BR112019022509B1 - ACTUATOR ASSEMBLY FOR AN OIL, GAS OR WATER WELL, VALVE AND METHOD FOR DRIVING A TOOL FOR AN OIL, GAS OR WATER WELL - Google Patents

Abstract

An oil or gas well actuator assembly comprising a fixed member, an actuating member being axially movable relative to the fixed member, with open-end recesses containing inclined helical springs e.g. in the fixed member, and a shoulder extending radially in the actuating member adapted to engage an inclined coil spring within a recess. A support member is adapted to cover the open ends of the recesses and moves to different axial positions relative to the recesses to uncover the open ends of the different recesses in the different axial positions of the support member. Expanding an inclined coil spring from an open end of a recess engages with the shoulder to restrict movement of the actuating member in indexed positions. When the actuating member moves relative to the direction of the supporting member, it maintains its position relative to the inclined coil spring.

Description

[001] The present invention relates to an actuator assembly, and a method of using it. In some examples, the actuator assembly provides an indexing mechanism configured to adopt a number of separate and different indexed positions. In some examples, the actuator assembly is a downhole actuator assembly and is adapted to be incorporated within a downhole assembly to drive a tool in an oil, gas, or water well.

[002] Downhole tools often need to switch between different configurations in the well, corresponding to different actuation states to control operations in the well. For example, sliding sleeve valves often need to adopt open or closed configurations, or different intermediate positions between 100% open and 100% closed, to control fluid flow through an opening.

SUMMARY

[003] The present invention provides an oil or gas well actuator assembly comprising: a fixed member having a shaft; an actuating member being axially movable with respect to the fixed member; a plurality of open-ended recesses in one of the fixed members and the actuating member wherein each recess at least partially houses an inclined coil spring; a shoulder extending radially over the other of the actuating member and the fixed member adapted to engage a helical spring inclined within a recess; a support member adapted to cover the open ends of the recesses and being axially movable in different axial positions relative to the recesses to uncover open ends of different recesses in the different axial positions of the support member.

[004] Expanding an inclined coil spring from an open end of a recess optionally engages with the shoulder to restrict movement of the actuating member in indexed positions. Movement of the actuating member causes the shoulder to move relative to springs in the recesses and causes the shoulder to engage a spring. Shoulder engagement with a spring in a first recess configuration can resist movement of the shoulder beyond the spring. Engaging the shoulder with a spring in a second configuration may allow movement of the shoulder beyond the spring. Movement of the actuating member can invert the springs between the first and second settings.

[005] The open end cover of a recess optionally resists changes in the configuration of the inclined coil spring within the recess. The optional open end cover maintains compression of the spring in the recess, which resists changes in the orientation of the spring within the recess, keeping it in the same orientation while the open end of the recess is covered. Uncovering the open end of the recess optionally allows changes in the configuration and/or orientation of the inclined coil spring within the recess. In certain examples, the open ends of the recess may be covered by the supporting member or the actuating member. Covering the open end of a recess optionally maintains a minimum level of spring compression within the recess, and uncovering the open end of a recess optionally allows expansion of the spring from the recess.

[006] The change of configuration of the spring in the recess when the open end is uncovered optionally occurs in response to movement of the actuating member or support member relative to the open end, optionally movement through the open end. Optionally, each inclined coil spring is resiliently energized upon compression within the recess. One end of the energized inclined coil spring is resiliently flexed out of the recess, and at least a portion of the inclined coil spring projects out of the recess to engage the shoulder and stop movement of the actuating member when the shoulder and spring engage, optionally in an indexed position. Optionally the actuation assembly has several indexed positions, optionally equal to the number of recesses, in which the axial movement of the actuation member is stopped at sequential indexed positions between a starting position of the actuating member and an end position of the actuating member corresponding to a functional change, for example, opening a valve, activating a tool, etc.

[007] In different positions of the support member in some examples, the open ends of some recesses are uncovered, and the open ends of other recesses are covered.

[008] Optionally the support member, the fixed member and the actuation member are concentric.

[009] Optionally each recess is symmetrical about a radius of the axis of the fixed member (the radius extends perpendicular to the axis of the fixed member). Optionally, each recess has first and second side walls axially spaced on both axial sides of the open end. Optionally the side walls are mutually parallel and also parallel to the radius. Optionally each recess has a square profile with a bottom wall disposed axially between the side walls at the inner end of the recess.

[0010] Optionally, each inclined coil spring is energized, for example, compressed when the open (outer) end of the recess containing the inclined coil spring is covered, optionally by the supporting member or the actuating member. Optionally, each turn in each spring naturally adopts an elliptical configuration having a major axis and a minor axis. Each turn of each spring is optionally angled relative to the centerline of the spring.

[0011] In cross section through its center line, each inclined helical spring optionally has an elliptical configuration having a major axis and a minor axis. Optionally movement of the shoulder past the spring in the recess is resisted when the spring is compressed by the shoulder in the recess along its major axis.

[0012] Optionally when energized for example in compression within the recess, with the open end of the recess covered, each inclined helical spring adopts an elliptical configuration with the main axis of each spring being inclined to the long axis of the hole (i.e. not parallel with the axis of the member fixed) when the recess is covered, and when energized, the configuration of the spring in the recess is optionally non-symmetrical about a radius perpendicular to the axis. Optionally, each spring may adopt a energized elliptical configuration with the main axis inclined at one axis radius. In other words, two alternative energized (e.g., compressed) elliptical configurations of each spring are possible in each recess, with the main axis of the inclined springs being tilted in one direction (i.e., /) or in the opposite direction (i.e., \) through the axis radius. Optionally, when in the inclined (optionally compressed) configuration in the recess, the major axis of the spring is parallel to or aligned with a diagonal of the recess, between opposite corners of the recess, and the minor axis of the spring is parallel to (but not necessarily aligned with) ) diagonally opposite the recess. Optionally in the two alternative compressed configurations of each spring, the main axis is parallel or aligned with different diagonals of the recess.

[0013] Optionally, when the spring is in a rest or neutral configuration (i.e., not in compression), it naturally adopts an elliptical shape within the recess and is optionally symmetrical about a radius. Optionally in the neutral configuration, the length of the spring along the main axis is greater than the distance along a diagonal of the recess, i.e. between the diagonally opposite corners of the recess, so that in the rest and uncompressed configuration, the spring does not fits completely within the recess, and one end of the main shaft of the spring will project normally from the open end of the recess. In such examples, to fit into the recesses, the spring is optionally resiliently compressed in the recess, for example when the open end is covered, which stores energy in the spring, and this optionally forces the spring to adopt an inclined compressed configuration in the recess. with the main axis of the spring aligned with the diagonal. Thus the spring may optionally resiliently expand through the open end of the recess, for example once the compressive force acting thereon has been removed, for example when the open end of the recess is uncovered.

[0014] In some examples, the spring is stronger and allows greater flexibility along its minor axis than along its main axis.

[0015] The springs optionally have an inner end (further into the recess, and normally engaged with the inner end of the recess) and an outer end (closer to the open end of the recess than the inner end of the spring). Optionally the outer ends of the springs are driven toward and optionally away from the open ends of the recesses by the resilience of the spring when the spring is energized (i.e., when the open end of the recess is covered).

[0016] Optionally in a first inclined configuration of the springs, the outer end of each spring faces axially towards the shoulder; in other words, the outer end of the spring at the open end of the recess is axially closer to the shoulder than the inner end of the spring at the inner end of the recess when the distance between the shoulder and the spring is decreasing. Thus, when the shoulder approaches a recess (or vice versa) containing a spring in the first inclined configuration, the outer end of the spring is axially spaced closer to the shoulder than the opposite inner end of the spring. The inner end of the spring is disposed in the recess, while the outer end of the spring is adjacent to the open end of the recess or protrudes from the recess through the open end. Optionally, once the shoulder reaches the recess containing the spring in the first inclined configuration, the shoulder initially engages the outer end of the spring resiliently flexed out of the recess. Because the spring is relatively resistant to further compression along its major axis, engagement of the shoulder with the outer end of the spring in the first configuration can be used to resist axial movement of the shoulder in a first direction (e.g., in the direction of action of the member that supports the shoulder). In the first inclined configuration, the inner end of the spring main shaft is optionally disposed in an inner corner of the recess, optionally between the bottom wall and the side wall in front of the shoulder, and the outer end of the spring main shaft is optionally projecting the from recess in front of the shoulder that moves toward it in the first direction toward a final drive position. Obviously, it is not essential that the shoulder moves and the recess remains motionless. In some examples, the shoulder may be static and recesses may be provided in the actuating member; thus references here to the shoulder moving relative to the recess or spring are understood to apply also to examples in which the shoulder is static relative to the fixed member and the recess and spring move relative to the shoulder, and vice versa. verse.

[0017] As the shoulder and the recess approach each other while the actuating member is moving in the initial direction, the shoulder engages with the outer end of the main spring shaft protruding from the recess in front of the shoulder. Thus, optionally, in the first configuration the major axis of the spring is pointing generally towards the shoulder, and the minor axis of the spring is pointing generally away from the shoulder, optionally in an axial direction. The spring is relatively resistant to deformation along the main axis, which is generally parallel to the diagonal of the recess in the first inclined configuration, so when the shoulder engages the outer end of the spring's main axis pushing out of the recess, the spring does not deform. it compresses much more in the recess and resists further movement of the shoulder (and therefore the limb carrying it) in the first direction (e.g. towards the trigger position). Because the inner end of the spring is trapped in the recess in front of the shoulder, for example at the corner, the spring remains in the first inclined configuration and cannot easily move in the recess or change within the recess to allow greater deformation in a different configuration. The high resistance to deformation along the main axis of the spring retained in the recess therefore prevents or restricts movement of the shoulder in the first direction after the point at which the shoulder engages the outer end of the spring. At this point the actuating member can withdraw in the second opposite direction in the hole, but cannot advance in such a way that the shoulder moves beyond the groove without interrupting the spring within the groove beyond the limits of plastic deformation.

