, having Filing Date of Dec. 3,
1991, entitled "Fastening Device"; U.S. Pat. No. 5,318,397, having
Filing Date of May 7, 1992, entitled "Mechanical Tensioner"; U.S.
Pat. No. 5,622,465, having Filing Date of Apr. 26, 1996, entitled
"Lock Nut"; U.S. Pat. No. 5,640,749, having Filing Date of Jun. 13,
1995, entitled "Method Of And Device For Elongating And Relaxing A
Stud"; U.S. Pat. No. 5,888,041, having Filing Date of Oct. 17,
1997, entitled "Lock Nut"; U.S. Pat. No. 6,254,322, having Filing
Date of Mar. 3, 1998, entitled "Bolt With A Bolt Member, A Washer
And A Sleeve For Applying Forces To The Bolt Member And The
Sleeve"; et al.
DESCRIPTION OF INVENTION
[0003] Conventional threaded fasteners are known. Mechanical
fastening with helically threaded components is typically achieved
with bolts, studs, screws, nuts and washers. Washers are thin
members that can be placed between the fastener and the fastened
component. Washers are typically used to prevent frictional damage
to assembled components. Washers are also commonly used to
distribute stresses evenly and to control friction losses. Nuts are
internally threaded fastening members commonly used to retain and
or deliver load to an externally threaded fastener. Nuts typically
have an external geometry that will allow rotational coupling with
a torque input device or machine.
[0004] Self-reacting nuts are typically comprised of an inner
sleeve, outer sleeve and washer. Self-reacting fasteners such as
the HYTORC Nut use the washer as a reaction point for the
application of input torque to the outer sleeve. In a self-reacting
fastener the outer sleeve functions as the nut while the inner
sleeve becomes an extension of the stud and is rotationally coupled
with the washer. This rotational coupling prevents sliding motion
between the inner sleeve and stud threads during the application of
torque to the outer sleeve. Self-reacting nuts with the same
external geometry as conventional nuts suffer from higher bearing
surface stresses. The bearing surface stresses are higher because
the outer sleeve inside diameter is increased to allow space for
the inner sleeve causing a thinner wall thickness than standard
nuts.
[0005] In contrast to conventional threaded fasteners,
self-reacting three-piece mechanical tensioner fasteners such as
the HYTORC NUT, include an outer sleeve, inner sleeve and washer.
Self-reacting fasteners such as the HYTORC Nut use the washer as a
reaction point for the application of input torque to the outer
sleeve. In a self-reacting fastener the outer sleeve functions as
the nut while the inner sleeve becomes an extension of the stud and
is rotationally coupled with the washer. This rotational coupling
prevents sliding motion between the inner sleeve and stud threads
during the application of torque to the outer sleeve. Self-reacting
nuts with the same external geometry as conventional nuts suffer
from higher bearing surface stresses. The bearing surface stresses
are higher because the outer sleeve inside diameter is increased to
allow space for the inner sleeve causing a thinner wall thickness
than standard nuts.
[0006] Additionally devices of coupling or mating a reaction or an
output shaft of a torque output device to fasteners used in bolting
also are known. Self-reacting three-piece mechanical tensioner
fasteners typically have spline, hex or square features to allow
torsion coupling with the reaction member of the torque input
device. This is achieved with machined rotational interferences
between two parts. The interference is typically created with a
male and female engagement between any two mating features that
prevent rotation between the two parts.
[0007] Three-piece mechanical tensioning stud devices are also
known. They consist of a stud, nut and washer. The stud has
external threads on both ends. Under the upper thread the stud will
also have a spline or other geometry to create a rotational
coupling with the inner diameter of the washer. The topside of the
stud will also have a spline or other geometry to allow rotational
coupling with the reaction shaft of the torque input device. The
nut is internally threaded to mate with the threads on the topside
of stud. The nut will have a spline or other geometry to allow the
introduction of torque from torque input device. The washer has an
internal geometry that will mate rotationally with the spline or
other geometry under the top thread of the stud.
