Information
-
Patent Grant
-
6467547
-
Patent Number
6,467,547
-
Date Filed
Monday, December 11, 200023 years ago
-
Date Issued
Tuesday, October 22, 200221 years ago
-
Inventors
-
Original Assignees
-
Examiners
- Bagnell; David
- Gay; Jennifer H
Agents
- Moser, Patterson & Sheridan, L.L.P.
-
CPC
-
US Classifications
Field of Search
US
- 166 212
- 166 373
- 166 377
- 166 381
- 166 382
- 166 383
- 166 386
- 166 2426
- 166 208
-
International Classifications
-
Abstract
The present invention generally provides a running tool comprising a torque-dampening system. A first portion and a second portion of the running tool are operably related by a torsion interface. In one embodiment, the torsion interface includes a plurality of interlaced teeth disposed on the each of the first and second portions. During relative rotation of the first and second portions, the teeth engage and “ride up” on one another, thereby forcing the first and second portions in opposite axial directions. At least one of the portions houses a flow restrictor assembly adapted to restrict fluid flow from one region to another during the axial movement of the portions. Accordingly, the relative rotation between the portions is inhibited, or dampened.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates generally to running tools. More specifically, the invention relates to a running tool adapted to compensate for undesired torque in order to prevent premature release of a component secured to the running tool.
2. Background of the Invention
Running tools are used for various purposes during well drilling and completion operations. For example, a running tool is typically used to set a liner hanger in a well bore. The running tool is made up in the drill pipe or tubing string between the liner hanger and the drill pipe or tubing string running to the surface. In one aspect, the running tool serves as a link to transmit torque to the liner hanger to help place and secure the liner in the well bore. In addition, the tool also provides a conduit for fluids such as hydraulic fluids, cement and the like. Upon positioning of the liner hanger at a desired location in the well bore, the running tool is manipulated from the surface to effect release of the liner hanger from the running tool. The liner may then optionally be cemented into place in the well bore. In some cases, the cement is provided to the well bore before releasing the liner.
The application of torque to the drill string facilitates lowering the liner past obstructions formed in the well bore. For example, during drilling the drill bit often creates pockets in the surfaces of the well bore. While being lowered, the liner may move into the pockets. By rotating the liner, the liner is able to navigate through the pockets more easily.
In a typical drill pipe or tubing string, lengths of drill pipe or tubing are connected by tool joints using right-hand threads on the drill pipe. These joints are made up using right-hand torque and unscrewed or released using left-hand torque. Drilling is carried out by right-hand or clockwise rotation of the drill string to avoid breaking out or loosening the tool joints making up the pipe string. In the case of a mechanical release, left-hand torque is then applied o the drill string. In particular, the torque is sufficient to shear one or more shear screws located in the running tool. Subsequently, the liner may be detached from the running tool.
A problem occurs when the liner (or potentially even the running tool or drill string) engages an obstruction (e.g., a rock formation) that prevents continued clockwise rotation of the liner. As the surface actuator continues to provide torque to the drill string, the drill string is “wound up,” much like a rubber band or other elongated elastic member. Once the liner breaks free of the obstruction, the accumulated potential energy due to the winding up is converted into kinetic energy as the drill string unwinds by rotating in the clockwise direction. In some cases (where enough energy is available), the liner may over-travel the neutral drilling position. This has the effect of simulating a manual mechanical release because the running tool is now turning in a left-hand (counter-clockwise) direction relative to the liner. In the event the shear screws shear out, the running tool is prematurely released from the liner hanger.
Another problem with prior art methods and apparatus is balancing the need for sufficient strength of the shearing screws while still allowing them to shear out when necessary. Consider, for example, the case in which the liner hanger may be of relatively light weight. When the hanger is set and ready to be mechanically released, the applied left-hand torque may cause the hanger to rotate in tandem with the drill string, thereby inhibiting the release procedure.
Therefore, there exists a need for a running tool that compensates for over-travel of the tool to prevent prematurely releasing the tool from a liner hanger or other connected component.
SUMMARY OF THE INVENTION
The present invention is directed to a running tool for setting a liner or other tool down hole. The running tool generally comprises a torque-dampening system.
In one aspect, the invention provides a running tool for a well tool, comprising a first portion, a second portion and a torsion interface disposed therebetween. A torque-dampening system contacts the first portion and is adapted to inhibit the relative rotational movement between the first and second portions during an opposing linear displacement.
In another aspect, the invention a running tool comprising a torsion interface adapted to cause opposing linear displacement of a first and second portions upon their relative rotation. A tubular member is concentrically disposed within the first and second portions and the tubular member is slidably disposed relative to the first portion. A torque-dampening system is located between the tubular member and the first portion. When actuated in response to the opposing linear displacement of the first and second portions, the torque-dampening system inhibits the relative rotational movement between the first and second portions.
In another aspect, a mechanical release is provided to enable operation of a running tool without the assistance of hydraulic pressure and without conventional shearing screws, which are made to shear out during application of left-hand torque to the tool. The mechanical release assembly comprises a first sleeve and a second sleeve each carrying a plurality of intermeshed teeth (which do not necessarily contact one another). During application of left-hand torque, the teeth engage and ride up one another to linearly displace the first sleeve and a second sleeve. As a result, the first sleeve strokes up relative to a tubular member concentrically slidably disposed within the first sleeve. In response to the linear displacement of the sleeves, a torque-dampening system, located between a tubular member and the first sleeve, is actuated to inhibit the relative rotational movement between the sleeves. Upon a predetermined degree of rotation, the teeth disengage, rotate over one another and come to rest in a release position. Downward pressure is then applied to the tubular member, thereby shifting the tubular member down relative to the sleeves and causing the tool to disengage from a liner hanger coupled to a bottom portion of the tool.