[0018] Optionally a second energized alternating configuration of the spring allows axial movement of the actuation member after the spring, for example in the same first direction. The first and second configurations are similar except that the spring is usually parallel to the opposite diagonals in the recess. Thus, whereas in the first configuration, the spring is generally parallel with or aligned with one diagonal, in the second configuration, the spring is generally parallel with or aligned with the other diagonal of the recess. Thus in the second configuration, while the inner end of the main spring shaft is still disposed in the recess, it is axially closer to the shoulder than the outer end, and while the outer end of the main spring shaft is still projecting from the recess, it is axially further from the shoulder than from the inner end. Thus, optionally, in the second configuration the major axis of the spring is pointing away from the shoulder, and the minor axis of the spring is generally pointing toward the shoulder. Since the minor axis of the spring is more compressible than the major axis, forward movement of the shoulder against a posterior face of the outer end of the spring compresses the spring in the recess applying force along the more deformable minor axis, deforming the spring more toward within the recess along its minor axis, and allowing passage of the shoulder beyond the recessed and compressed spring.

[0019] Optionally, in a rest or neutral configuration of the spring, when the main axis of the spring is not substantially inclined through the axis of the hole and the spring is expanded partially in the hole and out of the recess, optionally in a configuration generally symmetrical to the around a radius of the hole, the spring can be moved, for example rotated, in the recess between the two different energized inclined configurations by moving the actuating member (or the supporting member) axially within the hole in each direction. Optionally the spring passes through the neutral position when moving between the two alternative compressed and inclined configurations.

[0020] Optionally, recesses are provided on the inner surface of the fixed member. Optionally, recesses are provided in an inner surface of a housing sleeve, which is received within the fixed member, which may comprise a housing. Optionally, the inner surface of the housing sleeve forms at least a portion of the hole within the housing that receives the actuation member. In other words, the actuating member can be received within the bore of the housing sleeve, and can move axially therein between separate positions of the actuating member.

[0021] Optionally the springs allow movement of the shoulder beyond the recesses and springs in a second direction in one of the first and second configurations. In other words, the shoulder and spring optionally form a unidirectional stop, stopping movement of the actuating member in only one direction (the first direction) when the spring is in the first setting.

[0022] Optionally, the housing sleeve also receives the support member, which is movable within the bore of the housing sleeve between separate positions in response to movement of the actuation member. The provision of recesses in the inner surface of the housing sleeve is useful for construction and assembly of the actuator assembly, and allows different hole sizes, and different sizes of inclined coil springs, to be used with a single housing, but it is obviously possible form the recesses on the inner surface of the housing without necessarily employing a sleeve.

[0023] Optionally, the support member comprises a sleeve, having a hole with an axis that is optionally coaxial with the axis of the housing. The support member optionally allows fluid communication axially from one side of the support member to the other, optionally through the hole. Optionally, the actuating member may be moved between different positions in response to changes in the fluid pressure differential across the actuating member, which may be transmitted through the supporting member (optionally through the bore or some other fluid conduit). .

[0024] Optionally, the actuating member may comprise a piston, which may be sealed within a bore of the housing, optionally at a location spaced from the recesses. Optionally, the piston has more than one seal, dividing portions of the hole into different zones between the seals. Optionally, different axial positions adopted by the actuating member within the hole actuate different configurations of a tool connected to the actuator assembly and under its control. Optionally, separate positions of the actuation member correspond to separate actuation states of the downhole tool. For example, in one example, the actuating member may itself comprise a tool part, e.g. a component of a sliding sleeve valve system, which slides axially within the housing to move respective openings in the actuating member and the fixed member in and out of alignment, and optionally to vary the extent of overlap of such openings in order to control the cross-sectional area of a fluid conduit allowing radial movement of fluid through the walls of the actuating member and the fixed member . Optionally, the different axial positions may represent intermediate indexing positions that do not trigger individual changes depending on a tool, for example the opening of a valve or the like, but which individually advance the tool towards a configuration change. Thus, sequential changes in the differential pressure applied to the assembly can move the assembly through intermediate transition positions before a final actuation step.

[0025] Optionally recesses are provided in the actuation member. Optionally the supporting member comprises a sleeve that receives the actuating member. Optionally the support member moves over the surface of the actuating member. Optionally the movement of the support member over the actuating member is limited by the fixed member.

[0026] Finally at least two inclined helical springs each in a respective recess are provided, but the number of springs and recesses may vary in different examples.

[0027] Optionally, the actuating member may be axially flexed in one direction by a resilient biasing device, such as a spring, for example a helical spring, which may optionally be held in compression. Movement of the actuating member between separate positions relative to the fixed member may optionally be actuated by controlling a fluid pressure differential that opposes the force of the biasing device. For example, the biasing device may influence the actuating member axially in one direction, and a fluid pressure differential may influence the actuating member in the opposite direction, in order to resist movement of the actuating member by balancing the force applied by the polarization device. Reducing the fluid pressure on one side of the actuation member may result in movement of the actuation member under the force applied by the biasing device, which overcomes the lower pressure differential to move the actuation member axially. Increasing the fluid pressure in the actuating member can overcome the spring force and move the actuating member in the opposite direction, compressing the spring.

[0028] Optionally the support member moves relative to the spring in response to movement of the actuation member. Optionally, the actuating member pushes the supporting member between their separate positions. Optionally, the support member is held static relative to the fixed member as the actuating member moves relative to the support member, resulting in movement of the support member relative to the spring. Optionally the acting member is led through the support member. Optionally the support member moves in only one direction relative to the spring. Optionally when the actuating member moves relative to the supporting member in one direction, the supporting member maintains its position relative to the spring. Optionally when the actuating member moves relative to the support member in the other direction, the support member moves relative to the spring.

[0029] Optionally, axial movement of the actuation member in a first direction moves the support member in the same first direction, so that the support member moves with the actuation member in the first direction. However, in certain examples, the supporting member optionally moves with the acting member only in the first direction, and when the acting member moves in a second direction, opposite to the first direction, the acting member and the supporting member support member optionally separate, with the support member optionally remaining static and maintaining its position, while the actuating member moves axially away from the support member in the second direction.

[0030] Optionally, the support member may be centered within the assembly, for example, by a centering section of the support member being received within or by a portion of the assembly (e.g., a hole) with close tolerance and with sides parallels. Optionally, the centering section of the support member is disposed at one end of the support member, and normally does not engage or support any of the springs housed in the recesses. Optionally the centering section of the support member has a wider diameter than a spring support section of the support member that is axially spaced from the centering section of the support member along its axis. Optionally the springs expand radially from the recesses and engage the spring support section through the open ends of the recesses. Optionally, the spring support section of the support member engages the springs and supports them in the recesses, maintaining their compressed configuration within the recess.

[0031] Optionally, the shoulder supporting member is also adapted to engage the inclined helical springs within the recesses and to support, and optionally, energize them within the recesses. Optionally, the shoulder supporting member has a spring support section, optionally in its outer diameter, adapted to support and engage the springs within the recesses.

[0032] Optionally the member supporting the shoulder (e.g., the actuating member) is also adapted to be centered within the assembly, for example by a centering section of the actuating member being received within a hole section with tolerance close and with parallel sides. Optionally, the centering section is arranged at one end of the member, and normally does not engage with any spring supports housed in the recesses. The centering section may comprise spaced shoulders.

[0033] Optionally the member supporting the shoulder has several different sections arranged sequentially along its length with different diameters. The centering section is optionally disposed at one end and may incorporate a seal between the shoulders. The diameter of the member optionally passes through a ramp that coincides with a radial expansion space between the fixed member and the shoulder actuating member that optionally fits with a close tolerance against the recessed part of the assembly, optionally the inner surface of the sleeve. of accommodation. The shoulder optionally extends radially relative to the assembly body axis, engaging the recessed portion in a tight fit. The shoulder optionally divides the ramp coinciding with the expansion area and a spring support section of the member which is optionally disposed at one end of the member supporting the shoulder. Optionally the spring support section has a different diameter so that its surface is radially separated by a small distance from the recessed part, so that the springs can expand radially out of the recesses through the small radial distance, and engage the section spring support. Optionally, the spring support section of the shoulder supporting member engages the springs and supports them within the recesses and allows slight limited expansion of the springs outside the confines of the recess, yet maintains a small amount of compression on the springs so that there is optionally a gap between the recessed portion and the spring support section of the actuating member.

[0034] Moving the shoulder-supporting member through the free ends of the recesses may optionally displace the springs between the first and second inclined positions in the recesses, optionally when the shoulder-supporting member is moved through the free ends of the recesses first in a direction and then in the opposite direction. Changing the springs between different first and second inclined positions, optionally from a first position in which the spring engages with the member supporting the shoulder and resists passage of the shoulder past the recess, to a second configuration in which the spring engages with the actuating member and allows the shoulder to pass beyond the recess holding the spring, can be used to stop the movement of the actuating member at defined positions, for example when the shoulder reaches a limit of a recess, and control more precisely the stopping locations of the acting member in relation to the fixed member.