[0008] In bolting applications stresses are typically near the
elastic limits of the materials. The reaction feature that couples
the three-piece mechanical tensioning stud to the torque of the
torque input device typically has to be oversized to prevent
elastic material failures. Therefore it is not possible with known
coupling features to carry the high magnitude of torque with an
internal feature such as a square, hexagon or internal spline hole
in the top surface of the stud. Consequently prior art applications
that are subject to high bolting stress must have an external
feature on the topside of the stud that will allow the coupling of
a sufficiently sized reaction shaft from the torque input
device.
[0009] The present invention has therefore been devised to address
these issues.
[0010] According to a first aspect of the invention we provide an
apparatus for coupling a shank of a threaded fastener and a torque
device including: --a first coupling member having an external
surface portion defined by more than two steps that forms a taper;
a second coupling member having an inversely tapered internal
surface portion non-rotatably engagable with the tapered external
surface of the first coupling member; wherein the steps of the
first coupling member and the second coupling member are shaped
either as angled cylinders, frustums of an angled stepped cone or
frustums of an angled curved solid; and wherein the diameters of
the steps of the first coupling member and the second coupling
member are less than the diameter of the shank.
[0011] Advantageously, this aspect of the invention allows for an
increased load bearing surface area between the coupling members
without increasing the overall diameter of the apparatus; a three
dimensional load bearing surface area rather than a conventional
two dimensional plane; more efficiently and evenly distributed load
stress distribution over the load bearing surface area; higher
torsion strength; and apparatus with lower mass, dimensions and
volume.
[0012] Further features of the invention are set out in claims 2 to
24 appended hereto.
[0013] The invention may be described by way of example only with
reference to the accompanying drawings, of which:
[0014] FIG. 1 is a perspective view of a threaded fastener with an
embodiment of the present invention;
[0015] FIG. 2 is a side, cross-sectional view of an inner sleeve of
an embodiment of the present invention;
[0016] FIG. 3 is a side, cross-sectional view of an outer sleeve of
an embodiment of the present invention;
[0017] FIG. 4 is a side view of a threaded fastener for use with an
embodiment of the present invention;
[0018] FIG. 5 is a side, cross-sectional view of an embodiment of
the present invention;
[0019] FIG. 6 is a side, cross-sectional view of an embodiment of
the present invention;
[0020] FIG. 7 is a side, cross-sectional view of an embodiment of
the present invention;
[0021] FIG. 8 is a side, cross-sectional view of an embodiment of
the present invention;
[0022] FIG. 9 is a side, cross-sectional view of an embodiment of
the present invention;
[0023] FIG. 10 is a side, cross-sectional view of an embodiment of
the present invention;
[0024] FIG. 11 is a side view of an embodiment of the present
invention;
[0025] FIG. 12 is a perspective view of an embodiment of the
present invention;
[0026] FIG. 13 is a cross-sectional view of an embodiment of the
present invention;
[0027] FIG. 14 is a perspective view of an embodiment of the
present invention;
[0028] FIG. 15 is a perspective view of an embodiment of the
present invention;
[0029] FIG. 16 is a perspective view of an embodiment of the
present invention; and
[0030] FIG. 17 is a perspective view of an embodiment of the
present invention.
[0031] Referring to FIGS. 1-4 by way of example, this shows an
apparatus 1--a stepped conical fastener assembly--in accordance
with an embodiment of the present invention. Apparatus 1 has an
inner sleeve member 100 and an outer sleeve member 200 and is used
with, by way of example, a threaded stud 300. Inner sleeve member
100 is rotatably and threadedly engagable with stud 300; rotatably
and taperedly engagable with outer sleeve member 200; and
non-rotatably engagable with an action portion of a torque input
device. Outer sleeve member 200 is non-rotatably engagable with a
reaction portion of the torque input device; and rotatably and
taperedly engagable with inner sleeve member 100. Inner sleeve
member 100, when rotated by the action portion of the torque input
device, applies a load to stud 300 to close a joint (not
shown).
[0032] Inner sleeve member 100 is an annular body and, as shown in
FIGS. 1 and 2, formed as a sleeve. It has an inner surface 110 with
an inner helical thread means 120 engagable with an outer surface
310 with an outer helical thread means 320 of stud 300. It has an
outer surface 111 with a cylindrical formation 121 which is
rotatably engagable with an inner surface 210 with a cylindrical
formation 220 of outer sleeve member 200. It further has a lower
surface 113 which is rotatably engagable with inner surface
210.
