Abstract
A selective downhole actuator comprising at least a first actuator position, a second actuator position and a third actuator position. The selective downhole actuator is reconfigurable between the first actuator position and the second actuator position. The selective actuator is selectively reconfigurable to the third actuator position by varying an operating parameter during a transition of the selective downhole actuator between the first and second actuator positions.
Claims
1. A downhole actuator comprising at least a first actuator position, a second actuator position and a third actuator position, wherein the downhole actuator is fluid-actuated and is reconfigurable between the first actuator position and the second actuator position, and the downhole actuator is selectively reconfigurable to the third actuator position by increasing a fluid flow through or a fluid pressure within the downhole actuator during a transition of the downhole actuator between the first and second actuator positions; wherein at least a portion of a stroke of the actuator in at least one axial direction is damped, the damping comprising viscous damping provided by a choke; wherein the downhole actuator further comprises a passageway comprising a throughbore; wherein the choke is located in a chamber sealed from the throughbore.
2. The downhole actuator of claim 1, wherein the actuator comprises a downhole indexer such that the first, second and third actuator positions comprise first, second and third indexing positions respectively, and wherein being selectively reconfigurable comprises being selectively indexable.
3. The downhole actuator of claim 1, wherein at least one of: the downhole actuator is selectively reconfigurable to the third actuator position only by increasing the fluid flow through or the fluid pressure within the downhole actuator during the transition of the downhole actuator between the first and second actuator positions; the downhole actuator is selectively reconfigurable to the third actuator position by selectively varying the operating parameter during the transition according to a first predetermined pattern, sequence or procedure; and the downhole actuator is cyclable between the first and second positions and only reconfigurable to the third position upon the active selection of the third actuator position.
4. The downhole actuator of claim 1, wherein the downhole actuator is configured to always transition by default to a particular actuation state whenever subjected to a particular operating parameter condition.
5. The downhole actuator of claim 4, wherein at least one of: the default actuation state corresponds to a default actuation position, the default actuation position comprising a default axial and/or rotational actuation position; and the default actuation state comprises a non-actuating default state.
6. The downhole actuator of claim 5, wherein at least one of: the actuator comprises a single default actuation position, the actuator always returning to same actuation position whenever subjected to the default operating parameter condition; and the actuator comprises a plurality of default actuation positions, each comprising a same axial position.
7. The downhole actuator of claim 1, wherein at least one of: the third actuator position comprises an optional actuator position, selectable by the selective variation of an operating parameter; the first actuator position comprises a non-actuating position; the second actuator position comprises a non-actuating position; the second actuator position corresponds to a neutral, starting, return or no-flow or low-flow position; the third actuator position comprises an actuating position; the first actuator position corresponds to a first short stroke position, the second actuator position corresponds to a no-stroke and/or return stroke position; and the third actuator position corresponds to a long stroke position.
8. The downhole actuator of claim 1, wherein the downhole actuator is selectively reconfigurable to the third actuator position by increasing the fluid flow through or the fluid pressure within the downhole actuator during a particular phase or portion of the transition from the first actuator position to the second actuator position, the particular phase or portion corresponding to a window, such as a time and/or travel window.
9. The downhole actuator of claim 8, wherein at least one of: the transition from the first actuator position to the second actuator position is extended or prolonged; and at least a portion of at least the transition from the first actuator position to the second actuator position is damped.
10. The downhole actuator of claim 8, wherein the downhole actuator comprises: a primary path defining the transition from the first position to the second position; and a secondary path defining or at least providing access to the third actuator position; wherein the primary path comprises a junction or intersection for accessing the secondary path during the window portion of transition along the primary path from the first actuator position towards the second actuator position.
11. The downhole actuator of claim 10, wherein at least one of: the secondary path is accessible by reversing at least a portion of the transition along the primary path; and the downhole actuator comprises a main path between the second actuator position and the first actuator position, the main path and the primary path defining a circuit, the main path comprising a stroking or extension path from the second actuator position to the first actuator position, and the primary path comprising a return path from the first actuator position to the second actuator position.
12. The downhole actuator of claim 10, wherein a prolonged or extended window comprises sufficient time to distinguishably establish variation in the operating parameters.
13. The downhole actuator of claim 12, wherein the window provides for sufficient time and/or travel to sufficiently decrease fluid pressure and/or flow to transition along at least a portion of the primary path and then to sufficiently increase fluid pressure and/or flow to reverse transition along the at least a portion of the primary path, such as to access the secondary path.
14. The downhole actuator of claim 10, wherein the third actuator position is indirectly accessible from the first actuator position via the primary path, via a fourth actuator position, wherein the fourth actuator position is an intermediate actuator position between the first actuator position and the third actuator position.
15. The downhole actuator of claim 14, wherein the intermediate actuator position defines an additional pattern, sequence or procedure or a repetition of the first pattern, sequence or procedure, in order to access or index to the third actuator position, the downhole actuator being selectively reconfigurable to the intermediate actuator position by varying an operating parameter during a transition of the downhole actuator between the first and second actuator positions.
16. The downhole actuator of claim 1, wherein at least one of: the downhole actuator is cyclable between the first and second actuator positions by moving in opposite axial and/or rotational directions; the downhole actuator is configured to alternate or oscillate rotational direction during sequential indexing; and the downhole actuator is configured to continually or continuously rotate in substantially the same direction during sequential sequencing.
17. The downhole actuator of claim 1, wherein the downhole downhole actuator is reconfigurable from the first actuator position to the second actuator position by setting an operating parameter at a first value; the downhole downhole actuator is reconfigurable from the second actuator position to the first actuator position by setting the operating parameter at a second value, the downhole downhole actuator being reconfigurable from the second actuator position to the first actuator position by varying the operating parameter to the second value; and the downhole actuator being reconfigurable from the first actuator position to the third actuator position by setting the operating parameter at a third value during the transition from the first actuator position towards the second actuator position.
18. The downhole actuator of claim 1, wherein the downhole actuator comprises a piston, the piston being axially urged or moved according to a pressure differential acting across the piston.
19. A downhole tool comprising the downhole actuator of claim 1.
20. A tool string comprising the downhole actuator of claim 1.
21. A method of downhole actuation, the method comprising reconfiguring a downhole actuator between at least a first actuator position, a second actuator position and a third actuator position, wherein the method comprises: reconfiguring the downhole actuator from the first actuator position towards the second actuator position; and selectively reconfiguring the downhole actuator to the third actuator position by increasing the fluid flow through or the fluid pressure within the downhole actuator during a transition of the downhole actuator between the first and second actuator positions; wherein at least a portion of a stroke of the actuator in at least one axial direction is damped, the damping comprising viscous damping provided by a choke; wherein the downhole actuator is fluid-actuated and further comprises a passageway comprising a throughbore; wherein the choke is located in a chamber sealed from the throughbore.