[0035] Optionally a spring in the second configuration can resist the passage of the shoulder in the second direction. Optionally, the shoulder has a first and second face, optionally facing opposite directions. Optionally each of the first and second faces is adapted to engage with a spring in one of the first and second configurations to lock movement of the actuating member in a first or a second direction. Optionally the first face of the shoulder is adapted to engage with a spring in a first configuration to lock movement of the actuating member in a first direction. Optionally the second face of the shoulder is adapted to engage with a spring in a second configuration to lock movement of the actuating member in a second direction.

[0036] Optionally the shoulder maintains a second spring configuration while the spring is in contact with the shoulder. Optionally, the shoulder has a profiled region that engages the spring and maintains it in the second configuration. Optionally the spring maintained in the second configuration by the shoulder resists the passage of the shoulder (e.g., the second face of the shoulder) past said spring in the second configuration when the shoulder is moving in the second direction.

[0037] Optionally, the assembly comprises an axial fluid flow path through the housing. This optionally connects a flow path on the first side of the assembly to a flow path on the second side of the assembly. Thus the assembly can optionally connect in-line with a fluid conduit in a piping string, for example. Optionally, the assembly may be used to obstruct fluid flow from the fluid flow path to an external surface of the assembly, for example, to a ring between the assembly and an internal surface of the wellbore. This example is useful for circulation tools for example.

[0038] The invention also provides a method of actuating a tool for an oil, gas or water well, the tool having an actuator assembly comprising: a fixed member having an axis; an actuating member axially movable with respect to the fixed member; a plurality of open-ended recesses in one of the fixed members and the actuating member wherein each recess at least partially houses an inclined coil spring; a shoulder extending radially the other of the actuating member and the fixed member adapted to engage a helical spring inclined within a recess; a support member adapted to cover the open ends of the recesses and to be axially movable in different axial positions relative to the recesses; wherein the method includes: moving the actuating member axially relative to the fixed member; moving the support member beyond at least a portion of an open end of a recess housing an inclined coil spring; and restricting axial movement of the actuating member by engaging the shoulder with at least a portion of the inclined coil spring extending from the open end of the recess.

[0039] The invention also provides a valve comprising an actuator assembly as defined herein. Certain valves in accordance with the present disclosure can be reset to a closed position from any index position of the sleeve, without necessarily having to cycle through all indexed positions, which can save time when closing the sleeve, which is especially significant in closure case to restrict an uncontrolled release of hydrocarbons. Certain valves also allow a confirmed signature that the sleeve is fully closed compared to a cyclic sleeve which depends on the operator's known position of the sleeve.

[0040] The various aspects of the present invention can be practiced alone or in combination with one or more of the other aspects, as will be appreciated by those skilled in the art. The various aspects of the invention may optionally be provided in combination with one or more of the optional features of the other aspects of the invention. Furthermore, optional features described in relation to one aspect may typically be combined alone or together with other features in different aspects of the invention. Any matter described in this specification may be combined with any other matter in the specification to form a new combination.

[0041] Various aspects of the invention will now be described in detail with reference to the attached figures. Still other aspects, features and advantages of the present invention are readily apparent from the entire description thereof, including the figures, which illustrate various aspects and exemplary implementations. The invention is also capable of other and different examples and aspects, and its various details can be modified in various aspects, all without departing from the scope of the present invention. Accordingly, each example herein should be understood as having broad application and should illustrate a possible way of carrying out the invention, without intending to suggest that the scope of this disclosure, including the claims, is limited to that example. Furthermore, the terminology and phraseology used herein are used for descriptive purposes only and should not be construed as limiting in scope. In particular, unless otherwise indicated, the dimensions and numerical values included herein are presented as examples illustrating a possible aspect of the claimed object, without limiting the disclosure to the particular dimensions or values recited. All numerical values in this disclosure are understood to be modified by "about". All singular forms of elements, or any other components described here, are understood as plural forms thereof and vice versa.

[0042] Language such as "including", "comprising", "having", "containing", or "involving" and variations thereof, must be broad and encompass the material listed later, equivalents and additional non-recited material, and not be intended to exclude other additives, components, integers, or steps. Likewise, the term "comprising" is considered synonymous with the terms "including" or "containing" for applicable legal purposes. Accordingly, throughout the Descriptive Report and Claims, unless the context otherwise requires, the word "comprise" or variations thereof such as "comprises" or "comprising" will be understood to imply the inclusion of an integer or group of whole numbers, but not to the exclusion of any other whole number or group of whole numbers.

[0043] Any discussion of documents, acts, materials, devices, articles and the like is included in the specification solely for the purpose of providing a context for the present invention. It is not suggested or represented that any or all of these matters formed part of the basis of the prior art or were common general knowledge in the field relevant to the present invention.

[0044] In this disclosure, whenever a composition, an element or a group of elements is preceded by the transitional phrase "comprising", it is understood that we also contemplate the same composition, element or group of elements with transitional phrases "consisting essentially of" , "consisting of", "selected from the group consisting of", "including", or "is" preceding the recitation of the composition, element or group of elements and vice versa. In the present disclosure, the words "typically" or "optionally" are to be understood as being intended to indicate optional or non-essential features of the invention which are present in certain examples, but which may be omitted in others without departing from the scope of the invention. .

[0045] References to directional and positional descriptions, such as top and bottom and directions, for example "up", "down", "left", "right" etc. should be interpreted by one skilled in the art in the context of the examples described to refer to the orientation of the features shown in the drawings, and should not be interpreted as limiting the invention to the literal interpretation of the term, but should be understood by the person skilled in the art. In particular, positional references in relation to the well such as “up” and similar terms will be interpreted to refer to a direction toward the well's entry point into the ground or seabed, and terms “down” and similar terms will be interpreted to refer to a direction away from the entry point, whether the well referred to is a conventional vertical well or a deviated well.

BRIEF DESCRIPTION OF THE DRAWINGS

[0046] In the accompanying drawings: Figure 1 shows a sectional view through an actuator assembly; Figures 2-11 show enlarged views of the arrangement of Fig. 1 in sequential actuation positions; Figure 12 shows a cross-sectional view through the actuation assembly of Figure 1 in the position of Figure 11; Figure 13 shows an enlarged sectional view through a recess with an inclined helical spring; Figure 14 shows an enlarged sectional view of a piston head in the assembly of Figure 1; Figures 15-18 show a second example of an actuator assembly in sequential actuation positions; Figures 19-22 show enlarged views of the interaction of the shoulder and springs in the second example; Figures 23-26 show a third example of an actuator assembly in sequential actuation positions; Figures 27-30 show enlarged views of the interaction of the shoulder and springs in the third example; Figures 31-37 show a fourth example of an actuator assembly in sequential actuation positions; Figures 38-44 show enlarged views of Figures 31-37; Figures 45 and 46 show enlarged views of the interaction of the shoulder and springs in Figures 32 and 36, respectively; Figures 47-50 show enlarged views of a fifth example of an actuator assembly in sequential actuation positions; Figure 51 shows the fifth example of Figures 47-50; and Figure 52 shows a close-up view of the interaction of the shoulder and springs in Fig 49.

DETAILED DESCRIPTION

[0047] Referring now to the drawings, an actuator assembly in the form of a valve 1 is shown in the figures in cross section. The valve 1 has a fixed member in the form of a housing 10, with a tubular bore 10b which receives an actuating member in this example taking the form of a piston 30 comprising a solid rod which is centered within the bore 10b. The piston 30 is sealed in the bore 10b by means of seals in order to selectively isolate the respective sections of the bore. Hole 10b has an inner end (shown on the right side of figure 1 and figure 12), having a narrow inner diameter (ID), a center section 10c, having an ID slightly larger than the inner section, and an outer section, which is drilled with an additional ID step on the outer end of valve 1 (shown on the left side of figure 1 and figure 12). The gradual increase in hole ID between the inner and center sections, and between the center and outer sections of hole 10b takes the form of shoulders facing the outer end of hole 10b. In the central section, the piston 30 is sealed to the inner surface of the bore 10b by means of seals 34a, 34b, 34c, which may optionally comprise elastomeric Oring seals or the like.

[0048] The piston 30 has an inner section, a central section and a head, arranged sequentially along the piston 30 and with different diameters. The inner section of the piston comprises a narrow shaft which is received within the narrow inner section of bore 10b. The narrow shaft of the inner section of the piston 30 is retained by an end cap 36, and a biasing device in the form of a resilient piston drive spring 35 is held in compression between a shoulder 30s on the piston 30, and the outer opposite face of end cap 36. End cap 36 abuts against an outwardly facing shoulder in hole 10b, in the step between the inner and central sections of the hole. The spring 35 is thus held in compression around the narrow end of the piston shaft 30 and tilts the piston out of the bore 10b towards its outer section. The axial movement of the piston 30 within the bore is driven by fluid pressure generated by a pump (not shown) outside the bore 10b which increases the pressure within the bore 10b on the outside of the seals 34, to overcome the force of the spring 35 and cause the piston 30 to withdraw into the hole 10b, compressing the spring 35 as it does so. The movement of the piston in the reverse direction is controlled by balancing the pressure acting on the seals 34. When the pressure is balanced against the force of the spring 35, the piston remains static. When the fluid pressure force is greater than the spring force 35, the piston 30 withdraws into the hole 10b under the fluid pressure force. When the fluid pressure force is less than the spring force 35, the piston is expelled from the hole by the spring force.