In another aspect, a method for dampening rotation of a sleeve on a running tool is provided. The method comprises providing a first and second portion of a running tool, wherein a portion of the first portion is adapted to interface with a down hole tool. The rotation of the first portion is then restricted by actuating a fluid-actuated torque-dampening system operably connected to the first portion. In one embodiment, the first portion is operably connected to a second portion. The movement of the first portion is then restricted such that movement of the second portion is also restricted.
BRIEF DESCRIPTION OF THE DRAWINGS
A more particular description of the invention, briefly summarized above, may be had by reference to the embodiments thereof which are illustrated in the appended drawings. It is to be noted, however, that the appended drawings illustrate only typical embodiments of this invention and are therefore not to be considered limiting of its scope, for the invention may admit to other equally effective embodiments.
FIGS. 1A-C
is an elevation view of a running tool.
FIGS. 2-7
are partial side views a running tool illustrating operation of a torsion interface during application of torque.
FIGS. 8A-C
are side views partially in section of a running tool in a running-in position.
FIG. 9
is an elevation view of a bayonet.
FIG. 10
is a top cross-sectional view of the bayonet shown in FIG.
9
.
FIG. 11
is cross-sectional view of a torque sleeve.
FIG. 12
is a top cross-sectional view of the torque sleeve shown in FIG.
11
.
FIG. 13
a top cross-sectional view of the bayonet shown in
FIG. 9
disposed in the torque sleeve shown in FIG.
11
.
FIGS. 14-17
are a series of cross-sectional drawings of a running tool illustrating the operation of a torque-dampening system.
FIG. 18
is a side view partially in section of a running tool in a release position.
DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT
FIGS. 1A-C
is an elevation view of a running tool
100
according to one aspect of the invention. The running tool
100
is shown in an assembly position in which position the running tool
100
is ready to receive a liner hanger running profile. Once the setting sleeve or liner hanger is connected, the tool
100
is said to be in a running-in position. The running tool
100
can then be made up on a pipe string for releasably engaging the liner hanger in a well bore.
The running tool
100
generally includes a cylinder body
110
, a bottom connector
112
disposed at a lower end and an internally threaded top connector
114
. The bottom connector
112
supports a collet assembly
115
, which is connectable to a liner hanger (not shown), and the top connector
114
is connectable to a pipe string (also not shown). The lower portion of the running tool
100
(best seen in
FIG. 1C
) also includes components such as a castellation portion
117
for engaging and carrying a liner hanger and a dogs assembly
119
actuated to disengage from a liner hanger. These and other components are well known in the art and a detailed description is not necessary.
The cylinder body
110
includes a torque sleeve
116
and a clutch sleeve
118
. Both the torque sleeve
116
and the clutch sleeve
118
are concentrically disposed about a tubular member. Illustratively, the tubular member is formed from a bayonet
200
and a mandrel
232
which define a bore
208
. The torque sleeve
116
is rotatably disposed about the bayonet
200
and the mandrel
232
and secured from relative axial movement in one direction (e.g., downward toward the collet assembly
115
) by a retaining assembly
127
disposed on the mandrel
232
. Illustratively, the retaining assembly
127
comprises a split ring
129
secured by a snap ring
131
. The retaining assembly
127
acts as a support for a spring stop
133
that is rigidly secured to the torque sleeve
116
by a fastener
137
, such as a bolt. The spring stop
133
rotates freely over the retaining assembly
127
and because the torque sleeve
116
is not otherwise rigidly fixed, the torque sleeve
116
is permitted to rotate relative to the mandrel
232
. The spring stop
133
also provides a lower constraint for a spring
135
, which is constrained at an upper end by the bayonet
200
. The spring acts to bias the spring stop
133
toward the retaining assembly
127
. Thus, the spring stop
133
and the retaining assembly
127
often in mating abutment during operation of the tool
100
.
The upper end of the clutch sleeve
118
is concentrically slidably disposed over a lower portion
120
of the top connector
114
. Controlled axial (i.e. liner) movement of the clutch sleeve
118
relative to the top connector
114
is facilitated by the provision of a slot
122
and a key
124
. The slot
122
is an elongated opening formed at one end of the clutch sleeve
118
and having its length oriented along the axis of the running tool
100
. The key
124
is disposed within the slot
122
and is allowed to move freely through the length of the slot
122
. The key
124
is secured to the top connector
114
by screws
126
, thereby preventing relative rotational movement between the top connector
114
and clutch sleeve
118
.
The torque sleeve
116
and clutch sleeve
118
are operably related by a torsion interface
128
that allows a relative torque between the torque sleeve
116
and clutch sleeve
118
to produce relative axial movement between the torque sleeve
116
and clutch sleeve
118
. In a particular embodiment shown in
FIG. 1
, the torsion interface
128
comprises a plurality of intermeshed teeth
130
A and
130
B, or cogs, disposed on respective ends of the torque sleeve
116
and clutch sleeve
118
. In the presence of a relative torque between the torque sleeve
116
and clutch sleeve
118
, the teeth
130
engage with one another to provide axial thrust, thereby driving the clutch sleeve
118
. Although in the embodiment shown in
FIG. 1
the clutch sleeve
118
is axially driven, in other embodiments the torque sleeve
116
may be the axially driven member.
In the assembly position, the teeth
130
A-B are separated by a gap
132
. The gap
132
allows clearance for the torque sleeve
116
to ride up a mandrel
232
(shown, for example, in FIG.
8
and described below) when the liner hanger is being coupled to the running tool
100
. Once the liner hanger is attached to the tool
100
(i.e., the tool
100
is in the running-in position), the gap
132
is substantially narrower and, in one embodiment, eliminated.
The operation of the torsion interface
128
is described with reference to FIG.
2
through FIG.