22. The method of claim 21, wherein the method comprises indexing a downhole selective downhole indexer, the first, second and third actuator positions comprising first, second and third indexing positions respectively.
23. The method of claim 21, wherein at least one of: selectively reconfiguring to the third actuator position is only achievable by increasing the fluid flow through or the fluid pressure within the downhole actuator during the transition of the downhole actuator between the first and second actuator positions: the operating parameter is selectively varied during the transition according to a first predetermined pattern, sequence or procedure; and indexing or reconfiguring the downhole actuator to the activating position comprises or requires varying the operating parameter at least twice sequentially according to a predetermined pattern, sequence or procedure.
24. The method of claim 21, wherein the method comprises always transitioning by default to a particular actuation state whenever the actuator subjected to a particular operating parameter condition.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
(1) Embodiments will now be described, by way of example, with reference to the accompanying drawings, in which:
(2) FIG. 1 shows a schematic representation of a toolstring comprising an embodiment of a selective downhole actuator;
(3) FIG. 2 shows a partial cutaway three-quarter isometric view of an embodiment of a selective downhole actuator;
(4) FIG. 3 shows a cross-sectional schematic view of the selective downhole actuator in a neutral, starting, return or no-flow actuator position;
(5) FIG. 4 shows a further cross-sectional schematic view of the selective downhole actuator of FIG. 2 with the actuator in a different actuator position;
(6) FIG. 5 shows a yet further cross-sectional schematic view of the selective downhole actuator of FIG. 2 with the actuator in a further different actuator position;
(7) FIG. 6 shows a partial cutaway side view of the selective downhole actuator of FIG. 2 with the actuator in the actuator position of FIG. 3;
(8) FIG. 7 shows a detail view of FIG. 6 with the actuator in the actuator position of FIG. 3;
(9) FIG. 8 shows a detail view of the selective downhole actuator of FIG. 6 with the actuator in the actuator position of FIG. 4;
(10) FIG. 9 shows a detail view of the selective downhole actuator of FIG. 6 with the actuator in a first transitional actuator position in between the actuator positions of FIG. 4 and the neutral, starting, return or no-flow actuator position of FIG. 3;
(11) FIG. 10 shows a detail view of the selective downhole actuator of FIG. 6 with the actuator in a second transitional actuator position in between the actuator positions of FIG. 4 and the neutral, starting, return or no-flow actuator position of FIG. 3;
(12) FIG. 11 shows a detail view of the selective downhole actuator of FIG. 6 with the actuator returned to the neutral, starting, return or no-flow actuator position of FIG. 3 (and FIG. 7);
(13) FIG. 12 shows a detail view of the selective downhole actuator similar to that of FIG. 6with the actuator in the actuator position of FIG. 4;
(14) FIG. 13 shows a detail view of the selective downhole actuator of FIG. 6 with the actuator in an actuator position in between those of FIGS. 9 and 10;
(15) FIG. 14 shows a detail view of the selective downhole actuator of FIG. 6 with the actuator in a different actuator position;
(16) FIG. 15 shows a detail view of the selective downhole actuator of FIG. 6 with the actuator in a transitional position in between the positions of FIG. 14 and FIG. 7 (and FIGS. 3 and 11);
(17) FIG. 16 shows a detail view of the selective downhole actuator of FIG. 6 with the actuator in a further different actuator position similar to that of FIG. 5;
(18) FIG. 17 shows a detail view of the selective downhole actuator of FIG. 6 with the actuator returned to the neutral, starting, return or no-flow actuator position of FIG. 3 (and FIGS. 7 and 11);
(19) FIG. 18 shows a two-dimensional or flattened layout of a path of the selective downhole actuator of FIG. 3;
(20) FIG. 19 shows the two-dimensional or flattened layout of the path of FIG. 18 indicating a damping zone or phase;
(21) FIG. 20 shows the two-dimensional or flattened layout of the path of FIG. 18 with a cooperating element at a neutral, starting, return or no-flow position corresponding to the neutral, starting, return or no-flow actuator position of FIG. 3;
(22) FIG. 21 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 4 (and FIG. 8);
(23) FIG. 22 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 9;
(24) FIG. 23 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 10;
(25) FIG. 24 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 20;
(26) FIG. 25 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 23;
(27) FIG. 26 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 22;
(28) FIG. 27 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 14;
(29) FIG. 28 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at a transitional actuator position in between the positions of FIG. 27 and FIG. 20 (and FIG. 24);
(30) FIG. 29 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at a further transitional actuator positiongenerally similar to the position of FIG. 15in between the positions of FIG. 27 and FIG. 20 (and FIG. 24);
(31) FIG. 30 shows the two-dimensional or flattened layout of the path of FIG. 18 with a cooperating element at a neutral, starting, return or no-flow position corresponding to the neutral, starting, return or no-flow actuator position of FIG. 20;
(32) FIG. 31 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 29;
(33) FIG. 32 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 28;
(34) FIG. 33 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element in a further different actuator position corresponding to that of FIGS. 5 and 16;
(35) FIG. 34 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 32;
(36) FIG. 35 shows the two-dimensional or flattened layout of the path of FIG. 18 with the cooperating element at an actuator position corresponding to that of FIG. 31;
(37) FIG. 36 shows the two-dimensional or flattened layout of the path of FIG. 18 with a cooperating element at a neutral, starting, return or no-flow position corresponding to the neutral, starting, return or no-flow actuator position of FIG. 30;
(38) FIG. 37 shows a cross-sectional view of a portion of the selective downhole actuator of FIG. 6.