[0049] Seals 34 are retained in the shoulders on piston 30 extending radially outward toward the inner surface of bore 10b. When the seals 34 are compressed between the two surfaces, this seals the zones between the adjacent seals 34. The housing has an inlet 12 and an outlet 13 passing radially from the outer surface of the housing 10 and opening to the inner surface of the bore 10b in the central section. In the inlet 12 and outlet 13 openings in hole 10b, the inner wall of hole 10b has a respective annular groove 12g, 13g machined circumferentially around the inner surface of hole 10b, so that in these sections of the center section hole, the diameter inside the hole is larger than in the adjacent sections, and therefore is not constant. In grooves 12g, 13g, the inner wall of hole 10b gradually tapers radially outward at an angle towards the opening of inlet 12 and outlet 13 in hole 10b.

[0050] When the seals 34 carried on the piston 30 are compressed between the inner surface of the bore 10b and the outer surface of the piston 30 at positions axially apart from the annular grooves 12g, 13g around the inlet 12 and outlet 13, the seals 34 are radially compressed and resist fluid flow past the seals 34 in the ring. This isolates the various zones between the seals, and this configuration is shown in Fig 1. However, when the piston 30 slides axially within the bore 10b to a position where a seal, for example seal 34b, moves axially in the annular groove 12g around inlet 12, seal 34b is no longer compressed between the larger diameter inner surface of hole 10b and the outer surface of piston 30, and no longer presents a barrier to fluid flow after sealing. Therefore, fluid flowing through inlet 12 can flow past the unloaded seal 34b in the ring in each direction. Thus, the axial movement of the piston 30 within the hole 10b can open and close the fluid communication between the inlet 12 and outlet 13 by moving the seals 34 in and out of the grooves 12g, 13g. Figure 1 shows a configuration in which the inlet 12 is sealed by seals 34a and 34b on both sides, and the outlet 13 is sealed by seals 34b and 34c on both sides; whereas in the configuration of figure 12, seals 34a and 34c are engaged and resist the flow of fluid passing through these seals on the outer and inner sides of inlet and outlet 12, 13, but seal 34b is axially aligned with groove 12g, and is spaced radially from the inner surface of the hole 10b, and is therefore not compressed against the wall of the hole, and presents no barrier to the passage of fluid, allowing fluid from the inlet 12 to flow through the opening in the groove 12g, and through the ring between the piston 30 and the inner surface of the bore 10b, to the outlet 13 as shown by the arrows in figure 12. Note that the seals 34a and 34c at opposite ends of the piston 30 still maintain pressure integrity within the center section of the bore 10b when seal 34b is discharged.

[0051] As will be described below, this example provides an indexing mechanism to control and index movement between the closed configuration of Figure 1 where input 12 is isolated from output 13, to the open configuration of Figure 12, where input 12 is connected to outlet 13 allowing fluid flow between the two.

[0052] As best shown in figure 14, the outer end of the piston 30 has a head 30h with an outer diameter larger than the central section of the piston 30. The outer diameter of the piston 30 transitions from the central section to the head through a ramp 33, which is inclined at an angle to the 30° outer end of the piston 30. The head 30h has a plateau section with a relatively consistent outer diameter before tapering radially inward at a steep angle at the shoulder 31 to a cylindrical nose 32 , which has a smaller outer diameter, intermediate between the outer head plate 30h and the piston center section 30. The angle at the outer shoulder 31 between the flat section of the plateau and the angled front face leading to the nose 32 is steep, and in some examples, it may be substantially perpendicular to the axis of the piston. In this example, the angled face between the nose 32 and the plateau is at least (in this example) 50-55° relative to the piston axis, and the ramped face 33 on the other side of the plateau section between the plateau section and the center section of the piston are at most (in this example) approximately 45-50°, presenting a shallower angle on the inner face of the plateau than on the outer face for reasons that will be described below. It will be understood that dimensions and angles may vary in other examples.

[0053] Housing 10 at its outer end receives within the wide diameter section with counter-hole a housing sleeve 11, with a central hole 11b, best seen in figure 8 and figure 10, which is received with a close tolerance within the outer counterbore section of hole 10b, and which is held in place by a locking sleeve with an external thread on its outer surface that engages with an internal thread in the large diameter counterbore section at the outer end of the hole 10b, thereby keeping the housing sleeve 11 compressed between the inner end of the locking sleeve and an outwardly facing shoulder on the housing 10. In this configuration, the housing sleeve 11 essentially continues the inner surface of the bore 10b of the housing 10 which can be Replaced as necessary by unscrewing the locking sleeve. The locking sleeve has a central hole coaxial with the hole 11b of the housing sleeve 11, so that the hole 10b continues through the locking sleeve and the housing sleeve 11.

[0054] The inner surface of the housing sleeve 11 has a plurality of recesses in the form of circumferential annular grooves 20, best seen in figure 13, which are parallel to each other and which extend circumferentially around the entire inner surface of the hole 11b . Each groove 20 has a bottom wall 21 that extends axially between the radially and parallel arranged inner and outer side walls 22, 23, to form a generally square arrangement, optionally with rounded corners between the bottom wall 21 and the side walls 22, 23 Each slot 20 is open in the hole 11b of the housing sleeve 11 at an open inner end of the slot 20. In this example, the side walls 22, 23 are parallel and are perpendicular to the bottom wall 21, which is parallel to the axis of the hole. but in other examples this geometry can be varied. In this example, the corners between the side walls 22, 23 and the bottom wall 21 are rounded, but again, this detail may vary in other examples. Each groove is symmetrical about a radius of the hole (the radius extends perpendicular to the axis of the hole). Each groove has two alternative diagonals between opposite corners. In this example, all slots have the same geometry.

[0055] Each groove 20 retains an alloy-type helical spring in the form of an inclined helical spring 40, best seen in figure 13. Inclined helical springs 40 are known to those skilled in the art, and are available from, among others, Bal Seal Engineering Inc. Suitable examples of coil springs are disclosed in US4655462, US4826144, US4876781 and US4964204, the disclosures of which are incorporated herein by reference.

[0056] Each spring 40 in this example is naturally wound in an elliptical configuration with a cross section through the spring having a 40x major axis and a minor axis that is perpendicular to the 40x major axis, as best shown in Fig 13, which shows the spring 40 in its resting configuration, expanding slightly outward from the open end of the recess 20 since the main axis 40x of the spring 40 in the resting configuration is longer than the side walls 22, 23 and the diagonals between the opposing corners of the recess 20. In the rest configuration shown in Fig 13, the spring 40 is generally symmetrical about the hole axis, although it naturally adopts the elliptical configuration with the major axis 40x and the minor axis perpendicular thereto. Spring 40 is more resilient and allows greater flexion along its minor axis than along its 40x major axis. In order to fit within the groove 20, the spring 40 is resiliently compressed, which stores energy in the spring 40, and causes the spring 40 to expand elastically through the open end of the groove 20, e.g. since the force compression acting on it has been removed.

[0057] Each inclined helical spring 40 can therefore be energized in compression within its groove 20 (as shown in Fig 1). When the spring 40 is compressed in the recess and is energized, i.e. when the open end of the recess is covered, it may adopt one of two alternative elliptical configurations with the main axis 40x of the spring 40 inclined on the long axis of the hole (i.e. not parallel to the axis of the hole) at an angle between 0 and 90 degrees relative to the hole when the recess is covered, therefore in each of the two alternative energized configurations, the main axis 40x of the spring 40 is generally aligned with one of the two diagonals of the recess connecting the opposite inner and outer corners of the recess. See for example the arrangement of springs 40a and 40b in Figure 4, which are adopting alternative and different compressed configurations within their grooves 20, in general (but not necessarily exact) alignment with the two alternative diagonals of the grooves 20. The movement of the actuation member can displace the springs 40 between different configurations as will be described below.

[0058] The inner hole 11b of the housing sleeve 11 is very slightly smaller in ID than the inner hole of the locking sleeve immediately adjacent to it at its outer end and holding the housing sleeve 11 in place within the outer section of the hole 10b. The housing sleeve hole 11b and the locking sleeve hole accommodate a support member which is optionally separate from the actuation member and in this example is optionally in the form of a support sleeve 50 which is cylindrical and is axially movable within the hole. 10b between separate positions. The support sleeve 50 has a central hole 50b allowing the passage of fluid through the support sleeve 50. The support sleeve 50 is divided into two sections with a common internal diameter but different external diameters: i.e. an internal section that has a relatively narrow OD that can fit into the hole 11b of the housing sleeve 11; and an outer section, which has a larger OD that cannot fit into hole 11b of the housing sleeve, but can be received inside and can translate axially through the slightly larger hole of the locking sleeve. The outer section of the support sleeve 50 fits with close tolerance into the hole of the locking sleeve, and this centers the support sleeve 50 within the hole 11b of the housing sleeve, so that the sleeves 50, 11 and the locking sleeve locking are all coaxial with axis 10x of hole 10b. When the inner section of the support sleeve 50 is located in the hole 11b of the housing sleeve 11, the springs 40 expand radially within the grooves 20 and engage the outer surface of the inner section of the support sleeve 50, which supports the springs 40 in of the grooves 20 and maintains its compressed configurations within the grooves 20. As the inner section of the support sleeve 50 moves axially within the hole 11b of the housing sleeve toward the outer end of the hole 10b, the support sleeve moves through opposite ends of each of the slots 20, uncovering them in sequence as it translates axially through hole 11b in the first right-to-left direction in the drawings. The OD of the inner section of the support sleeve 50 and the ID of the housing sleeve 11 are very close, with close tolerance. Passage of support sleeve 50 into hole 11b from left to right in the drawings covers the open inner ends of slots 20 in sequence as it moves into hole 11b, and uncovers them in reverse sequence as it withdraws from the hole 11b from right to left. Thus, at different positions of the support sleeve 50, the open ends of some grooves 20 are covered, and the open ends of other grooves 20 are uncovered.