7
. In
FIG. 2
, the running tool
100
is shown in an initial running-in position. This position is maintained during normal drilling operation of the running tool
100
, i.e. during application of right hand torque causing synchronous rotation of the torque sleeve
116
and clutch sleeve
118
. In such a position, the hydraulic cylinder teeth
130
A and the torque sleeve teeth
130
B are separated from one another by a gap
136
. In a particular embodiment, the gap
136
is merely provided to accommodate a desired degree of axial tolerance (e.g., 0.5 inches) necessary to disengage the tool
100
from a liner hanger. During operation, the gap
136
may be periodically closed when the torque sleeve
116
and clutch sleeve
118
collapse toward one another (e.g., due to a force acting on each end of the tool
100
).
FIG. 3
shows the effect of applying a right-hand torque to the torque sleeve
116
while the clutch sleeve
118
is held stationary. This is equivalent to a left-hand torque applied to the clutch sleeve
118
while the torque sleeve
116
is held stationary. In either case, the clutch sleeve
118
and the torque sleeve
116
rotate relative to one another causing the teeth
130
to engage. The teeth
130
define inclined surfaces
138
, or flanks, which, when rotated against one another, produce an opposing force. As a result, the clutch sleeve
118
is axially actuated away from the torque sleeve
116
as shown by arrow
140
. As shown in
FIGS. 3 and 4
, during continued application of left-hand torque, the gap
136
′ between the torque sleeve
116
and the clutch sleeve
118
is widened as the respective inclined surfaces
138
continue to slide over one another.
If the torque ceases prior to the teeth
130
disengaging and rotating past one another, then the torque sleeve
116
and the clutch sleeve
118
return to the neutral drilling position (shown in FIG.
2
). If, however, the torque continues, then the teeth
130
rotate past one another as shown in FIG.
5
and FIG.
6
. Further, as shown in
FIG. 6
, the torque sleeve
116
and the clutch sleeve
118
begin to collapse toward one another due to the relative axial movement of the clutch sleeve
118
in the direction indicated by arrow
144
.
FIG. 7
shows the running tool
100
in a terminal position, or release position, after the torque sleeve
116
and the clutch sleeve
118
have been rotated one tooth
130
over and are fully collapsed (i.e., the gap
136
is closed). In the terminal position, the liner (not shown) is released from the running tool
100
and the running tool
100
may then be extracted from the well bore.
In a particular application, the torque referenced above may be caused by the over-rotation of the torque sleeve
116
relative to the clutch sleeve
1118
. Such over-rotation may occur after the torque sleeve
116
is freed from an impediment to rotation (e.g., a sloughed in formation). The potential energy stored in the drill string above the running tool
100
and in the liner below the tool
100
while the tool
100
was inhibited from rotation is released as rotational kinetic energy once the tool is freed from the obstruction to rotation. If enough energy is available, the torque sleeve
116
may continue rotating (in the direction shown by arrow
142
) beyond the neutral drilling position causing the teeth
130
to engage. In another application, the relative rotation between the torque sleeve
116
and the clutch sleeve
118
is the result of a purposeful mechanical release facilitated by the surface application of a left-hand torque to the running tool while the torque sleeve
116
is held stationary (e.g., by a liner resting in the wellbore).
The foregoing embodiments of the torsion interface
128
are merely illustrative. In general, the torsion interface
128
is any assembly, device, or structural formation that allows a relative torque between the torque sleeve
116
and clutch sleeve
118
to produce relative axial movement between the torque sleeve
116
and clutch sleeve
118
Thus, in another embodiment, the torsion interface
128
comprises threads formed on a lower inner surface of the clutch sleeve
118
. Mating counter-threads formed on the upper outer surface of the torque sleeve
116
may be fitted in to the threads of the clutch sleeve
118
. Upon relative rotation of the sleeves
116
,
118
the clutch sleeve is stroked upward. Unthreaded surfaces between the threaded portion of each sleeve allow the threads to disengage and sleeves to collapse inward toward one another. Persons skilled in art will recognize other embodiments.
It is understood that the terms “right-hand torque” and “left-hand torque” are relative terms and that the invention is not limited by the use of such terms. Accordingly, in other embodiments, the drilling torque may be left-hand torque and the applied torque to mechanically release running tool
100
from a liner, or other component being carried by the tool, may be right-hand torque.
During the relative rotation of the sleeves
116
,
118
shown in
FIGS. 3-4
, the clutch sleeve
118
experiences a torque dampening effect that resists the relative rotation. Accordingly, the relative linear movement of the clutch sleeve
118
and the torque sleeve
116
away from each other is restrained or resisted. Such a torque dampening effect is caused by the provision of a torque dampening system housed within the running tool
100
. The torque dampening system and other features of the tool
100
will now be described with reference to
FIGS. 8-13
.
FIGS. 8A-C
shows a partial cutaway of an upper portion of the running tool
100
in a running-in position.
FIGS. 8A-C
shows a bayonet
200
axially disposed along the length of the running tool
100
. The bayonet
200
is a generally tubular member defining a central bore
208
through which a fluid (e.g., hydraulic fluid) may be flowed. The bayonet
200
is secured at its upper end to the lower portion
120
of the top connector
114
by fasteners, such as torque screws
202
. Accordingly, the bayonet
200
and the top connector
114
are constrained against any relative axial or rotational movement. Further, an
0
-ring seal
204
is disposed between the inner diameter of the lower portion
120
and outer diameter of the bayonet
200
in order to prevent fluid flow from a chamber
210
.
As shown in
FIG. 8C
, a tip
230
of the bayonet
200
is located at an upper end of the torque sleeve
116
. The tip
230
provides a diametrically enlarged opening to receive a portion of a mandrel
232
. The bayonet
200
and the mandrel
232
are secured to one another by a threaded interface
231
and a set screw
233
. Together, the bayonet
200
and the mandrel
232
form a tubular member having the bore
208
axially disposed therein. Although described herein as two separate members, the bayonet
200
and the mandrel
232
may be integrally formed of a single piece of material or formed as two materials and permanently fixed together, e.g., by welding.