(39) FIG. 38 shows a two-dimensional or flattened layout of a path of a selective downhole actuator, indicating a damping zone or phase;
(40) FIG. 39 shows the two-dimensional or flattened layout of the path of FIG. 38 with a cooperating element at a neutral, starting, return or no-flow position corresponding to the neutral, starting, return or no-flow actuator position of FIG. 3;
(41) FIG. 40 shows the two-dimensional or flattened layout of the path of FIG. 38 with the cooperating element at an actuator position similar to that of FIG. 4 (and FIG. 8);
(42) FIG. 41 shows the two-dimensional or flattened layout of the path of FIG. 38 with the cooperating element at an actuator position similar to that of FIG. 9 (and FIG. 22), with the actuator in a transitional actuator position in between the actuator positions of FIG. 40 and the neutral, starting, return or no-flow actuator position of FIG. 39;
(43) FIG. 42 shows the two-dimensional or flattened layout of the path of FIG. 38 with the cooperating element at an actuator position similar to that of FIG. 10 (and FIG. 23);
(44) FIG. 43 shows the two-dimensional or flattened layout of the path of FIG. 38 with a cooperating element at a neutral, starting, return or no-flow position corresponding to the neutral, starting, return or no-flow actuator position of FIG. 39;
(45) FIG. 44 shows the two-dimensional or flattened layout of the path of FIG. 38 with the cooperating element at an actuator position corresponding to that of FIG. 42 (and similar to that of FIG. 23);
(46) FIG. 45 shows the two-dimensional or flattened layout of the path of FIG. 38 with the cooperating element at an actuator position similar to that of FIG. 14 (and FIG. 27);
(47) FIG. 46 shows the two-dimensional or flattened layout of the path of FIG. 38 with the actuator in a first transitional actuator position in between the actuator positions of FIG. 45 and a neutral, starting, return or no-flow actuator position similar to FIG. 39;
(48) FIG. 47 shows the two-dimensional or flattened layout of the path of FIG. 38 with the actuator in a second transitional actuator positionin between the first transitional position of FIG. 46 and a neutral, starting, return or no-flow actuator position similar to FIG. 39;
(49) FIG. 48 shows the two-dimensional or flattened layout of the path of FIG. 38 with the actuator in a neutral, starting, return or no-flow actuator position similar to that of FIG. 39;
(50) FIG. 49 shows the two-dimensional or flattened layout of the path of FIG. 38 with the actuator in the second transitional actuator position of FIG. 47in between the first transitional position of FIG. 46 and a neutral, starting, return or no-flow actuator position similar to FIG. 39;
(51) FIG. 50 shows the two-dimensional or flattened layout of the path of FIG. 38 with the cooperating element in a further different actuator position similar to that of FIGS. 5, 16 and 33;
(52) FIG. 51 shows the two-dimensional or flattened layout of the path of FIG. 38 with the cooperating element at an actuator position corresponding to that of FIG. 49;
(53) FIG. 52 shows the two-dimensional or flattened layout of the path of FIG. 38 with the cooperating element in a third transitional actuator positionin between the second transitional position of FIG. 47 and a neutral, starting, return or no-flow actuator position similar to FIG. 39; and
(54) FIG. 53 shows the two-dimensional or flattened layout of the path of FIG. 38 with the actuator in the neutral, starting, return or no-flow actuator position corresponding to that of FIG. 48;
(55) FIG. 54 shows a two-dimensional or flattened layout of a path of another selective downhole actuator, indicating a damping zone or phase;
(56) FIG. 55 shows a schematic representation of a further toolstring comprising an embodiment of a selective downhole actuator; and
(57) FIG. 56 shows a schematic representation of a yet further toolstring comprising an embodiment of a selective downhole actuator.
DETAILED DESCRIPTION OF THE DRAWINGS
(58) Reference is first made to FIG. 1, which shows a schematic representation of a downhole tool string 2 in accordance with a first embodiment of the present invention. Here, the tool string comprises a selective downhole actuator 10 located near-bit in a BHA, adjacent an under-reamer 5, above a drill-bit 4. However, it will be appreciated that in other embodiments (not shown), the selective downhole actuator is located at any position in the tool string. It will also be appreciated that in other tool string embodiments (not shown) additional or alternative tools, including for selective downhole actuation, are selected from one or more of: a reamer; a drill-tool; a valve; a scraping tool; a percussion tool; an agitator; a bypass tool; or the like (not shown). Examples of under-reamers are described in applicant's International (PCT) Application Publication Nos. WO 2004/097163 and WO 2010/116152, the disclosures of which are incorporated herein by reference.
(59) As shown here, the selective downhole actuator 10 is located downhole of a positive displacement motor 6 used to rotate the under-reamer 5, the actuator 10, and the drill-bit 4. In the embodiment shown a stabilizer 7 is also optionally provided as desired. It will be appreciated that in at least some embodiments, elements (not shown), such as a rotatable mandrel, may extend through the actuator 10, such as through a throughbore of the actuator 10.
(60) The selective downhole actuator 10 can be used to selectively actuate and deactuate the under-reamer 5 such that the under-reamer 5 reams when desired and only when desired. The selective actuation will be described in detail below, with particular reference to embodiments of selective downhole actuators in the subsequent Figures.
(61) Reference is now made to FIG. 2, which shows a partial cutaway three-quarter isometric view of an embodiment of a selective downhole actuator 110. It will be appreciated that the selective downhole actuator 110 shown may be mounted in a tool string, such as that shown in FIG. 1. For example, the selective downhole actuator 110 may be mounted using appropriate box connections at its upper and lower ends.
(62) The selective downhole actuator 110 comprises at least a first actuator position, a second actuator position and a third actuator position. The selective downhole actuator is reconfigurable between the first actuator position and the second actuator position to the third actuator position by varying an operating parameter during a transition of the selective downhole actuator 110 between the first and second actuator positions, as will be described in detail below.
(63) In the embodiment shown here, the selective downhole actuator 110 comprises a downhole indexer. Accordingly, the first, second and third actuator positions comprise a respective first, second and third indexing position; and the indexer is selectively indexable to the third indexing position by varying an operating parameter during a transition of the indexer between the first and second indexing positions.
(64) The selective downhole actuator 110 is mountable within a tool string so as to allow the passage of fluid therethrough. For example, the selective downhole actuator 110 is mountable to allow the passage of drilling fluid or injection fluid or of formation fluids, such as production fluid. The selective downhole actuator 110 comprises a passageway 112 for the passage of fluid. Here, the passageway 112 comprises a central throughbore.
(65) A first portion of the selective downhole actuator 110 comprises a housing 114 in the form of a tubular portion of toolstring here. A second portion of the selective downhole actuator 110 comprises a sleeve or mandrel 116 housed within the housing 114.
(66) Here, the housing 114 comprises a pair of protrusions in the form of a pair of guide pins 118, each being positioned diametrically opposed from the other 118. The guide pins 118 are fixed to the housing 114 here via a support member 128. Here, the sleeve or mandrel 116 has a pair of recesses in the form of a pair of slot channels 120 also diametrically opposed from each other 120with each of the corresponding pins 118 extending into the respective slot channel 120.
(67) The selective downhole actuator 110 comprises a piston 122 integral with the sleeve or mandrel 116, the piston 122 being acted upon by fluid in an adjacent chamber 123. The chamber 123 is defined between the sleeve or mandrel 116 and the housing 114, external to the throughbore 112. Here, the chamber 123 is in fluid communication with the throughbore via an internal port 126. In addition an external port 127 to annulus is provided such that fluid in the chamber 123 is in fluid communication with the annulus. Accordingly, a fluid pressure differential across the internal port 126 may be generated with different pressure in the throughbore 112 and in the fluid chamber 123. The internal and external ports 126, 127 are sized and arranged such that the fluid pressure in the fluid chamber 123 corresponds to the external fluid pressure in the annulus. Whilst there is a fluid pressure differential across the internal port 126, an axial force acting on the piston 122 is generated.