[0059] Uncovering the open end of a groove 20 accommodating a spring 40 allows expansion of an outer end of the inclined helical spring 40 out of the groove 20 as the groove 20 is uncovered, which in this example may allow a change in configuration of spring 40 in groove 20. The change in spring configuration may occur in response to movement of piston 30 or support sleeve 50. Each inclined helical spring 40 is resiliently held in compression within groove 20, and upon discovery the open end of a groove 20 the inclined coil spring 40 expands and at least a portion of the outer end of the inclined coil spring 40 projects out of the groove 20.

[0060] The support sleeve 50 in this example is movable in each axial direction within the hole 10b, and the axial position of the support sleeve 50 within the hole 10b is optionally maintained by friction. Optionally, some of the friction holding the support sleeve 50 in place within the hole arises by drag between the inner surface of the locking sleeve abutting the outer surface of the larger diameter outer section of the support sleeve 50, but optionally the friction arises primarily by the ends of the springs extending outward from the grooves 20 in the housing sleeve 11 abutting the outer surface of the inner section of the support sleeve 50 and retarding or resisting its axial movement relative to the springs. Therefore, the axial force applied to the support sleeve 50 that overcomes friction may cause the support sleeve 50 to translate axially relative to the grooves 20. Optionally, the friction generated between the springs and the support sleeve may be increased by several ways, for example, by roughening the surface of the support sleeve, or facing them with high friction coatings, or creating formations on the surface of the support sleeve such as annular grooves for engaging the ends of springs expanding out of the recesses. Moving the springs out of engagement with the annular grooves requires additional axial force to be applied to the support sleeve. Frictional retardation of the movement of the support sleeve relative to the springs can be helpful in resisting movement resulting from normal vibration in use.

[0061] To configure the assembly for actuation, the support sleeve 50 is initially pressed into the hole 10b in the second direction, from left to right in the drawings, so that the inner section of the support sleeve 50 moves through the hole 11b from the outside of the hole (left side in the drawings) to the inside of the hole (right side in the drawings) until the inner end of the inner section of the support sleeve 50 abuts the outer 30° face of the piston 30 as shown in Fig 1 and Fig 2. Upon reaching this configuration, the OD of support sleeve 50 has moved from left to right across all open ends of grooves 20 housing springs 40d, 40c and 40b. This has moved the protruding outer ends of springs 40d, 40c and 40d towards the inner end of the hole so that as they compress within their respective grooves 20 they adopt the first compressed inclined configurations shown in Fig. 1 generally aligned with a diagonal, with its outer ends pushing outward from the groove 20 furthest from the outer end of the hole 10b and closest to the shoulder 31 (and facing it in an axial direction), while the inner ends are secured in a corner of the inner end of the groove, closer to the outer end of the hole 10b and further away from the shoulder 31 than the outer ends of the springs. Since the movement of the support sleeve 50 from left to right (the second direction) is pressing the springs along their minor axes rather than their major axes, they compress in the grooves 20 with substantially little resistance, or at least least with insufficient resistance to stop the progress of the support member 50 through the hole in the second direction. Initially the support sleeve 50 is moved inwards beyond the position shown in Fig 1, to sweep past the first spring 40a as well, and move it to the first inclined configuration shown in Fig 1 in uniformity with the other springs 40b, c, and d. While moving inward, the inner end of the support sleeve 50 is eventually pressed against the outer end 30° of the piston head 30h, so that the nose 32 on the piston is contiguous with the support sleeve 50 as it passes through the groove. innermost part that holds spring 40a when completing the stroke. When the spring 40a has adopted the first compressed and inclined configuration shown in Fig 1, the force pushing the support sleeve 50 is reduced, allowing the piston 30 to push the support sleeve 50 forward in the first direction, from right to left. in the drawings, out of hole 10b to the position of Fig. 1.

[0062] In Fig 1, the innermost (first) groove on the inner spring end of housing 11b of hole 40a is shown axially aligned with nose 32 of the outer end of piston 30, which has a very slightly narrower OD than the adjacent inner section of the support sleeve 50.

[0063] The narrower diameter of the nose 32 of the piston 30 means that the outer surface of the nose 32 is spaced radially a small distance from the inner wall of the housing sleeve 11, as best seen in Figs. 3, 6 and 8 so that the outer ends of the springs 40 can expand radially out of the grooves 20 through the small radial distance between the housing sleeve 11 and the nose 32, and bear against the nose 32. Furthermore , because the nose is narrower than the support sleeve, the springs 40 can track the transition from the support sleeve 50 to the nose 32 without trapping the axial movement of the piston 30 in the bore, as the springs 40 just expand a little more away from the grooves 20 when transitioning the step between the support sleeve 50 and the nose 32, keeping the configurations compressed and inclined in the grooves. The nose 32 supports the springs within the slots 20, maintaining the compressed configurations of the springs 40 within the slots 20 and keeping them resiliently energized, but allowing slight expansion of the outer ends of the springs 40 outside the confines of the open end of the slot. 20 when engaged with nose 32 of piston 30.

[0064] When the support sleeve 50 is pushed back out of the hole in the first direction 10b by the piston 30 in the initial cycle, the spring 40a experiences a slight "bump" as the outer end of the spring 40a transitions between the O.D. of the support sleeve 50 into the smaller OD of the slightly narrower nose 32. This is enough to allow the spring to expand slightly out of the groove and press against the nose 32, but the expansion is not enough to allow the spring 40a to shift its configuration in groove 20, therefore, it remains in the same first inclined but slightly expanded compression configuration as shown in Fig 2 (a close-up of Fig 1).

[0065] As can be seen in Fig. 1 and Fig. 2, in the initial ready-to-actuation configuration, each spring 40 is energized in its groove 20 and adopts an energized elliptical configuration with the spring's main axis 40x inclined at a radius of axis 10x from hole 10b. Two different alternative energized (compressed) elliptical configurations of each spring 40 are possible in each groove 20, with the outer end of the main axis 40x of the inclined spring 40 being inclined in one direction through the radius toward the shoulder 31 or in the opposite direction. away from the shoulder 31 and with the major axis 40x of the spring 40 generally (but not necessarily exactly) parallel or aligned with one of the two diagonals of the groove 20, between opposite corners of the groove 20, and the minor axis of the spring 40 being parallel or aligned (generally and not necessarily exactly) with the opposite diagonal of groove 20.

[0066] The present example will be explained with reference to the two ends of the 40x main axis of the spring. These are best understood as the inner and outer ends of the spring 40. The inner end of the spring 40 is normally contained within the inner end of the groove 20. The outer end of the spring 40 is generally being pushed out of the open end of the groove 20.

[0067] In this example, the direction of continuous movement of the piston 30 in the first direction is outside the hole 10b from right to left. In this example, the piston 30 supports the shoulder 31 (in other examples, the shoulder may be static in the housing) and therefore the direction of movement of the piston shoulder 31 in this example is also from right to left in the first direction as shown in the transition between the positions in Figs. 1 and 13, in which Fig. 1 is closed with the piston 30 fully withdrawn in hole 10b, and Fig 13 is opened with the piston 30 fully extended out of hole 10b.

[0068] Thus when the piston is moving in the first direction, out of the hole from right to left in the drawings, the inner end of the main shaft 40x of the spring 40 is the end closest to the outside of the hole and furthest from the shoulder 31 (and facing axially away from it), and the outer end of the spring is the end furthest from the hole and closest to shoulder 31 (and facing axially towards it), so that the outer end generally faces the shoulder 31. Obviously, the actual direction of movement of the actuating element in different examples can be modified, and the details recited here about directions and orientations such as left and right etc. are merely illustrative of this particular example, and should not be considered as a restriction on the scope of the present disclosure as it applies to other examples.

[0069] Before adopting the configuration of Figs 1 and 2, a reset stroke of the support sleeve 50 from left to right swept the protruding outer ends of the springs 40 along in the same direction, so that the main axis 40x of each spring 40 in Fig. 1 and 2 has an inner end disposed in the groove 20 facing the outer end of the hole and spaced radially further away from the axis of the hole in the outer end of the spring projecting from the groove 20 through the open end of groove 20, facing the inner end of the hole and shoulder 31. The inner end of spring 40 is further from shoulder 31 than the outer end of spring 40. In this first configuration, each spring 40 resists additional compression along its main axis 40x. This can be used to resist axial movement of the piston 30 in a first direction (e.g., out of the bore, right to left in the present example).