[0033] Cylindrical formation 121 is shaped as an inverted frustum
of a stepped cone which has a tapered or conical appearance from
the bottom up. Each step on outer surface 111 is progressively
smaller from top to bottom. An external hollow cylindrical feature
is removed from the outside of inner sleeve member 100 at a shallow
depth. Successive external hollow cylindrical features are removed
at regular length and width intervals. Each successive feature
starts where the preceding feature stops. The geometric pattern of
removed external cylindrical features continues until space
restricts the addition of another internal cylindrical feature.
[0034] Inner sleeve member 100 further has an upper surface 112
with a coupling means 130 which may be formed by a plurality of
bores extending in an axial direction and spaced from one another
in a circumferential direction. Coupling means 130 non-rotatably
engages with the action portion of the torque input device.
[0035] Outer sleeve member 200 is an annular body and, as shown in
FIG. 3, formed as a sleeve. It has inner surface 210 with
cylindrical formation 220 which is rotatably engagable with an
outer surface 111 with cylindrical formation 121 of inner sleeve
member 100. Outer sleeve member 200 has an outer surface 211 with a
coupling means 230. Coupling means 230 is formed by a plurality of
outer spines extending in an axial direction and spaced from one
another in a circumferential direction. Coupling means 230
non-rotatably engages with inner spines of a reaction portion of
the torque input device.
[0036] Cylindrical formation 220 is shaped as a frustum of a
stepped cone which has a tapered or conical appearance from the top
down. Each step on inner surface 210 is progressively smaller from
top to bottom. An internal cylindrical feature is removed from the
inside of outer sleeve member 200 at a shallow depth. Successive
internal cylindrical features are removed at regular length and
width intervals. Each successive feature starts where the preceding
feature stops. The geometric pattern of removed internal
cylindrical features continues until space restricts the addition
of another internal cylindrical feature.
[0037] Stud 300 has a cylindrical shape with outer helical thread
means 320 for mating with inner helical thread means 120 of inner
sleeve 100. An end 312 of stud 300 has a coupling means 314 which
may be formed by a polygonal formation 330, which in this case is a
hexagon shape. Polygonal formation 330 allows for rotational
coupling with the torque input device.
[0038] Second coupling member 150 further has a lower surface 163
which rests on an upper surface of the joint. Lower surface 163 may
be substantially rough and may be made in many different ways, for
example by a plurality of ridges, ripples or teeth.
[0039] The stepped conical fastener geometry of apparatus 1 creates
tensile load in stud 300 by the mechanical sliding action through
the helical inclined plane between stud threads 320 and inner
sleeve member threads 120. The sliding helical thread action is
created by using the torque input device to apply rotation under
torque to inner sleeve member coupling means 130 while reacting the
torque on outer sleeve member external splines 230. As outer
surface 111 and inner surface 210 are substantially smooth, outer
sleeve member 200 remains static while inner sleeve member 200
rotates. The reaction element of the torque input device is
rotationally coupled with end 312 of stud 300 by coupling means
314. This prevents rotation of stud 300 and allows the relative
sliding action between inner sleeve member threads 120 and studs
threads 320. Stud translation occurs in proportion to the
resistance against such translation as the torque input device
continually applies torque to inner sleeve member 100 while
reacting on outer sleeve member external splines 230 and being
rotationally coupled with stud 300 by coupling means 314.
[0040] Inner sleeve member coupling means 130 may be formed by any
suitable geometry or used with other means or features for
rotationally coupling with the torque input device such as gear
teeth, hex, double hex, castellation or any other common geometry
that allows rotational coupling. One possible alternative is hex
geometry shown in FIG. 5 as 530.
[0041] Outer sleeve member coupling means 221 may be formed by any
suitable geometry or used with other means or features for
rotationally coupling with the torque input device such as gear
teeth, hex, double hex, castellation or any other common geometry
that allows rotational coupling. One possible alternative is hex
geometry shown in FIG. 6 as 621.
[0042] Note that the quantity, dimensions, geometries and intervals
of removed external (inner sleeve member 100) and internal (outer
sleeve member 200) cylindrical features may vary to optimize
characteristics of apparatus 1, such as, for example, stress
biasing, depending on the application.