(68) It will be appreciated that in alternative embodiments, no internal port 126 may be provided, with the fluid chamber 123 only being in fluid communication with the external annulus. However, as shown here, the internal port 126 may provide a fluid supply that may assist in flushing the fluid chamber 123 such that the fluid chamber 123 may remain free of debris or obstructions.
(69) The selective downhole actuator 110 comprises a biasing member, here in the form of a helical compression return spring 124. In FIG. 2, the spring 124 is shown for biasing the piston 122 to the left. The spring 124 acts against a force acting on the piston 122 that is generated by the fluid pressure differential acting across the port 126. Accordingly, the biasing or movement of the piston 122 is variable by adjusting the fluid pressure in the throughbore 112 to vary a fluid pressure differential across the port 126, such that the resultant fluid pressure force may be varied relative to the force applied by the spring 124. It will be appreciated, that in alternative embodiments, the spring biasing force may be at least augmented by a fluid pressure force generated by fluid pressure, such as from fluid entering the sealed chamber that houses the spring 124 via an external port.
(70) The selective downhole actuator 110 comprises a support member 128 to support the selective downhole actuator 110 at a plurality of the actuator positions. Here, the support member 128 is configured to carry substantially all of a load or force otherwise transferable between the sleeve or mandrel 116 and the housing 114 of the selective downhole actuator 110 at at least the first and third actuator positions. The support member 128 supports the sleeve or mandrel 116 at actuator positions corresponding to when the selective downhole actuator 110 is stroking (e.g. with the sleeve or mandrel 116 moved to the right from FIG. 3, such as shown in FIGS. 4 and 5), when resultant forces of fluid pressure acting on the piston 122 (as a result of the fluid pressure differential from the throughbore 112 across the port 126) are higher than the biasing force of the spring 124, such as when the pumps are ON or fully ON.
(71) With particular reference to FIGS. 3, 4 and 5 respectively, the selective actuator of FIG. 2 is shown in cross-sectional views in various positions, noting that the spring 124 has been omitted from FIG. 4 for clarity. The actuator 110 is shown in FIG. 4 in a first actuator position, which is a short stroke position in the embodiment shown. Here, the short stroke position of FIG. 4 is a non-actuating position, with the sleeve or mandrel 116 not extended sufficiently (to the right as shown) from an initial, neutral or return longitudinal position of FIG. 3 in order to cause actuation.
(72) The sleeve or mandrel 116 is moved to the first actuation position of FIG. 4 from the position of FIG. 3 by increasing the fluid pressure differential across the port 126, such as by turning on pumps (not shown) pumping a fluid through the throughbore 112 (e.g. to power a downhole motor and/or to flush whilst drilling). Increasing the fluid pressure in the throughbore 112 causes an increased fluid pressure differential between fluid pressure in the throughbore 112 and the fluid pressure in the piston chamber 123. When the fluid pressure differential across the fluid port 126 is sufficient, the corresponding force generated on the piston 122 overcomes the biasing force of the spring 124 and the sleeve or mandrel 116 moves axially relative to the housing 114 (to the right as shown in FIGS. 2 to 5).
(73) The movement of the sleeve or mandrel 116 relative to the housing 114 from the position of FIG. 3 to the position of FIG. 4 is guided by the pin 118 and slot 120 arrangement. In the position of FIG. 4, the sleeve or mandrel 116 is axially supported by the support member 128 in order to reduce axial loads or forces carried by the pins 118 that may be associated with the forces generated by the increased fluid pressure in the throughbore 112. The support member has a first landing portion 130 for supporting a corresponding support flange 132 of the sleeve or mandrel 116 at the short stroke position of FIG. 4, as can also be seen in FIGS. 8 and 12.
(74) The actuator 110 can be returned from the first actuator position of FIG. 4 to the second actuator position of FIG. 3 by reducing the pressure differential across the piston 122, such as by turning down or off of pumps to reduce fluid pressure in the throughbore 112 and allowing the fluid pressure across the port 126 to balance or at least drop sufficiently below the biasing force of the spring 124.
(75) FIG. 5 shows a third or different actuator position that may be selectively accessed subsequent to the first position of FIG. 4, as will be described in detail below with particular reference to FIGS. 6 to 36. In FIG. 5, the different actuator position shown is a long stroke position corresponding to an actuating position of the actuator 110, with the sleeve or mandrel 116 extending sufficiently (to the right as shown in FIG. 5) relative to the housing 114 to cause actuation, such as of an adjacent tool (not shown, e.g. to the right of the actuator 110 as shown in FIG. 5).
(76) Referring now to FIGS. 6 to 17, there are shown an overview and then subsequent sequential views showing partial cutaway side views of the selective downhole actuator 110 of FIG. 2. FIG. 6 shows the overview of the actuator 110 with the housing 114 and the return spring 124 omitted for clarity. The actuator 110 is shown in FIG. 6 with the sleeve or mandrel 116 in the actuator position of FIG. 3. FIG. 6 shows the first landing shoulder 130 of the support member 128 for supporting the corresponding support flange 132 at the first actuator position of FIG. 4 and a second landing shoulder 131 of the support member 128 for supporting the corresponding support flange 132 at the actuator position of FIG. 5.
(77) FIG. 7 shows a detail view of FIG. 6, with the view position rotated 90 to provide a clearer side view of one of the guide pins 118. The actuator 110 is shown with the sleeve or mandrel 116 in the neutral or starting position such as may be associated with no flow through the throughbore 112 (e.g. prior to commencing a drilling operation or the like).
(78) FIG. 8 shows a detail view with the sleeve or mandrel 116 moved or indexed to the first actuator position corresponding to FIG. 4 from the neutral or starting position of FIG. 3. It will be appreciated that the sleeve or mandrel 116 has moved relative to the housing 114 along a path 148 defined by the slot channel 120 engaging the projecting pin 118. The movement of the sleeve or mandrel 116 was propelled by the increase in fluid pressure differential across the port 126 generating an axial force (to the right as shown) on the piston 122 that overcame the biasing force (to the left as shown) of the spring 124. Just prior to the sleeve or mandrel 116 moving or extending sufficiently for the pin 118 to engage an axial end wall of a portion of the slot channel 120, the first landing shoulder 130 is engaged by the corresponding support flange 132 to define a no-go such that a clearance 136 (as shown in FIG. 37) is maintained between the pin 118 and the axial end wall of the slot channel 120.