[0070] In the first inclined compressed configuration shown in Fig 2, the inner end of the main axis 40x of the spring 40a faces axially away from the piston shoulder 31 and towards the outer end of the hole 10b and is disposed at an inner corner of the groove 20, between the bottom wall and the side wall in front of the piston shoulder 31. The outer end of the main axis 40x of the spring 40a is extending from the groove 20 in front of the piston shoulder 31, facing in an axial direction towards the piston shoulder 31 and closer than the inner end of the spring 40a. The spring 40a is held in this first configuration, in compression along its main axis by the piston nose 32, which has a smaller OD than the piston head plateau section 30h, which is separated from the nose 32 by the acute angular shoulder. 31. As the piston 30 moves in the bore in a first right-to-left direction, the shoulder 31, which is spaced from the front end of the piston 30, moves toward the outer end of the bore 10b, and eventually becomes engages with the outer end of the main shaft 40x of the spring 40a extending from the groove 20 in front of the shoulder 31. As the shoulder 31 moves axially in the first direction, the outer end of the spring 40a moves about the nose 32 until reaching the transition between nose 32 and shoulder 31. The relatively steep angular pitch between nose 32 and shoulder 31 prevents the spring from rising on shoulder 31 and compressing, because spring 40a is highly resistant to deformation along of the main axis 40x. Thus, the piston can translate axially while the outer end of the spring 40a is compressed against the smooth nose 32 and parallel to the axis; however, when the shoulder 31 on the piston engages the outer end of the main axis 40x of the spring 40 protruding from the groove 20 in the first configuration, the spring 40a cannot compress further in the groove 20 along its main axis 40x and resists the further movement of the shoulder 31 (and therefore the piston 30) in the first direction (e.g., out of the hole from right to left in this example). Since the inner end of the spring 40a is secured in the corner of the groove 20 in front of the shoulder 31, the spring 40 cannot move along its axis in the groove 20, nor shift within the groove 20 to allow further deformation in a different configuration. The high resistance to deformation along the main axis 40x of the spring 40a secured between the inner corner of the groove 20 and the shoulder 31 therefore restricts the movement of the piston 30 in the first direction after the point at which the nose 32 at the main end of the piston 30 covers the groove 20 and the shoulder 31 on the piston 30 engages the outer end of the spring 40a protruding from the groove 20. At this point the piston 30 can withdraw in the second opposite direction in the bore (see arrow in Fig. 3) but cannot advance beyond the point of Fig. 2 without interrupting (i.e. breaking) the spring 40a, for example, compressing it beyond the plastic deformation limit and deforming it irreversibly.

[0071] Withdrawing the piston 30 back into the hole in the second direction, as shown in the transition from Fig 2 to Fig 3, drives the piston back from left to right in hole 10b to uncover the open end of the first groove which houses the first spring 40a and drives the ramp 33 backwards against an outwardly facing shoulder in hole 10b that limits axial displacement in the second direction (in the direction of the arrow shown in Fig. 3). In this position, seals 34a, b and c still isolate the inlet and outlet 12, 13, and prevent any fluid flow therethrough. The axial movement of piston 30 is driven in this example by applying fluid pressure differentials across bore 10b via piston 30, which are transmitted from outside the bore via a pump (not shown) in fluid communication with the outer end of the bore. 10b. Fluid pressure is transmitted through hole 50b of support sleeve 50, which does not react to pressure changes and remains in position (due to friction mainly between support sleeve 50 and springs 40) when piston 30 retracts to inside the hole in the second direction. As the piston 30 retreats in the second direction and the support sleeve 50 remains static, the open end of the groove housing spring 40a is uncovered so that the spring 40a is not supported at its ID and therefore expands into the bore. 11b in a rest or neutral configuration. In the rest or neutral configuration of the spring 40a, the main axis 40x of the spring 40a is not substantially inclined through the axis of the hole and the spring 40a is partially expanded in the hole and out of the groove 20, generally symmetrical configuration about a radius of the hole as shown in Fig. 3 and Fig. 13. Spring 40a is no longer forced to adopt the first inclined energized configuration shown in Fig. 1, and adopts the neutral configuration of Fig. 3 and 13. In the neutral configuration, the spring 40c can now be moved, for example rotated, in the groove 20. This allows the spring 40a to rotate to a second energized inclined configuration as will now be described, driven in this case by the return movement of the piston 30 axially within the hole 11b in the first direction .

[0072] When the fluid pressure acting on the piston 30 to maintain it in the position of Fig. 3 is reduced so that the fluid pressure force is below the force of the spring 35, the piston 30 is pushed out of the hole 10b by spring 35, moving once again in the first right-to-left direction in the drawings (see arrow in Fig 4). When the nose 32 of the piston 30 passes the open inner end of the groove housing the first spring 40a, the piston 30 pushes the unsupported, protruding outer end of the spring 40a in the first direction, toward a second energized inclined alternative configuration of the spring 40a with the inner end of the main shaft 40x of the spring 40a disposed in the groove 20 axially closer to the shoulder 31 approaching from the right in the drawings, and the outer end of the main shaft 40x of the spring 40a protruding from the groove 20 (radially closer to the hole than the inner end) pointing away from the shoulder 31 toward the outer end of the hole and axially further away from the shoulder 31 than the inner end of the spring 40a, achieving the configuration shown in Fig. 4, in which the main axis 40x of spring 40a is now aligned with the opposite diagonal in groove 20 compared to the configuration shown in Fig. 2.

[0073] Shoulder 31 again engages with the outer end of spring 40a, projecting from groove 20, but as spring 40a has changed orientation from the first to the second configuration in groove 20, shoulder 31 compresses the minor axis instead of the 40x main axis. Since the minor axis of the spring 40 is more compressible than the major axis 40x, continued forward movement of the shoulder 31 in the first direction of the arrow shown in Fig. 4 after the position of Fig. 4 presses the shoulder 31 against the rear face of the outer end of the spring 40 which projects from the open end of the groove 20 and compresses the spring 40 in the groove 20 by applying force along the minor axis of the spring 40, pressing the spring 40 further into the groove 20 and allowing the passage of the shoulder 31 of the piston 30 passing through the groove 20 and the compressed spring 40a. The spring 40a remains in the second inclined compressed configuration as shown in Fig. 4 as the piston head 35 translates axially in the first direction (in the direction of the arrow in Fig. 4). At about the same time as the piston head 30h compresses the outer end of the spring 40a, the outer end 30o of the piston again engages the inner end of the static support sleeve 50, still in the same position as in the previous cycle, plus the axial translation of the piston 30 in the first direction (in the direction of the arrow in Fig. 40) pushes the support sleeve 50 further out in hole 10b to the position of Fig. 5. Spring 40b experiences the same "bump" when transitioning to the step slightly inward at OD between support sleeve 50 and nose 32, but remains in the same first compressed inclined configuration as shown in Fig 5, with a slightly steeper expansion out of groove 20 than springs 40c and 40d .

[0074] Thus, it can be seen that moving the piston 30 through the free end of a groove 20 first in one direction and then in the opposite direction can change the spring 40a within the groove from a compressed inclined position to a neutral position, and then to an opposite compressed inclined position. Changing the spring 40a between different inclined configurations, from a first configuration in which the spring 40a engages with the piston 30 and resists the passage of the piston 30 past the groove 20, to a second configuration in which the spring 40a engages with the piston 30 and allows the passage of the piston 30 through the groove 20 which holds the spring 40a can be used to stop the movement of the piston 30 at defined positions in the bore, for example at the boundaries of the grooves, and control different more precisely indexed stop locations of piston 30 in the hole that defines the intermediate positions between open and closed configurations.

[0075] After compressing the outer end of the spring 40a in its groove, the piston 30 passes through the position of Fig 4 under the force of the expansion spring 35, pushing the support sleeve 50 forward in the hole 10b in the first direction shown in Fig 5, to the position shown in Fig 5. Here the configuration is essentially the same as in Fig 2, but moved along a groove 20 towards the outer end of the hole 10b. As in the configuration of Fig. corner of the groove 20, between the bottom wall and the side wall in front of the piston shoulder 31 and further from the piston shoulder 31 than the outer end of the spring 40b, and the outer end of the main shaft 40x of the spring 40b projects from the groove 20 in front of the piston shoulder 31, facing in an axial direction towards the piston shoulder 31 and closer (in the axial direction) than the inner end. The spring 40b is resiliently held in compression by the nose 32 of the piston, and as the piston 30 moves in the bore in a first right-to-left direction, the shoulder 31 engages with the outer end of the main shaft 40x of the piston. spring 40b extending from groove 20 in front of shoulder 31. The steep angle in shoulder 31 acts as a stop, and the high resistance to deformation along the main axis 40x prevents or resists further movement of piston 30 in the first direction after the point of Fig 5 on the nose 32 on the leading end of the piston 30 covers the groove 20 and the shoulder 31 on the piston 30 engages the outer end of the spring 40 projecting from the groove 20, generally in the same manner as explained for the configuration of Fig. 2, but moved along a spring 40. At this point, the piston 30 can withdraw in the second opposite direction into the hole (see arrow in Fig 6), but cannot advance out of the hole beyond the point in Fig 5. Note that at the point in Fig 5, spring 40a is not compressed, because it is aligned axially with a free space 30f in the ring between the hole 10b and the piston 30 behind the ramp 33 in the piston head 30h, and therefore the spring 40a adopts an uncompressed neutral position in its groove. This presents no substantial resistance to the passage of the piston 30 in any direction past the spring 40a.

[0076] An increase in fluid pressure on the outside of hole 10b again drives piston 30 in the second direction back to hole 10b to reach the position shown in Fig 6, which uncovers the open ends of the grooves housing the two springs 40a and 40b, which then adopt the same neutral position and can be rotated in their grooves 20 and/or passed by the piston 30 without substantial resistance as previously described. The head 30h of the piston 30 can easily compress the springs 40b and 40a in their grooves as they are in the neutral position. The configuration of Fig 6 is the same as Fig 3, with the piston 30 unable to move further in the second direction, except that the support sleeve 50 has moved further along the row of grooves 20 towards the outer end of the bore. 10b, and uncovered the two spline housing springs 40a and 40b. The support sleeve 50 remains where it is when the piston 30 moves away from it in the second direction, due to friction between the support sleeve 50 and the springs 40.