The mandrel
232
abuts a ledge
234
formed on an inner surface of the bayonet
200
, thereby preventing the mandrel
232
from sliding freely beyond a predetermined position relative to the bayonet
200
. In addition, the ledge
234
ensures that the axial movement of the bayonet
200
toward the bottom connector
112
is transferred through the mandrel
232
. This relationship is needed during the mechanical release of the liner hanger (not shown) from the running tool
100
during which a downward force is applied to the bayonet
200
.
The bayonet
200
also carries a plurality of ribs
236
on an outer surface which are adapted to limit the relative movement between the bayonet
200
and the torque sleeve
116
within a predetermined allowance. The ribs
236
and additional features of the bayonet
200
will be described with brief reference to FIG.
9
and FIG.
10
.
FIG.
9
and
FIG. 10
show an elevation review and a bottom view, respectively, of the bayonet
200
. The ribs
236
are annular sections circumferentially disposed on the bayonet. Each rib
236
defines an upper surface
239
and a lower surface
240
adapted to engage corresponding surfaces on the torque sleeve
116
, as will be discussed below with reference to FIG.
8
. In the particular embodiment shown, the ribs
236
comprise two sets of four on opposite sides of the bayonet
200
. Although eight (8) ribs
236
are shown, any number may be used.
Adjacent to each set of ribs
236
is a spline or stop member
238
. The stop member
238
is an elongated protrusion extending axially along the length of the bayonet
200
. The stop members
238
are adapted to limit the degree of rotation allowed by the bayonet
200
while seated in the torque sleeve
116
, as will be discussed below.
Referring now to FIG.
11
and
FIG. 12
a cross sectional view and a top view of the torque sleeve
116
is shown. Fingers
244
formed on an inner surface of the torque sleeve
116
define recesses
242
for containing the ribs
236
. The fingers
244
are structurally similar to the ribs
236
. That is, the fingers
244
comprise two sets of axially equidistant annular sections wherein each set of fingers
244
is disposed on opposite sides of the torque sleeve
116
in facing relationship with the other set. Further, the radial space between each set is dimensioned to accommodate the ribs
236
and the stop member
238
of the bayonet
200
. Accordingly, when the ribs
236
and the stop member
238
are rotationally offset from the fingers
236
, the bayonet
200
may be inserted into the torque sleeve
116
. This position is illustrated in
FIG. 13
which shows a top view of the bayonet
200
and the torque sleeve
116
. When the bayonet
200
is inserted to a point at which the ribs
236
are aligned with the recesses
242
, the bayonet
200
is rotated so that the ribs
236
move into the recesses
242
. The bayonet continues rotation until the stop member
238
engages the fingers
244
. The bayonet
200
is now in a “locked” position relative to the torque sleeve
116
.
Referring back to
FIG. 8
(and particularly to FIG.
8
C), the bayonet
200
is shown in the “locked” position. Accordingly, the ribs
236
are disposed in the recesses
242
defined by fingers
244
of the torque sleeve
116
. As shown, the recesses
242
have a width greater than the ribs
236
to allow some relative axial movement between the bayonet
200
and the torque sleeve
116
. Initially, in the assembly position, the upper surfaces
239
of the ribs
236
abut the fingers
244
. However, upon attaching a liner hanger, the torque sleeve
116
rides up toward the clutch sleeve
118
while the bayonet
200
remains stationary. Thus, in the compressive running-in position, the lower surfaces
240
of the ribs
236
abut the fingers
244
as shown in FIG.
8
C.
As shown in
FIG. 8A
, the clutch sleeve
118
is concentrically slidably disposed over the lower portion
120
of the top connector
114
. The inner surface of the clutch sleeve
118
carries a seal
211
which prevents fluid flow from the chamber
210
and is also adapted to tolerate relative axial movement between the lower portion
120
and the clutch sleeve
118
. The stroke of the clutch sleeve
118
is delimited by a shoulder
212
formed on the top connector
114
and that engages an upper surface
214
of the clutch sleeve
118
. In a particular embodiment, the farthest distance D
1
between the shoulder
212
and the upper surface
214
is about 2 inches. However, more generally, the distance D
1
may be any length as determined by a particular application. It should be noted that the slot
122
is also dimensioned to allow the key
124
to travel a distance substantially equal to D
1
within the slot
122
. Thus, either or both of the slot
122
and the shoulder
212
may act to define the clutch sleeve stroke.
In order to maintain the maximum distance D
1
between the shoulder
212
and the upper surface
214
, a return coil
220
is provided. The return coil
220
acts to motivate top connector
114
(and hence the bayonet
200
) and the clutch sleeve
118
in opposite directions. In a particular embodiment, return coil
220
is disposed in the annular upper chamber
210
defined by the inner diameter of the clutch sleeve
118
and the outer diameter of the bayonet
200
. The chamber
210
is sealed at either end by the lower portion
120
of the top connector
114
and a torque-dampening system
260
that also act to compress the return coil
220
at its ends.
The stroke speed of the clutch sleeve
118
relative to the lower portion
120
is controlled by the torque-dampening system
260
. The torque-dampening system
260
(also referred to herein as “the system
260
”) is best described with reference to FIG.
8
B. The system
260
generally comprises a sealing bushing
262
containing flow restrictors. The sealing bushing
262
is a generally annular member (in the form of a collar) and is disposed between the inner diameter of the clutch sleeve
118
and the outer diameter of the bayonet
200
. The sealing bushing
262
abuts a rim
265
formed on in inner surface of the clutch sleeve
118
which provides a biasing surface to drive the sealing bushing
262
axially upward (toward the top connector
114
) during the up-stroke of the clutch sleeve
118
. In another embodiment, the sealing bushing
262
may be secured to the hydraulic cylinder
118
by fasteners such as screws. In still another embodiment, the sealing bushing
262
and the clutch sleeve
118
are integral components. For example, the sealing bushing
262
and the clutch sleeve
118
may be formed of a single piece of material. More generally, the sealing bushing
262
is fixedly disposed relative to the clutch sleeve
118
so that the sealing bushing
262
is carried by the clutch sleeve
118
during its up-stroke.