(79) FIG. 9 shows the actuator 110 in a first transitional actuator position in between the actuator positions of FIG. 8 and the neutral, starting, return or no-flow actuator position of FIG. 7. Again, it will be appreciated that the sleeve or mandrel 116 has moved relative to the housing 114 along the path 134 defined by the slot channel 120 engaging the projecting pin 118. From the position of FIG. 8 to the position of FIG. 9, the movement of the sleeve or mandrel 116 was propelled by the biasing force (to the left as shown) of the spring 124 acting on the sleeve or mandrel 116, which has become greater than an axial force (to the right as shown) generated on the piston 122 by a decrease in fluid pressure differential across the port 126, such as by turning down or off pumps. As shown in FIG. 9, the sleeve or mandrel 116 is moving relative to the housing 114 with the pin 114 at a first transitional position along a primary path 138 defining the transition from the first position of FIG. 8 to the second position of FIG. 11 (and FIG. 7the second position also being the neutral or starting position in this instance).
(80) A continuing imbalance between the force of the spring 124 and the pressure differential-generated force across the port 126 with the spring force being greater than the fluid pressure force as shown in FIG. 9, causes the sleeve or mandrel 116 to continue along the primary path 138 in the same axial direction. Accordingly, as shown in FIG. 10, the pin 118 reaches a second transitional position along the primary path 138 towards the second position of FIG. 11. Whilst the fluid pressure differential force remains lower than the spring force, the sleeve or mandrel 116 continues to move further in the same axial direction (to the left as shown in FIG. 10) such that the pin 118 is ultimately located in the second actuator position of FIG. 11, which in this embodiment shown is the same position as the neutral or starting position of FIG. 7.
(81) Accordingly, the sequence of relative movements between the sleeve or mandrel 116 and the housing 114 of FIGS. 8 to 11 results in the actuator 110 being reconfigured between the first and second actuator positions. In the embodiment shown, the first actuator position of FIG. 8 is a short stroke position and the neutral or starting position of FIG. 7 is also the second or return actuator position of FIG. 11. All of the actuator positions of FIGS. 7 to 11 correspond to relatively limited axial movement of the sleeve or mandrel 116, such that all of the positions of FIGS. 7 to 11 correspond to non-actuating positions. Accordingly, the fluid operating conditions may be varied, such as by turning on and off pumps, without causing the actuator 110 to actuate. For example, the actuator may be incorporated in a drill string where it is desired to operate the pumps a number of times prior to extending the cutters of an underreamer, such as to test pumps, flush and/or drill without reaming. The fluid operating conditions may be endlessly varied without actuating the actuator 110, provided the operating conditions are not varied according to a predetermined pattern during the transition from the first position of FIG. 8 to the second position of FIG. 11, as will be described in detail below.
(82) FIG. 12 is the same as FIG. 8, with the sleeve or mandrel 116 moved or indexed to the first actuator position corresponding to FIG. 4 from the neutral or starting position of FIG. 3, with the pumps turned on, but with no actuation. FIG. 13 shows the actuator 110 with the sleeve or mandrel 116 moved, by turning the pumps off, to a transitional position between those of FIGS. 9 and 10. In FIG. 13, the pin 118 is located along a window portion of the primary path 138, the window portion of the primary path extending between a junction or intersection 140 and the second position of FIG. 11, the intersection 140 of the primary path defining an access route to an optional secondary path 142.
(83) The secondary path 142 provides access to a further actuator position of FIG. 14 and is accessible from the primary path 138 by the selective variation of an operating parameter during the relative transition of the pin 118 along the window portion of the primary path 138 from the first transitional actuator position of FIG. 9 towards the second transitional position of FIG. 10. Here, the further actuator position of FIG. 14 is a further short stroke position, which provides an intermediate actuator position prior to an actuating actuator position. The secondary path 142 may be considered as a branch path from the primary path 138, allowing for the selective transition from the first position to a further actuator position. Here, the secondary path 142 is accessed by turning the pumps back on whilst the pin 118 is relatively transitioning along the window portion of the primary path 138 towards the position of FIG. 11. Turning the pumps back on before the pin 118 reaches the position of FIG. 10 causes the axial direction of movement of the sleeve or mandrel 116 to reverse as the fluid pressure force (generated by the pressure differential across the port 126) overcomes the spring biasing force. Accordingly, the relative movement of the pin 118 along the primary path 138 is reversed and the pin 118 relatively travels towards the intersection 140, away from the second position of FIG. 10. On reaching the intersection 140, continued axial movement of the sleeve or mandrel 116 caused by the pumps being on causes the relative movement of the pin 118 in the slot 120 to continue along the secondary path 142. In the embodiment shown, the sleeve or mandrel 116 is not rotationally-biased relative to the housing 114, such that axial movement is in the direction of least resistance (e.g. direct axial movement where possible), such that the pin 118 does not continue back along the primary path 138 beyond the intersection 140 towards the position of FIG. 12, but instead follows the secondary path 142 beyond the intersection 140 towards the position of FIG. 14. In alternative embodiments, it will be appreciated that the sleeve or mandrel may be rotationally biased to at least assist in directing into a particular path or slot, such as a particular path that is not purely axial.
(84) Again, just prior to the sleeve or mandrel 116 moving or extending sufficiently for the pin 118 to engage an axial end wall of a portion of the secondary path 142 of the slot channel 120, the first landing shoulder 130 is engaged by the corresponding support flange 132 to define a similar no-go such that a clearance 136 is maintained between the pin 118 and the axial end wall of the slot channel 120, as shown in FIG. 14.
(85) The position of FIG. 14 is another short stroke position, such that again the actuator 110 is in a non-actuating position. Such a further short stroke position may allow for a turning back on of the pumps during a first return stroke (from the position of FIG. 8 to the position of FIG. 11), such as an accidental turning back on of the pumps. Or the further stroke position may allow for a brief lapse in fluid pressure, such as the pumps accidentally dropping or being turned off, or of a valve (elsewhere) in the string being opened or closed. In each case, the further stroke position of FIG. 14 may provide for a safety means to prevent or at least reduce a risk of accidental actuation of the actuator 110.