[0077] From the position shown in Fig. 6, the fluid pressure is then reduced again, allowing the spring force to return the piston 30 in the first direction as shown in Fig. 7, to the nose 32 beneath the spring 40c , which abuts the shoulder 31 of the piston 30. This position is maintained for the same reasons explained above in relation to Figures 2 and 5, as the shoulder 31 abuts the outer protruding end of the spring 40c and cannot go any further in the first direction due to the high compressive strength of the 40c spring while it is in its first configuration. The piston 30 is again reset to the configuration of Fig 8, increasing the fluid pressure to overcome the spring force as described in relation to Fig 6, and moving the piston 30 back to the hole 10b in the second direction as shown by the arrow. in Fig 8 to the stop position.

[0078] Note that the piston 30 has been translated in alternating first and second directions, being prevented from moving in the first direction on each spring 40 when the spring 40 is in the first compressed configuration with the outer end protruding from the groove and closer to the shoulder 31, but passing each spring in the first direction without substantial resistance (in each direction) when the spring 40 was in a neutral or second compression configuration, because each of these configurations could be compressed in the groove by compression of the spring at the same time. along its minor axis, considering that the springs in the first configuration resist compression in the groove along their main axes and therefore act as a stop. Note that at each transition, the piston advances axially in a stepwise manner further in the first direction out of hole 10b than was possible in previous transitions, and that the stopping or indexing position is dictated by the position of the grooves 20. So far, this did not lead to any change in the actuation state of the assembly, because although the seals 34a, b and c in the piston 30 moved axially with the piston 30 in the hole 10b, they remained compressed in the ring between the hole 10b and the piston 30 on the opposite sides from inlet 12 and outlet 13, and is therefore still isolating inlet 12 from outlet 13, although seal 34c is now closer to outlet 13 than it was previously, and seal 34b is now closer to inlet 12. Also note that shoulder 31 on piston 30 acts as a one-way stop for the actuating member, reacting with the springs to stop movement in the first direction if the spring in front of it is in the first setting, but allowing movement in the second direction in each setting of the springs.

[0079] In the next cycle the fluid pressure is reduced in the configuration of Fig 8 and the spring force returns the piston 30 to the configuration of Fig 9. Seal 34b is now relatively close to the groove 12g that surrounds the inlet 12, but is still compressed and still resists fluid communication between the inlet and outlet 12, 13. The piston 30 reaches its maximum limit of displacement in the first direction (of the arrow shown in Fig 9) when the shoulder 31 touches the outer protruding end of the spring 40d, and fluid pressure is then increased again from the pump to drive piston 30 back to bore 10b for the arrangement of Fig 10, which is the final cycle before actuation of valve 1. As before, piston 30 pushed the support sleeve 50 past the groove housing in the end spring 40d, which is now unsupported as the support sleeve 50 remained in position when the piston retracted to the Fig. 10 position.

[0080] Note that in each cycle, the elongated extension of the nose 32 pushed the support sleeve 50 beyond the groove housing the spring in the first compressed configuration that stops the piston. Thus, in each cycle, when the piston moves in the bore, it pushes the support sleeve 50 between its different positions, and removes the support sleeve holder 50 from the open end of the recess, one spring at a time. Thus, when the nose 32 retracts into the hole 10b after stopping on the spring, the spring 40 is displaced from its first compressed configuration, in which it may prevent the spring from advancing axially in the hole in the first direction, to a neutral position in which the spring 40 allows piston 30 to pass in each direction without substantial resistance.

[0081] Thus, in the final cycle between the positions of Fig. 10 and Fig. 11, when the fluid pressure is reduced, the spring force pushes the piston 30 axially through hole 10b, passing through all springs 40a, b, and c which are all in the neutral position and offer little or no resistance to the passage of the piston 30. Thus, the piston 30 moves under the force of the compressed spring 35 until the seal 34b enters the groove 12g at the inlet, and loses its sealing function as it is no longer compressed by the opposing walls. There is now an open fluid path between inlet 12 and outlet 13, although leaks at both ends of piston 30 are still prevented by seals 34a and 34c. Therefore, while the assembly is in position Fig 11 and Fig 13 (which are the same) the valve is open and fluid can flow from inlet 12 to outlet 13.

[0082] Valve 1 can be reset by moving the support sleeve 50 (which pushes the piston in front of it) axially back into the bore in the second direction (shown by the arrow in Fig 3) in a reset stroke until the end internal support sleeve 50 has passed through the spring groove housing 40a and the ramp 33 has been pushed out of the housing as shown in Fig 3, and all springs 40a, b, c, and d have been reset to their first compressed configurations. inclined cylinders shown in Fig 1, and are supported from the inside by the support sleeve 50. Optionally, the support sleeve may be moved by a piston (which may be an integral part of the support sleeve or may be a separate item and which may optionally incorporate differential sealed areas) which can be activated by a separate control line, providing fluid pressure to move the support sleeve axially in hole 10b. Once the springs 40 have been reset beyond the positions of Fig. 1, the pressure can be released, and the piston 30 will return the assembly under the force of spring 35 to the position of Fig. 1, where it is restrained by the first inclined configuration. compressed spring 40a.

[0083] In the present example, the different intermediate axial positions adopted by the piston 30 within the hole 10b are used as indexing points which, in this example, do not trigger different input and output configurations, but which advance the assembly to the final position in that the configuration change is triggered at the transition between the positions in Figure 10 and Figure 11. However, in other examples, each position of the piston 30 could affect a different configuration change in the assembly. In some examples, a tool may be connected to the actuator assembly and may operate under its control. For example, separate positions of the actuation member may correspond to separate actuation states of the downhole tool. In one example, the piston 30 may itself comprise a tool part, for example a component of a sliding sleeve valve system, which slides axially within the housing in order to move respective openings in a sliding sleeve connected to the piston 30 in and out of alignment with a flow path that controls fluid flow, or to vary the extent of overlap of such openings in order to increase or decrease the cross-sectional area of a fluid conduit by gradually increasing or decreasing the fluid flow gradually in each position.

[0084] Referring now to Figs. 15-22, a second example of an actuator assembly in the form of a valve 101 has similar characteristics to valve 1, which are referenced with the same number but increased by 100. One skilled in the art is directed to the first example described herein. for a complete description of similar parts. The valve 101 has a fixed member in the form of a housing 110, with a tubular bore 110b which receives an actuating member in this example taking the form of a piston 130 which is centered within the bore 110b and sealed in the bore as previously described. The inner end of the bore is substantially the same as valve assembly 1. The differences between the first and second examination are generally related to the outer end of the bore and the piston head.

[0085] While in the first example, the shoulder is located in the piston actuating member and the recesses and springs are located in the fixed member of the housing, in the second example, these are reversed, and the shoulder is located in the fixed member of a sleeve. housing, while the recesses and springs are located in the piston actuating member.

[0086] In the second example, the inward travel of the piston 130 is limited by respective opposing beveled edges on the outer end of the piston 130 and a housing sleeve 111. The housing sleeve 111 is secured to the housing 110 by a screw thread and has a shoulder 131 similar to shoulder 31 in the first example, but facing in the opposite direction, toward the inner end of hole 110b. The housing sleeve 111 has a central hole that is coaxial with the hole 110b of the housing 110.

[0087] The outer surface of the piston 130 has a plurality of recesses in the form of circumferential annular grooves 120 having a similar geometry to the grooves 20. Each groove 120 retains an alloy-type helical spring in the form of an inclined helical spring 140 essentially as described for the first example.

[0088] The open end of bore 110b has a counter bore that defines an outward facing shoulder 110s, and creates an annular area between the inner surface of the housing 110, the outer surface of the piston 130, the shoulder 110s, and the sleeve of housing 111, which encloses the outer end of the annular area. Support sleeve 150 has a coaxial hole that accommodates piston 130 and allows the support sleeve to move axially in each direction relative to piston 130 and housing 110. Support sleeve 150 is captive within the annular area within the hole, which is closed at the inner and outer ends of the hole by shoulders 110s and housing sleeve 111 respectively. As previously described, the axial position of the support sleeve 150 is optionally maintained by friction between the support sleeve 150 and the springs 140.

[0089] To configure the assembly for actuation, the piston 130 is pressed into hole 110b in the second direction, from left to right in the drawings. The outer end of the shoulder 131 in the housing sleeve 111 has a ramp similar to the ramp 33 in the first example, which slides through all open ends of the slots 120 of the housing springs 140a-d. This moved the protruding outer ends of the springs towards the outer end of the hole, so that as they compress within their respective grooves 20, they adopt the first compressed inclined configurations shown in Fig 15 generally aligned with a diagonal, with their outer ends pushing towards outside the groove 120 furthest from the inner end of the hole 110b and closest to the shoulder 131 (and facing it in an axial direction), while the inner ends are secured in a corner of the inner end of the groove, closer to the inner end of the hole 110b and further away from the shoulder 131 (and facing axially away from the shoulder 131) than the outer ends of the springs. This movement is compressing the springs along their minor axes rather than their major axes, so that they compress into the 120 grooves with substantially little resistance. While moving inward, the chamfered face at the inner end of the piston 130 is eventually pressed against the ramp at the outer end of the housing sleeve 111. The support sleeve 150 may be pushed into the position of Fig. 15 at this point by pressure from fluid or the like during reset and maintains the springs 140a-d in this first inclined configuration. Optionally the support sleeve 150 may be secured in the position of Fig. 15 during assembly by a pin extending radially through the housing wall 110, maintaining the support sleeve 150 in the position of Fig. 15 during insertion of the piston 130 , after which the pin can be removed. When all springs 140 have adopted the first compressed and inclined configuration shown in Fig. 15, the fluid pressure forcing piston 130 into hole 110b is reduced, allowing spring 130s to move piston 130 in the first direction, from right to right. left in the drawings, out of hole 10b to the position of Fig. 15. Friction between the springs 140 and the support sleeve 150 ensures that the position of the support sleeve 150 remains as shown in Fig. 15 when the piston 130 is extended out of hole 110b from right to left under the force of spring 135. Optionally the support sleeve 150 may be moved axially during or after reset operations by a separate control line, providing fluid pressure. Optionally the support sleeve 150 may be held in the position of Fig. 15 during reset, for example, by fluid pressure from this control line.