[0043] FIG. 2 shows inner sleeve member 100 with four external
cylindrical features removed at regular length and width intervals.
FIG. 3 shows outer sleeve member 200 with four internal cylindrical
features removed at regular length and width intervals. As shown in
FIG. 7, varying the quantity, dimensions, geometries and intervals
from one removed external and internal cylindrical feature to the
next varies the nominal angles, step heights and step widths of an
outer surface 711 with a cylindrical formation 721 and an inner
surface 710 with a cylindrical formation 720. Alternatively, the
step length may be sized infinitely small to create a nearly smooth
taper. External portions of inner sleeve member 100 and internal
portion of outer sleeve member 200 may be removed in one step to
form smooth conical surfaces, respectively.
[0044] FIG. 8 shows an outer surface 811 with a cylindrical
formation 821 and an inner surface 810 with a cylindrical formation
820 with mating faces of varying vertical spacing, or step heights.
This allows movement on selective steps only as other steps are
loaded. Plastic deformation allows vertical movement therefore
strategically biasing stress distribution across each stepped face.
In other words, increased clearance or spacing between mating faces
of inner and outer sleeve members 100 and 200 allow for radial
expansion during loading.
[0045] FIG. 9 shows an outer surface 911 with a cylindrical
formation 921 and an inner surface 910 with a cylindrical formation
920 with mating faces of varying step face angles. This promotes
more evenly and controlled biasing stress distribution across the
steps. In other words, either or both inner and outer sleeve
members 100 and 200 may have stepped vertical surfaces with varying
pitch angles to bias stress to selective horizontal stepped
surfaces.
[0046] FIG. 10 shows outer sleeve member 200 having internal
features at bottom that couple with similar mating external
features added to stud 300. These may include splines, knurls, hex,
slots, double hex or other geometry. They allow axial translation
of stud 300 but couple rotational movement of outer sleeve member
200 and stud 300. Both coupling means 314 formed of polygonal
formation 330 and the necessity to couple this hex with the
reaction member of the torque input device are no longer necessary.
Internal spline 1040 and mating external spline 1041 form a spline
interface between outer sleeve member 200 and stud 300,
respectively.
[0047] In standard bolting industry terms, apparatus 1 includes a
nut (inner sleeve member 100) and a washer (outer sleeve member
200). The standard bolting flat surface nut and washer interface is
changed. The torque reaction point is moved upwards, as compared to
conventional three-piece fasteners. Apparatus of the present
invention utilize the concept of conventional three-piece
fasteners, which allows for surface conditioning of the outer
sleeve to prevent galling, leveraged with a conventional nut and
washer arrangement, which retains radial strain such that the inner
sleeve may be surface conditioned with minimal risk of
fracture.
[0048] Advantageously, the invention allows for an increased load
bearing surface area between the inner sleeve member, which is
clamped, and the outer sleeve members without increasing the
overall diameter of the apparatus; a three dimensional load bearing
surface area rather than a conventional two dimensional plane; more
efficiently and evenly distributed load stress distribution over
the load bearing surface area; higher torsion strength; and
apparatus with lower mass, dimensions and volume.
[0049] Referring to FIGS. 11-14 by way of example, this shows an
apparatus 1101 for torsionally coupling a threaded fastener 1110
and a torque input device 1102 in accordance with an embodiment of
the present invention. Apparatus 1101 has a first coupling member
1103 with a tapered external surface 1104 and a polygonal formation
1105; and a second coupling member 1113 having an inversely tapered
internal surface 1114 and a polygonal formation 1115 non-rotatably
engagable with tapered external surface 1104 of first coupling
member 1103.
[0050] In other words, apparatus 1101 torsionally couples torque
input device 1102 and threaded fastener 1110 of the kind having a
shank 1111 with a tapered axial bore 1112 at one end. Apparatus
1101 includes coupling member 1103 having inversely tapered
external surface 1104 non-rotatably engagable with tapered axial
bore 1112.
[0051] Discussion related to quantity, dimensions, geometries and
intervals of removed external (inner sleeve member 100) and
internal (outer sleeve member 200) cylindrical features of FIGS.