(86) FIG. 15 shows a position of the actuator 110 after the pumps have been turned off again, subsequent to the position of FIG. 14. The sleeve or mandrel 116 is forced axially by the spring 124 (to the left as shown) such that the pin 118 has transitioned along a return portion of the secondary path 142 towards the return neutral or starting position of FIGS. 7 and 11. The pin 118 is again located in another window portion of the return stroke in FIG. 15. Accordingly, if the pumps are switched on again for a second time before the pin 118 has relatively transitioned along the return portion of the secondary path to reach the return neutral or starting position of FIGS. 7 and 11, then the axial direction of movement of the mandrel or sleeve 116 relative to the housing 114 is reversed and the pin 118 travels relatively back along the return portion of the secondary path 142 towards a further junction or intersection 144, the further intersection 144 of the secondary path 144 defining an access route to an optional further secondary path 146. Again, the slot channel 120 is configured such that continued axial movement of the sleeve or mandrel 116 propelled by the fluid pressure force causes the pin 118 to relatively travel along the further secondary path 146 towards a further stroke position as shown in FIG. 16. The further stroke position of FIG. 16 is a long stroke position, corresponding to an actuating position. Accordingly, the actuator 110 is reconfigured or indexed to the actuating position by a predetermined series of changes in the fluid pressure, within windows provided in return portions of strokes. In this example, the actuator 110 is reconfigured or indexed to the actuating position only by re-engaging pumps during particular windows of two successive return strokes. Upon return to the neutral or starting position, the actuator must be reconfigured or indexed twice in particular succession in order to access the actuating position of FIG. 16. Accordingly, the actuator 110 may be incorporated in a drill string where it may be desirable to vary the fluid pressure without necessarily reconfiguring or indexing the actuator 110 to an actuating position, even although a particular fluid pressure may be reached during the variation that may otherwise be sufficient to actuate the actuator 110. Subsequent to actuation, the actuator 110 may be returned to the starting or neutral positions of FIGS. 7 and 11 by again turning off the pumps such that the sleeve or mandrel 116 and the housing 114 move axially, with the pin 118 relatively transitioning along the further secondary path 146 and return portion of the secondary path 142 from the position of FIG. 16 to the position of FIG. 17. Thereafter the actuator may be endlessly cycled between the short stroke position of FIG. 8, 12 or 14 and the neutral or start position of FIG. 7 or 11 without actuation; or endlessly cycled between these non-actuating positions and the actuating position of FIG. 16 by following the predetermined sequence of fluid pressure variations corresponding to FIGS. 11 to 16 sequentially.
(87) Once in the start or neutral position of FIG. 7, 11 or 17, the pin 118 always must transition along a main path 148 of the slot channel 120 to reach the first position of FIG. 8and optionally any of the other actuating positions, such as of FIG. 14 and then 16. Accordingly, the main path 148 and the primary, secondary, and further secondary paths 138, 142 146 define circuits for the endless cycling of the actuator 110.
(88) Referring now to FIG. 18, there is shown a two-dimensional or flattened representative layout of the slot channel 120 of the selective downhole actuator 110 of FIG. 3. The primary, secondary and further secondary paths 138, 142, 146 are shown, together with the appropriate intersections 140, 144 therebetween. It will be appreciated that in the embodiment shown here, the same slot channel 120 is repeated twice around the circumference of the sleeve or mandrel 116, although only one slot channel 120 is shown here for clarity.
(89) FIG. 19 indicates the window portion 150 of the axial return stroke of the sleeve or mandrel 116, as the sleeve or mandrel 116 travels axially towards the neutral or start positions of FIG. 7, 11 or 17, relative to the pin 118 (not shown in FIGS. 18 and 19). In the embodiment shown, the piston 122 is a damped piston during the window portion 150 of the axial return stroke of the sleeve or mandrel 116. A portion of the piston's 122 return stroke corresponds to a passage of a damping piston 153 associated and moveable with the piston 122 through a necking 152 of the housing to define a choke. During the passage of the damping piston 153 through the necking 152, the cross-sectional flow area for fluid, such as a fixed volume of oil, to flow between the chambers either axial side of the damping piston 153 is reduced, such that the rate of travel of the damping piston 153 and associated piston 122 is reduced. Accordingly, the period of transition from the stroking actuator positions of FIGS. 8 and 14 (and 16) to the start or neutral actuator position of FIGS. 7 and 11 (and 17) is extended or prolonged, at least relative to a conventional transition of a selective downhole actuator between actuator positions or of such an actuator without such damping provision. The damped portion corresponds to the window portion 150 for selectively accessing the optional (second and further second or third) actuating positions. Accordingly, a prolonged or extended period for selectively accessing the third actuator position is provided. The prolonged or extended period comprises sufficient time to distinguishably establish variation in the operating parameters. Here, the period provides for sufficient time and travel to sufficiently decrease fluid pressure to transition along at least a portion of the primary path 138 beyond the intersection 140, and then to sufficiently increase fluid pressure to reverse transition along the primary path 138 to access the secondary or branch path 142. For example, the window provides sufficient time for an operator at surface to receive feedback on a measured fluid pressure. Here, the window portion 150 provides for successive respective periods of between two and ten minutes for accessing each of the secondary and further secondary paths 142, 146. Damping at least a portion the transition between the actuator positions also reduce stresses or strains, such as may otherwise be associated with impact or higher velocity or undamped transitions or movements.
(90) It will be appreciated that, in the embodiment shown, the choke, the pin 118 and slot 120 arrangement, the landing shoulders 130 and corresponding flanges 132, and the spring 124 are isolated from the fluid in the throughbore 112. In the embodiment shown, the choke, the pin 118 and slot 120 arrangement, the landing shoulders 130 and corresponding flanges 132, and the spring 124 are located in a chamber sealed from the throughbore 112, which, as shown, can be filled with a different fluid such as a closed oil reservoir, also isolated from the annulus external to the toolstring 110 in the embodiment shown.
(91) It will also be appreciated, that the provision of a damped portion of transition that provides an extended period of time between actuation positions may be utilised in alternative or additional applications. For example, the damped portion may provide a sufficient period of time to define an intermediate actuation position. That intermediate actuation position may define an additional or intermediate actuation state or function. For example, that intermediate position may correspond to a further actuation state, such as to define an additional state or function of a tool or member actuatable by the actuator. For example, the damped portion may correspond to an intermediate state of a valve, which may be held in an intermediate state (e.g. partially open) between two other states (e.g. fully closed and fully open), at least for the duration of the damped period of transition. Other applications may include the use of the damped portion to provide an intermediate position of a tool, member or element associated with the actuator, such as an intermediate extension position of a member (e.g. a cutter).