In an initial position (as shown in FIG.
8
), the sealing bushing
262
also abuts a split ring
268
secured to the bayonet
200
with a retainer spring
270
. The split ring
268
prevents a balance piston
310
(described below) from riding up too far on the bayonet
200
. In addition, the split ring
268
restricts the travel of the sealing bushing
262
relative to the bayonet
200
.
The sealing bushing
262
provides at least one fluid passageway to allow fluid flow from the upper chamber
210
to a lower chamber
266
. In a particular embodiment, one such fluid passageway is defined by an orifice
272
and a cavity
274
in fluid communication with one another. The cavity
274
is defined by sealed at an upper end by a keeper
276
which also defines a portion of a lower buttressing surface to the return coil
220
. Fluid flow over and around the sealing bushing
262
is prevented by O-rings
263
A-B disposed between the sealing bushing
262
and the clutch sleeve
118
and between the sealing bushing
262
and the bayonet
200
, respectively.
In order to control the fluid flow between the chamber
210
and chamber
266
via the orifice
272
and the cavity
274
, a flow restictor is housed in the sealing bushing
262
. In one embodiment, the flow restrictor comprises a restrictor member disposed in the orifice
272
and adapted to provide impedance to fluid flow from the chamber
210
to the lower chamber
266
. Illustratively, the impedance is achieved by a bypass pin
264
having a tortuous fluid flow path
278
formed on its outer surface. The path is narrow, shallow and labyrinthine so that fluid flowing therethrough experiences a substantial pressure drop.
It should be noted that the above-described bypass pin
264
is merely illustrative. More generally, flow impedance may be achieved by any means adapted to slow the flow of fluid between the chambers
210
,
266
. For example, in another embodiment, the by-pass pin
264
may be a fluid permeable member, such as a porous filter. In yet another embodiment, flow impedance is accomplished by reducing the diameter of the orifice
272
, thereby eliminating the need for a bypass pin or other member disposed within the orifice
272
. Other embodiments will be readily recognized by those skilled in the art.
As shown in
FIG. 8B
, the cavity
274
contains a sintered metal filter
280
. The filter
280
is biased against a surface of the sealing bushing
262
(and downward toward the bypass pin
264
) by a spring
282
. The filter
280
acts to prevent contaminants from plugging the bypass pin
264
.
The sealing bushing
262
also houses a check valve assembly
290
. The check valve assembly
290
includes a blocking member
292
(e.g., a ball) biased downwardly against a seating surface of the sealing bushing
262
by a spring
294
. The spring
294
is restrained at its upper end by a retainer
296
that forms an outlet
298
. In its initial position, the blocking member
292
blocks an inlet
300
that is fluidly connected at its lower end to the lower chamber
266
. This position (i.e., “closed position”) is maintained so long as the pressure in the chamber
210
is greater than or equal to the pressure in the lower chamber
266
. Once the pressure in the lower chamber
266
increases beyond the pressure in the chamber
210
, the blocking member
292
is biased upwardly toward the chamber
210
and disengages from the seating surface of the sealing bushing
262
. The check valve assembly
290
is then said to be in a “open position,” and fluid is permitted to flow freely from the lower chamber
266
to the upper chamber
210
.
In one embodiment, the running tool
100
also includes a balance piston
310
adapted to compensate for fluid expansion and pressures. As can be seen in
FIG. 8B
, the balance piston
310
is an annular member slidably disposed between the inner diameter of the clutch sleeve
118
and the outer diameter of the bayonet
200
. The piston is provided a range of axial movement between the split ring
268
and an annular ledge
311
formed on the bayonet
200
. O-rings
312
disposed on the inner and outer surfaces of the balance piston
310
maintain annular seals with respect to the bayonet
200
and the clutch sleeve
118
, respectively.
An upper end of the balance piston
310
defines an axial channel
314
that is radially traversed by a bore
316
. The bore
316
allows fluid communication between the lower chamber
266
and an interior annular region
315
formed between the bayonet
200
and the balance piston
310
. The axial channel
314
terminates at a lower end in a relatively diametrically enlarged volume
317
housing a check valve assembly
320
. The check valve assembly
320
generally comprises a grooved check valve member
322
, a valve seat
324
, a valve retainer
326
, and a spring
328
. The spring
328
is disposed between the valve retainer
326
and the check valve member
322
and urges the check valve member
322
upwardly toward the valve seat
324
. A tip
330
of the check valve member
322
is conformed to be received in a conduit
332
of the valve seat
324
, thereby blocking fluid flow through the conduit
332
.
During operation of the running tool
100
, a pressure gradient between the interior spaces of the tool and the external environment may occur (e.g., due to fluid expansion). For example, the ambient pressure (i.e., the pressure in the well bore) may become greater than the pressure in the lower chamber
266
. In response, the balance piston
310
is urged upwards toward the chamber
266
. Accordingly, the fluid in the chambers
210
,
266
is compressed until the interior and exterior pressure conditions are equalized.
In the event of a pressure gradient increasing from the well bore to the lower chamber
266
(i.e., the pressure is relatively greater in the chamber
266
), the balance piston
310
is urged downward toward the ledge
311
, thereby relieving the pressure in the chamber
266
. If, when the piston
310
engages the ledge
311
, a sufficient pressure gradient still exists, the check valve member
322
may be actuated to further relieve the pressure gradient. Specifically, the fluid pressure in the axial channel
314
and the conduit
332
forces the tip
330
out of the conduit
332
, against the opposing bias of the spring
328
. The fluid then flows over grooves
336
formed on the outer surface of the check valve member
322
and out of the volume
317
via an outlet
338
formed in the valve retainer
326
. The fluid may then flow through the annular space between the clutch sleeve
118
and the bayonet
200
and ultimately into an external region (i.e., the well bore) through the gap
136
formed between the teeth
130
or through any other opening formed in the tool
100
.