1-10 generally applies to the quantity, dimensions, geometries and
intervals of removed external (first coupling member 1103) and
internal (second sleeve member 1113) polygonal features of FIGS.
11-14. Note that the interface between inner and outer sleeve
members 100 and 200 is cylindrical and smooth thus allowing
relative rotation. Note, however, that the interface between first
and second coupling members is polygonal and angled thus no
relative rotation is possible.
[0052] A conical geometry for torsional coupling of a threaded
fastener and a torque output device yields a better load stress
distribution. The embodiment of FIGS. 11-14 introduces a low
profile coupling geometry that will allow a torsion-coupling
feature on the top of a stud to be formed internally. This
distributes stresses more evenly and therefore allows for a more
efficient packaging of the coupling features.
[0053] Generally, a stepped 12-point hole in the top surface of the
stud is used for torsion coupling with a three-piece mechanical
stud-tensioning device and/or an apparatus for use with the stud.
An internal 12-point feature is placed in the top of the stud at a
shallow depth. Successive 12-point features are progressively added
at smaller 12-point sizes each at shallow depths and each starting
where the preceding 12-point stopped. The pattern of decreasing
12-point geometry will decrease until space restricts the addition
of another 12 point. Advantageously, a shaft of the torque input
device with external matching features for each of the steps will
allow for evenly distributed stress distribution and high torsion
strength while decreasing the mass and volume of the studs.
[0054] As shown in FIGS. 16 and 17, varying the depth and size
change from one 12-point feature to the next will increase or
decrease the nominal angle of the conical shape these features
form. The 12-point feature can be substituted with any geometry
that will prevent rotation between the two parts, such as the hex
in FIG. 15. Additionally, the step depth can be sized infinitely
small to create a smooth taper. Mixed step sizes and geometries can
be used to optimize production of such a coupling.
[0055] Note that any type of suitable components, sizes and
materials of apparatus of the present invention may be used,
including: fastener categories, for example wood screws, machine
screws, thread cutting machine screws, sheet metal screws, self
drilling SMS, hex bolts, carriage bolts, lag bolts, socket screws,
set screws, j-bolts, shoulder bolts, sex screws, mating screws,
hanger bolts, etc.; head styles, for example flat, oval, pan,
truss, round, hex, hex washer, slotted hex washer, socket cap,
button, etc.; drive types, for example phillips and frearson,
slotted, combination, socket, hex, allen, square, torx, multiple
other geometries, etc.; nut types, for example hex, jam, cap,
acorn, flange, square, torque lock, slotted, castle, etc.; washer
types, for example flat, fender, finishing, square, dock, etc.; and
thread types, for example sharp V, American national, unified,
metric, square, ACME, whitworth standard, knuckle, buttress,
single, double, triple, double square, triple ACME, etc.
[0056] It will be understood that each of the elements described
above, or two or more together, may also find a useful application
in other types of constructions differing from the types described
above. The features disclosed in the foregoing description, or the
following claims, or the accompanying drawings, expressed in their
specific forms or in terms of a means for performing the disclosed
function, or a method or process for attaining the disclosed
result, as appropriate, may, separately, or in any combination of
such features, be utilized for realizing the invention in diverse
forms thereof.
[0057] While the invention has been illustrated and described as
embodied in a fluid operated tool, it is not intended to be limited
to the details shown, since various modifications and structural
changes may be made without departing in any way from the spirit of
the present invention.
[0058] Without further analysis, the foregoing will so fully reveal
the gist of the present invention that others can, by applying
current knowledge, readily adapt it for various applications
without omitting features that, from the standpoint of prior art,
fairly constitute essential characteristics of the generic or
specific aspects of this invention.
[0059] When used in this specification and claims, the terms
"tapered", "taperedly" and variations thereof mean that the
specified features, steps, quantities, dimensions, geometries and
intervals may, from one end to another, either gradually, suddenly,
step-wisely, and/or conically: be inconsistent, vary, narrow,
diminish, decrease, get smaller, thin out, etc.
[0060] When used in this specification and claims, the terms
"comprising", "including", "having" and variations thereof mean
that the specified features, steps or integers are included. The
terms are not to be interpreted to exclude the presence of other
features, steps or components.
* * * * *