(92) FIGS. 20 to 36 show sequentially the successive relative positions and movements therebetween of the pin 118 relative to the slot channel 120, with a previous position of the pin 118 being indicated in broken lines and preceding movement identified with appropriate arrows along the slot channel 120. FIGS. 20, 24, 30 and 36 show the relative position of the pin 118 to the slot channel 120 corresponding to the neutral or start position of FIGS. 3, 7, 11 and 17. FIG. 21 shows the relative position of the pin 118 to the slot channel 120 corresponding to the short stroke position of FIGS. 4, 8, and 12. FIG. 27 shows the relative position of the pin 118 to the slot channel 120 corresponding to the intermediate short stroke position of FIG. 14. FIG. 33 shows the position of the pin 118 relative to the slot channel 120 corresponding to the long stroke position of FIGS. 5 and 16. FIGS. 22, 23, 25, 26, 28, 29, 31, 32, 34 and 35 show the positions of the pin 118 relative to the slot channel 120 in between the immediately preceding and succeeding numbered figure. For example, FIG. 22 shows the position of the pin 118 relative to the slot channel 120 in between the positions of FIG. 21 and FIG. 23. Accordingly it is clear that the actuator may be selectively actuated by performing a predetermined operating sequence to vary fluid parameters to control actuation of the actuator 110, whilst providing the possibility to vary fluid parameters without affecting the actuation state of the actuator, such as to prevent unintended or accidental actuation.
(93) It will be appreciated that the selective downhole actuator 110 is configured to transition by default to a particular actuation state in a particular condition, such as whenever subjected to a particular operating parameter condition. In the embodiment shown here, the default actuation state corresponds to a single default actuation position of FIGS. 20, 24, 30 and 36, which can be considered as a default axial and rotational actuation position. Here, where the actuator 110 is defaulting to a non-actuating state under no flow or low fluid pressure from the first, third and intermediate actuation positions, the actuator defaults to the second actuation position, which is also the initial or starting position as shown here.
(94) FIG. 37 shows a detail view of the actuator 110 of FIG. 4, with the first landing shoulder 130 engaging the corresponding flange 132 at the short stroke position, corresponding to that of FIGS. 8 and 14. Accordingly, the clearance 136 between the pin 118 and an axial end wall of the slot 120 is clearly visible.
(95) FIG. 38 shows an alternative slot channel 220 for providing a similar actuation pattern to that of the slot channel 120 of FIG. 18, with similar features denoted by similar reference numerals, incremented by 100. Accordingly, the slot channel comprises a primary path 238 and a first intersection 240. As shown here, the direction of fluid pressure force and also of spring bias are reversed (i.e. the fluid pressure force acts to propel the sleeve or mandrel 216 to the left, whilst the springnot shown hereacts to propel the mandrel or sleeve to the right). Such an arrangement may be achieved by substantially inverting the actuator 110 of FIG. 6 or by swapping the positions of the spring 124 and the piston chamber 123 of FIG. 6. Accordingly, it will be appreciated that the neutral or starting position shown in FIG. 38 corresponds to a similar neutral or starting actuator axial or longitudinal position of FIGS. 3, 7, 11, 17, 20, 24, 30 and 36.
(96) FIGS. 39 to 53 show sequentially the successive relative positions and movements therebetween of the pin 218 relative to the slot channel 220, with a previous position of the pin 218 being indicated in broken lines and preceding movement identified with appropriate arrows along the slot channel 220. Again, in the embodiment here, there is provide a first short stroke position, shown in FIG. 40; and a further short stroke position, in FIG. 45 intermediate the stroking position of FIG. 40 and a long stroke position of FIG. 50. The first short stroke position of FIG. 40 is generally functionally similar to that of FIGS. 4, 8, 12 and 21. The intermediate short stroke position of FIG. 45 is generally functionally similar to that of FIGS. 14 and 27. The long stroke position of FIG. 50 generally corresponds functionally to the long stroke position of FIGS. 5, 16 and 33. However, in the embodiment of FIGS. 38 to 53, subsequent to actuation by accessing the long stroke position of FIG. 50 or of accessing the intermediate short stroke position of FIG. 46, the pin 218 does not necessarily return to the same return actuator position upon completion of the return stroke as in the embodiment of FIGS. 2 to 37. Rather, the return portion of the secondary path 242 (and, here, the further secondary path 246) does not necessarily require returning to the same return position as the starting or neutral position of FIG. 39.
(97) As can be seen when comparing FIG. 48 or 53 with FIG. 39 (or FIG. 43), the pin 218 may be returned to a return actuator position laterally adjacent the start actuator position. Here, the optionally selectable return positions of FIGS. 48 and 53 are of similar longitudinal or axial position to the start actuator position of FIG. 38 and the default first return position of FIG. 43. Here, the start actuator position of FIG. 38 and the default first return position of FIG. 43 are merely laterally or circumferentially separated from the optionally selectable return positions of FIGS. 48 and 53 (i.e. the start and return positions are longitudinally aligned and rotationally spaced around the sleeve or mandrel 216). It will be appreciated that here the optionally selectable return positions of FIGS. 48 and 53 correspond to the start position of a second pin (not shown) positioned diametrically opposite the first pin 118. Accordingly, the portion of the slot channel 220 shown in FIG. 38 is repeated around the sleeve or mandrel 216 to define a continuous slot channel 220 around the circumference of the sleeve or mandrel 216. Whereas the embodiment 110 of FIGS. 2 to 37 can continuously cycle by repeatedly oscillating in rotational and axial directions, the embodiment of FIGS. 38 to 53 may endlessly cycle by repeatedly oscillating in rotational direction between the positions of FIGS. 39 and 40 and/or may endlessly cycle by repeatedly progressively rotating in a continuous direction of rotation. In both of these embodiments 110, 210, the actuator 110, 210 may be endlessly cycled by reversing an axial direction of movement of the sleeve or mandrel 116, 216.
(98) As can be seen in FIG. 38, the return portions of each of the primary, secondary paths 238, 242, provide identical windows, such as for selectively accessing the secondary or further secondary paths 242, 246. Compared to the embodiment of FIGS. 2 to 37, the embodiment of FIG. 38 to FIG. 53 may require a shorter axial length for the slot channel 220 providing a generally similar functionality. For example, comparing the similar window portions 150, 250, it can be seen that the return portion of the secondary path 146 of FIG. 19 comprises a section towards the return position beyond (to the right of) the window portion 150, which is not required in the embodiment of FIG. 38.
(99) In both of these examples, there is provided an intermediate actuator position (second short stroke position), such that the selective downhole actuator is transitionable to an actuating position by varying the operating parameters appropriately during the two sequential windows. Indexing the selective downhole actuator 110, 210 to the activating position requiring at least two sequential variations of the operating parameter according to a predetermined pattern, sequence or procedure provides a failsafe or an additional reassurance that the likelihood or risk of undesired indexing towards an actuated actuator state (e.g. of the third actuator position) is reduced. For example, in the event that the pumps temporarily fail or are inadvertently temporarily turned off, or there is an unrelated drop in fluid pressure (e.g. a valve or other restriction opening or closing), then the selective downhole actuator 110, 210 is not necessarily be indexed to an activating position as soon as the fluid pressure is restored, such as due to the re-engagement of the pumps or the reversal of the valve or other restriction.