The operation of the running tool
100
will now be described in more detail in a right hand rotation run-in application and a subsequent release procedure. The operation of the torque-dampening system
260
and the check valve assembly
290
is described with reference to
FIGS. 14-18
. Reference is also made back to
FIGS. 2-7
to illustrate the corresponding position of the torsion interface
128
.
In operation, the running tool is made up and run into the well bore hole while maintaining right hand rotation on the pipe string. As described above, the tool
100
(or more likely, the liner being carried by the tool
100
) will occasionally become lodged against an obstruction, thereby preventing rotation. When the tool
100
is subsequently dislodged, the liner being carried by the tool
100
may over-rotate, thereby simulating a left-hand release operation in which the clutch sleeve
118
and the torque sleeve
116
rotate with respect to one another. In the event of over-rotation, the torque-dampening system
260
and, subsequently, the check valve assembly
290
, are engaged.
FIG. 14
shows the torque-dampening system
260
in an initial position, i.e., prior to any g relative rotation between the clutch sleeve
118
and the torque sleeve
116
. The corresponding position of the torsion interface
128
is shown in FIG.
2
. Upon the left-hand rotation of the clutch sleeve
118
relative to the torque sleeve
116
, the teeth
130
A of the clutch sleeve
118
engage with, and begin to “ride up” on, the teeth
130
B of the torque sleeve
116
, as shown in FIG.
3
. Accordingly, the clutch sleeve
118
strokes up relative to the bayonet
200
and carries the torque-dampening system
260
as shown in FIG.
15
. During the up-stroke, fluid from the upper chamber
210
is compressed and is forced through the tortuous path
278
of the bypass pin
264
. The resulting impedance provided by the bypass pin
264
works to resist the up-stroke and slows the upward travel of the clutch sleeve
118
.
During continued relative rotation of the clutch sleeve
118
and the torque sleeve
116
(shown in FIG.
4
), the torque-dampening system
260
clears a plurality of undercuts
350
formed in the outer surface of the bayonet
200
, as shown in FIG.
16
. At this point, fluid is no longer restricted to traveling through the bypass pin
264
and may instead flow around the sealing bushing
262
via the undercuts
350
. Such an embodiment substantially eliminates the dampening provided by the torque-dampening system
260
at a predetermined stage during the up-stroke. This effect may be desirable in order to avoid excessive load being placed on the teeth
130
which may result in their being damaged.
If the left-hand torque ceases before the teeth
130
disengage, the tool
100
will reset to the initial position shown in FIG.
14
and continue its descent into the well bore. If over-rotation is experienced again, the steps above are repeated. In a particular embodiment, the tool may experience left-hand torque of about 1900 ft-lb for a period of time of about 150 seconds before the teeth
130
disengage. However, persons skilled in the art will recognize that the tool
100
can be adapted for other torque and time conditions according to application.
When the running tool and liner hanger have reached the desired depth, the liner may be released from the tool
100
. In the case of a hydraulic release, a hydraulic fluid is pumped into the pipe string or tubing string behind a plug, such as a ball. Hydraulic fluid flows from the pipe or tubing string and into the bore
208
. As best seen in
FIG. 1C
, the fluid is flowed through ports
121
disposed at a lower end of the tool
100
. With increasing pressure a shear screw
125
securing a hydraulic cylinder
123
is sheared, and the hydraulic cylinder
123
is actuated upwards. The hydraulic cylinder
123
is connected to the collet
115
which is pulled back to release the liner hanger. A locking dog assembly
119
may be actuated to secure the collet
115
in a retracted position.
However, should the inlets to the source of hydraulic fluid become clogged or should hydraulic fluid otherwise be prevented from operating the releasing mechanisms of the tool
100
, a mechanical release procedure is used to advantage. In particular, a left-hand torque is applied to the drill string, and hence, to the top connector
114
and bayonet
200
, while the torque sleeve
116
is held stationary by the liner. The left-hand torque effects relative rotation between the torque sleeve
116
and the clutch sleeve
118
, thereby actuating the torque-dampening system
260
and, subsequently, the check valve assembly
290
in the manner described above. That is, the torque-dampening system
260
and the check valve assembly
290
respond in the same manner as when the tool experiences over-rotation. However, rather than returning to an initial position (shown in FIG.
14
), the continued application of left-hand torque causes the teeth
130
to disengage and rotate past one another as shown in FIG.
5
. The clutch sleeve
118
then begins a down-stroke under the bias of the return coil
220
as shown in FIG.
6
. In addition, the check valve assembly
290
is opened to allow fluid flow from the lower chamber
266
to the upper chamber
210
as shown in FIG.
17
. The running tool
100
then proceeds to the terminal/release position shown in
FIGS. 7 and 18
. Note that the bayonet
200
has “dropped down” into a release position. Specifically, the ribs
236
have cleared the corresponding fingers
244
and the stop member
238
(not shown) has rotated away from the set of the fingers
244
contacted by the stop member
238
in the initial “locked” position. The stop member
238
now abuts the other set of fingers
244
to prevent further left-hand rotation of the bayonet
200
. In this position, a force applied to the top connector
114
moves the bayonet
200
and the mandrel
232
downward into the release position, thereby forcing the bottom connector
112
down relative to the collet
115
which carries the liner. As a result, the liner is disconnected.
In one embodiment, before weight is applied to the running tool
100
, the tool
100
may be reset after disengaging from a liner. Specifically, while in tension the bayonet
200
is rotated to the right, thereby reversing the torque-dampening system to the running position.
The foregoing embodiments are merely illustrative and persons skilled in the art will recognize other embodiments. In particular, the invention contemplates numerous embodiments of the torque-dampening system
260
. For example, the torque-dampening system may be located in another position in the tool
100
, e.g., between the torque sleeve
116
and the mandrel. In some embodiments, the provision of the torque-dampening system between the torque sleeve
116
and the mandrel may eliminate the need for the axially sliding clutch sleeve
118
. In another embodiment, the torque-dampening system may be actuated by rotational, rather than linear, movement. In another embodiment, the torque-dampening system may be mechanically actuated rather than fluidly actuated. For example, the torque-dampening system may comprise a coil (spring), such as coil
220
, without the use of the sealing bushing
262
and associated flow restrictor assembly. In still another embodiment, the torque-dampening system may comprise elastic members connecting the clutch sleeve
118
and the torque sleeve
116
, thereby inhibiting relative axial movement away from one another. These and other embodiments will be apparent to those skilled in the art.