(100) However, it will be readily be appreciated that other embodiments may comprise no intermediate positions, or more intermediate positions, such that the number of required sequential variations of the operating parameter/s may be predetermined as desired. The number of intermediate positions may be varied by adjusting the slot channel 120, 220 pattern.
(101) FIG. 54 shows an alternative slot channel 320 generally similar to that of the slot channel 220 of FIG. 38, with similar features denoted by similar reference numerals, incremented by 100. Accordingly, the slot channel comprises a primary path 338 and a first intersection 340. As shown here, the direction of fluid pressure force and also of spring bias are the same as FIG. 38 (i.e. the fluid pressure force acts to propel the sleeve or mandrel to the left, whilst the springnot shown hereacts to propel the mandrel or sleeve to the right).
(102) As shown here, the intermediate position corresponds to a different actuator state. Here, the third actuator position corresponds to a first actuation actuator state, such as a long piston stroke position; and the intermediate position corresponds to an intermediate actuating actuator state, such as an intermediate piston stroke position. Accordingly, it may be possible to hold or maintain the selective downhole actuator 310 in an intermediate actuating actuator state, such as when the operating parameter is maintained at a first value. Such a selective downhole actuator 310 may enable the extension or maintenance of a piston at two stroke lengths, such as to provide two active actuating positions or states. For example, such an actuator 310 may enable operations at at least two different operating parameters (e.g. reaming or under-reaming at two or more different diameters). It will be appreciated that the relative axial positions of the intermediate and third actuator positions may be predetermined to provide predetermined axial translations of the sleeve or mandrel in the respective actuation states.
(103) It will be appreciated that, as shown in FIG. 54, the selective downhole actuator 310 is configured to always transition by default to a particular actuation state, whenever subjected to a particular operating parameter condition. Here, the default actuation position comprises a default axial actuation position. It will be appreciated that where a plurality of slot patterns as shown in FIG. 54 are repeated around the circumference of a sleeve or mandrel (e.g. two such slot patterns overlapping and connected, with two corresponding guide pins), then the default actuation position from the intermediate and third actuation positions may be the second actuation position (corresponding to the initial or starting position) of the adjacent slot pattern. Accordingly, the actuator 310 returns to a particular default position of the plurality of default positions dependent upon the actuation position from where the actuator 310 is transitioning under the default conditions. For example, where the actuator 310 is defaulting to a non-actuating state under no flow or low fluid pressure from the first actuation position, the actuator 310 defaults to the second actuation position (the initial or starting position as shown here); and where the actuator 310 is defaulting to a non-actuating state under no flow or low fluid pressure from the intermediate and third actuation positions, the actuator 310 defaults to a further second actuation position, rotationally arranged relative to the initial or starting second position.
(104) FIG. 55 shows a schematic representation of a further toolstring 402 comprising an embodiment of a selective downhole actuator 410. The toolstring schematically shown is generally similar to that of FIG. 1. However, here the actuator 410 is located uphole of the BHA, connected to an upper toolstring portion 411. It will be appreciated that the actuator 410 may be used for the actuation of one or more associated tools or functions (not shown). It will also be appreciated, that the toolstring 402 may comprise a plurality of actuators 410 according to the present invention. In addition, or alternatively, the toolstring 402 may comprise one or more additional actuators (not shown) such as one or more conventional actuators.
(105) FIG. 56 shows a schematic representation of a yet further toolstring 502 comprising an embodiment of a selective downhole actuator 510. Here, the actuator 510 is shown at an intermediate portion of the toolstring 502, between a lower toolstring portion 509 and an upper toolstring portion 511. It will again be appreciated that the actuator 510 may be used for the selective actuation of one or more associated tools or functions (not shown). It will also be appreciated that the toolstring 502 may comprise one or more additional actuators, such as one or more actuators according to the present application and/or conventional actuator/s. For example, the BHA 503 may comprise one or more additional actuators (not shown).
(106) It will be appreciated that the actuator of the present application may find utility in or at various locations along or within a toolstring, such as according to particular functional requirements of particular toolstrings.
(107) It will be apparent to those of skill in the art that the above described embodiments are merely exemplary of the present invention, and that various modifications and improvements may be made thereto, without departing from the scope of the invention. For example, it will also be appreciated that in other embodiments, a toolstring comprises a plurality of selective downhole actuators, each selective downhole actuator being configured to actuate and/or deactuate an associated tool. The window portions and the slot channel patterns of each of the tools may be similar such that the plurality of tools may be actuatable simultaneously according to a similar variation in the operating parameters. Alternatively, the windows and/or the slot patterns may be different such that the respective associated downhole tolls may be actuated according to different predetermined variations in operating parameters. For example, a first actuator may require two re-engagement of pumps within two successive time windows of between two and four minutes; whereas a second actuator may require two re-engagement of pumps within two successive time windows of between six and eight minutes. Accordingly, each of the actuators may be independently actuated in the string. The windows may be varied by providing different damped lengths of return stroke, or different fluids or restrictions in an associated cylinder chamber. Alternatively, two actuators may be provided with identical windows, whereas a first of the two actuators may comprise one intermediate non-actuating short-stroke position, whilst a second of the two actuators may comprise two intermediate non-actuating short-stroke positions. Accordingly, a first tool associated with the first actuator may be actuated by two sequential re-engagements and both the first and a second tool may be actuated by three successive re-engagements of pumps during the windows.
(108) It will be appreciated that any of the aforementioned tools 110, 210 may have other functions in addition to the mentioned functions, and that these functions may be performed by the same tool 110, 210.
(109) Where some of the above apparatus and methods have been described in relation to actuating an underreaming tool 6; it will readily be appreciated that a similar actuator 10, 110, 210 may be for use with other downhole tools, such as for actuating drilling, cleaning, and/or injection tools, or valves or the like.
(110) Where features have been described as downhole or uphole; or proximal or distal with respect to each other, the skilled person will appreciate that such expressions may be interchanged where appropriate. For example, the skilled person will appreciate that where the sleeve or mandrel extends downhole to actuate; in an alternative embodiment, the sleeve or mandrel may be extended uphole to actuate.
(111) The applicant hereby discloses in isolation each individual feature described herein and any combination of two or more such features, to the extent that such features or combinations are capable of being carried out based on the present specification as a whole in the light of the common general knowledge of a person skilled in the art, irrespective of whether such features or combinations of features solve any problems disclosed herein, and without limitation to the scope of the claims. The applicant indicates that aspects of the present invention may consist of any such individual feature or combination of features. In view of the foregoing description it will be evident to a person skilled in the art that various modifications may be made within the scope of the invention.