While the foregoing is directed to preferred embodiments of the present invention, other and further embodiments of the invention may be devised without departing from the basic scope thereof. The scope of the invention is determined by the claims which follow.
Claims
- 1. A running tool for a well tool, comprising:(a) a first portion, a second portion and a torsion interface disposed therebetween; and (b) a torque-dampening system contacting the first portion and adapted to inhibit relative rotational movement between the first and second portions during an opposing linear displacement caused by the torsion interface upon relative rotation of the first and second portions.
- 2. The running tool of claim 1, wherein the well tool is a liner hanger.
- 3. The running tool of claim 1, wherein the torque-dampening system abuts a biasing surface formed on an inner surface of the first portion, the biasing surface adapted to urge the torque-dampening system in a linear direction during the opposing linear displacement of the first and second portions.
- 4. The running tool of claim 1, wherein the torque-dampening system is disposed in an annular member concentrically disposed within the first portion.
- 5. The running tool of claim 1, further comprising a tubular member concentrically disposed within the first and second portions, wherein the tubular member is slidably disposed relative to the first portion.
- 6. The running tool of claim 5, further comprising a retaining member secured to the tubular member and slidably disposed in the first portion, wherein the retaining member allows relative axial movement between the first portion and the tubular member while restricting relative rotational movement.
- 7. The running tool of claim 5, wherein the torque-dampening system is slidably disposed relative to the tubular member and fixedly disposed relative the first portion.
- 8. The running tool of claim 5, wherein the torque-dampening system is disposed in an annular member slidably disposed relative to the tubular member and fixedly disposed relative the first portion.
- 9. The running tool of claim 1, wherein the torque-dampening system comprises a flow restrictor.
- 10. The running tool of claim 9, wherein the flow restrictor comprises a restrictor member having a fluid flow path formed on an outer surface.
- 11. The running tool of claim 9, wherein the flow restrictor comprises a bypass pin having a tortuous fluid flow path formed on an outer surface.
- 12. The running tool of claim 9, wherein the flow restrictor is disposed between a first chamber and a second chamber formed between the first portion and a tubular member slidably concentrically disposed within the first portion, and wherein the flow restrictor allows fluid communication between the first and second chambers.
- 13. The running tool of claim 12, further comprising a balance piston disposed between the first portion and the tubular member, wherein the balance piston comprises a check valve assembly that responds to reduce pressure gradients between the second chamber and ambient conditions.
- 14. The running tool of claim 12, further comprising a return coil disposed in the first chamber and engaging the torque-dampening system.
- 15. The running tool of claim 12, wherein the torque-dampening system is disposed in an annular member slidably disposed about the tubular member and positioned to separate the first and second chambers.
- 16. The running tool of claim 15, further comprising a check valve assembly disposed in the annular member, wherein the check valve assembly is adapted to allow fluid flow only from the second chamber to the first chamber.
- 17. The running tool of claim 1, further comprising a liner release assembly disposed at a lower end of the second portion and selectively actuated when the torsion interface is rotated into a mechanical release position.
- 18. The running tool of claim 17, further comprising:a bayonet concentrically disposed within the first portion and the second portion; a first set of locking members disposed on an outer surface of the bayonet; a second set of locking members disposed on an inner surface of the second portion, wherein the first set and second set of locking members are selectively engaged to prevent relative sliding movement between the bayonet and the second portion and are selectively disengaged when the portion interface is rotated into the mechanical release position to allow relative sliding movement between the bayonet and the second portion.
- 19. A running tool, comprising:(a) a first sleeve and a second sleeve forming a torsion interface therebetween, wherein the torsion interface is adapted to cause opposing linear displacement of the first and second sleeves upon relative rotation of the first and second sleeves; (b) a tubular member concentrically disposed within the first and second sleeves, and wherein the tubular member is slidably disposed relative to the first sleeve; and (c) a torque-dampening system disposed between the tubular member and the first sleeve and actuated in response to the opposing linear displacement; the torque-dampening system comprising; (i) an annular member slidably disposed about the tubular member and contacting the first sleeve, wherein the annular member is positioned to separate a first chamber and a second chamber; and (ii) a flow restrictor disposed in the annular member and adapted to allow fluid communication between the first and second chambers.
- 20. The running tool of claim 19, further comprising a valve assembly adapted to allow flow only from the second chamber to the first chamber.
- 21. The running tool of claim 19, wherein the annular member abuts a biasing surface formed on an inner surface of the first sleeve, the biasing surface adapted to urge the torque-dampening system in a linear direction during the opposing linear displacement of the first and second sleeves.
- 22. The running tool of claim 19, further comprising a return biasing member disposed in a space between the first sleeve and the tubular member.
- 23. The running tool of claim 19, wherein the return biasing member comprises a coil annularly disposed about the tubular member.
- 24. The running tool of claim 19, wherein the flow restrictor comprises a restrictor member having a fluid flow path formed on an outer surface to allow fluid communication between the first and second chambers.
- 25. The running tool of claim 19, wherein the flow restrictor comprises a bypass pin having a tortuous fluid flow path formed on an outer surface to allow fluid communication between the first and second chambers.
- 26. The running tool of claim 25, further comprising a balance piston disposed between the first sleeve and the tubular member, wherein the balance piston comprises a check valve assembly that responds to reduce pressure gradients between the second chamber and ambient conditions.
- 27. The running tool of claim 25, further comprising a return coil disposed in the first chamber and engaging the torque-dampening system.
- 28. A running tool comprising:(a) a first sleeve defining a first plurality of teeth at one end of the first sleeve; (b) a second sleeve defining a second plurality of teeth at one end of the second sleeve, wherein the first plurality of teeth and the second plurality of teeth are intermeshed and cause an opposing linear displacement of the first sleeve and second sleeve upon relative rotation between the sleeves; (c) a tubular member comprising a bottom connector and a top connector, at least partly disposed within the first and second sleeves; and wherein at least a portion of the tubular member is slidably disposed relative to the first sleeve; and (d) a torque-dampening system disposed between the tubular member and the first portion and actuated in response to the opposing linear displacement; the dampening system comprising: (i) an annular member slidably disposed relative to the tubular member and carried by the first portion in at least a first direction away from the second sleeve during the opposing linear displacement; (ii) a flow restrictor disposed in the annular member and adapted to allow fluid communication between a first chamber and a second chamber formed between the tubular member and the first sleeve and separated by the annular member; (iii) a first valve assembly adapted to allow flow only from the second chamber to the first chamber; and (iv) a balance piston disposed between the first sleeve and the tubular member, wherein the balance piston comprises a second valve assembly that responds to reduce pressure gradients between the second chamber and ambient conditions; and (e) a return biasing member disposed in the first chamber and abutting the torque-dampening system at one end and abutting the top connector at a second end.
- 29. The running tool of claim 28, wherein the tubular member comprises a bayonet and a mandrel.
- 30. The running tool of claim 28, wherein the tubular member comprises a ribbed portion formed on an outer surface and adapted to be rotated into a mating ribbed portion formed on an inner surface of the second sleeve.
- 31. The running tool of claim 28, wherein the flow restrictor comprises a restrictor member having a fluid flow path formed on an outer surface.
- 32. The running tool of claim 28, wherein the flow restrictor comprises a restrictor member having a tortuous fluid flow path formed on an outer surface to allow fluid communication between the first and second chambers.
- 33. The running tool of claim 28, further comprising a retaining member secured to the tubular member and slidably disposed in the first sleeve, wherein the retaining member allows relative axial movement between the first sleeve and the tubular member while restricting relative rotational movement.
- 34. The running tool of claim 28, wherein the return biasing member is a coil.
- 35. A liner hanger running tool, comprising:(a) a tubular member, (b) a top connecting member disposed at one end of the tubular member and adapted to be connected to a tubular string; (c) a bottom connecting member disposed at another end of the tubular member and adapted to be received by a liner hanger; (d) a sleeve disposed about the tubular member and comprising at least a portion rotatably disposed relative to the tubular member, (e) a torque-dampening system disposed between the tubular member and the sleeve, wherein the torque-dampening system restricts relative rotation between the at least the portion and the tubular member.
- 36. The running tool of claim 35, wherein the tubular member is axially slidably disposed relative to another portion of the sleeve.
- 37. The running tool of claim 35, wherein the sleeve comprises castellations formed at a lower end thereof.
- 38. The running tool of claim 35, wherein the tubular member comprises a mandrel and a bayonet each carrying a plurality of ribs intermeshed with one another.
- 39. The running tool of claim 35, wherein the torque-dampening system comprises a flow restrictor.
- 40. The running tool of claim 35, wherein the sleeve comprises a first portion and a second portion defining a torsion interface adapted to cause an opposing linear displacement of the first and second portions upon relative rotation of the first and second portions.
- 41. The running tool of claim 40, wherein the torque-dampening system abuts a biasing surface formed on an inner surface of the first portion, the biasing surface adapted to urge the torque-dampening system in a linear direction during the opposing linear displacement of the first portion and the second portion.
- 42. The running tool of claim 40, further comprising a retaining member secured to the tubular member and slidably disposed in the first portion, wherein the retaining member allows relative axial movement between the first portion and the tubular member while restricting relative rotational movement therebetween.
- 43. The running tool of claim 40, wherein the torque-dampening system is slidably disposed relative to the tubular member and fixedly disposed relative the first portion.
- 44. The running tool of claim 40, wherein the torque-dampening system comprises a flow restrictor disposed between a first chamber and a second chamber formed between the first portion and the tubular member, and wherein the flow restrictor allows fluid communication between the first and second chambers.
- 45. A method for dampening rotation of a first portion relative to a second portion on a running tool, wherein the first portion is adapted to interface with a down hole tool, the method comprising:rotating the first portion relative to the second portion; and restricting the rotation of the first portion relative to the second portion by actuating a fluid-actuated torque-dampening system operably connected to the first portion.
- 46. The method of claim 45, wherein the rotation of the first portion is restricted for less than a full rotation relative to the second portion.
- 47. The method of claim 45, terminating the rotation of the first portion at a mechanical release position in which the first portion can be released from the down hole tool.
- 48. The method of claim 45, wherein the fluid-actuated torque-dampening system comprises a flow restrictor disposed between a first chamber and a second chamber formed between the first portion and a tubular member, and wherein restricting the rotation of the first portion comprises flowing fluid from the first chamber to the second chamber.
- 49. The method of claim 45, further comprising:axially actuating the second portion relative to the first portion in response to rotating the first portion, wherein the first and second portions are operably connected at a torsion interface adapted to translate relative rotation between the first and second portions into axial movement of the second portion relative to the first portion; and restricting axial movement of the second portion.
- 50. The method of claim 49, wherein restricting axial movement of the second portion comprises actuating the fluid-actuated torque-dampening system.
- 51. The method of claim 50, wherein actuating the torque-dampening system comprises flowing a fluid therethrough.
- 52. The method of claim 50, wherein the fluid-actuated torque-dampening system is connected to the second portion.
- 53. The method of claim 45, further comprising rotating the first portion relative to the second portion to place the running tool in a liner release position.
US Referenced Citations (20)
Foreign Referenced Citations (1)
Number |
Date |
Country |
WO 9725515 |
Jul 1997 |
WO |