[0090] In Fig 15, the outermost (first) groove on the outer end of the piston housing spring 130 is shown axially in line with the nose of the inner end of the housing sleeve 111, which has a very slightly narrower OD than the adjacent inner inner section of the support sleeve 150 (as best seen in Fig 20). The narrower diameter of the nose allows the outer ends of the springs 140 to expand radially outward from the grooves 120 across the short radial distance between the piston 130 and the housing sleeve 111, and support the nose, essentially as described for the previous example. . The nose supports and compresses the springs within the slots, but allowing slight expansion from the open ends of the slots 120 as previously described.

[0091] In the initial configuration ready for actuation, each spring 140 adopts an energized elliptical configuration. A reset stroke of the piston 130 set the springs 140 in the first configuration, with the main axis of each spring 140 having an inner end disposed in the groove 120 facing the inner end of the hole and spaced radially closer to the axis of the hole than the outer end of the spring extending from the groove 120 through the open end of the groove 120, facing the outer end of the hole and shoulder 131. The inner end of the spring 140 is further away (in an axial direction) from the shoulder 131 than the outer end of the spring 140. In this first configuration, each spring 140 resists additional compression along its main axis, as previously described. Thus, in the first inclined compressed configuration shown in Fig. 15, the inner end of the spring main shaft 140a lies in an axial direction away from the shoulder 131 and toward the inner end of the hole 110b and is disposed in an inner corner of the groove 120. between the bottom wall and the shoulder-facing side wall 131. The outer end of the spring main axis 140a is projecting from the groove 120, facing in an axial direction toward the shoulder 131 and closer to it than the inner end of spring 140a. The spring 140a is held in this first configuration, in compression along its main axis by the nose. As the piston 130 moves in the bore in a first right-to-left direction, the shoulder 131 engages with the outer end of the main shaft of the spring 140a projecting from the groove 120 facing the shoulder 131 and in this arrangement, the spring 140a cannot compress further in the groove 120 along its main axis and resists further movement of the shoulder 131 (and therefore the piston 130) in the first direction (e.g., out of the hole from the right to left in this example). The piston 130 may withdraw in the second opposite direction in the bore, but it may not advance beyond this point without interrupting (i.e., breaking) the spring 140a.

[0092] Withdrawing the piston 130 back into the hole in the second direction, as shown in the transition from Fig 15 to Fig 16, drives the piston back from left to right in hole 110b to uncover the open end of the first groove that houses the first spring 140a and drives the beveled edges of the piston 130 and the housing sleeve 111 together, which limits the axial displacement in the second direction. In this position, seals 134a, b and c still isolate the inlet and outlet 112, 113 and prevent any fluid flow therethrough. As piston 130 withdraws in the second direction, spring 140a expands into bore 111b in a rest or neutral configuration as previously described, and can now be displaced, e.g., rotated, in groove 120 to turn to a second energized inclined configuration, driven by the return movement of piston 130 axially within hole 111b in the first right-to-left direction in the drawings. As the nose passes the open inner end of the groove housing the first spring 140a, the nose pushes the unsupported, protruding outer end of the spring 140a into a second alternative energized inclined configuration in which the main axis of the spring 140a is now aligned. with the opposite diagonal in the groove 120 compared to the original configuration adopted by the other springs 140b, c, d.

[0093] The shoulder 131 again engages with the outer end of the spring 140a exiting the groove 120, but as the spring 140a has changed orientation from the first to the second configuration, the shoulder 131 compresses the minor axis rather than the major axis, so that the piston 130 continues to move until the spring 140a passes the shoulder 131.

[0094] Movement of the piston 130 out of hole 110b forces the support sleeve 150 against the inner end of the housing sleeve 111 and causes the support sleeve 150 to slide axially relative to the piston 130 until the support sleeve 150 find the next recess by holding spring 140b. Spring 140b experiences the same "bump" when transitioning step in OD between support sleeve 150 and nose, but remains in the same first compressed inclined configuration as previously described.

[0095] Thus, it can be seen that moving the piston 130 through the free end of a groove 120 first in one direction and then in the opposite direction can displace the spring 140 within the groove from a compressed position to a neutral position, and then then to an opposite compressed inclined position. Changing the spring 140 between different inclined configurations, from a first configuration in which the spring 140 engages with the piston 130 and resists the passage of the piston 130 past the groove 120, to a second configuration in which the spring 140 engages with the piston 130 and allows the passage of the piston 130 through the groove 120 holding the spring 140 is used in this example to stop the movement of the piston 130 at defined positions in the bore as previously described, until the final position is reached as shown in Fig. 18 In the final cycle before the position of Fig. 18, when the fluid pressure is reduced, the spring force pushes the piston 130 axially through hole 110b, past all springs 140a, b, c and d which are all in the neutral position. and offer little or no resistance to the passage of piston 130. Thus, piston 130 moves under the force of compressed spring 135 until seal 134b is unloaded and the valve is open, allowing fluid to flow from inlet 112 to exit 113.

[0096] Valve 101 can be reset by moving piston 130 axially back into the bore on a reset stroke. At this stage, the pressure can be released and the piston 130 will return under the force of the spring 135 to the position of Fig 15, where it is restrained by the first compressed inclined configuration of the spring 140a. Optionally, the axial position of the support sleeve 150 within hole 110b may be adjusted after reset operations by a separate control line, supplying fluid pressure to the support sleeve 150 to move it back to the position of Fig. 15 after reset.

[0097] Referring now to Fig. 23-30, a third example of an actuator assembly in the form of a valve 201 has similar characteristics to valve 1, which is referenced with the same number, but increased by 200. The person skilled in the art. Subject is directed to the first and second examples described here for a complete description of similar parts. In valve 201, instead of the piston being contained within a hole in a fixed housing, the piston is in the form of a sleeve with a hole that accommodates a fixed mandrel, into which the piston sleeve slides axially. The piston sleeve and mandrel are contained in a housing (not shown) that may incorporate seals on the outer surface of the piston. The valve 201 thus has a fixed member in the form of a fixed mandrel 210, in the form of a generally cylindrical rod fixed in position in the assembly and having an axle and having an internal end (shown in the drawings on the right side) fixed to a body. The mandrel 201 has an outer end (shown in the drawings on the left side) where the mandrel 201 ends and allows mounting of the different sleeves and springs on the mandrel 201. The mandrel 201 is received within the bore of an actuation member in this example, taking the form of a piston sleeve 230. The ring between the piston sleeve bore 230 and the mandrel 201 is sealed in the same manner as described previously, with seals 234a-c and an additional seal 234d in an outer section of the bore of the piston sleeve 230 having a wider inner diameter than an inner section. The inward axial displacement of the piston sleeve 230 is limited by an end shoulder on a cylindrical projection disposed at the outer end of the mandrel 210 disposed in the large diameter outer section of the piston sleeve 230. The outward axial displacement of the piston sleeve 230 piston 230 over mandrel 210 is limited by opposing beveled edges at the outer end of the protrusion on mandrel 210 and at the inner end of the widest section in the bore of piston sleeve 230. Piston sleeve 230 incorporates a fluid inlet and outlet 212, 213, which cooperate with seals 234 a-c in the same manner as described for seals 3, 4a-c and outlet and inlet 12 and 13. A spring 235 is held in compression between an inner end of piston sleeve 230 and a shoulder facing out on the 210 chuck.

[0098] In the third example 201, the shoulder 231 is located in the actuating member of the piston sleeve 230 and the recesses and springs are located in the fixed member of the mandrel 210. Thus, the outer surface of the mandrel 210 has a plurality of recesses in the form of circumferential annular slots 220 having a similar geometry to the slots 20, containing inclined helical springs 240 essentially as described for the first example.

[0099] The support sleeve 250 has a coaxial hole that accommodates the mandrel 210 and allows the support sleeve 250 to move axially in each direction relative to the mandrel 210 and the grooves 220 and relative to the piston sleeve 230. support sleeve 150 is arranged together with the piston sleeve 230 in the same manner as described in the first example, so that the piston sleeve 230 pushes the support sleeve 250 axially when moving in the first direction (in this case externally from right to left). As previously described, the axial position of the support sleeve 250 is optionally maintained by friction between the support sleeve 250 and the springs 240, so that the support sleeve 250 can move relative to the piston sleeve 230 when the friction is overcome, but retains its position in the mandrel 210 in the absence of any forces (for example, applied by the piston sleeve 230) tending to move it, remaining static in the mandrel 210 when the piston sleeve 230 withdraws from it. The shoulder 231 is disposed at the outer end of the piston sleeve 230, facing the support sleeve 250.

[00100] To configure the assembly for actuation, the piston sleeve 230 is compressed in the configuration of Fig 24, with the piston sleeve 230 retracted toward the inner end of the mandrel 210 and the spring compressed as the piston sleeve 230 moves inward in the second direction, from left to right across the drawings in a reset course. The inner end of the shoulder 231 on the piston sleeve 230 has a ramp similar to the ramp 33 in the first example, which slides through all open ends of the grooves 220 of the springs of the housing 240a-d. This moved the protruding outer ends of the springs to the right towards the inner end of the mandrel 210, so that they compressed within their respective grooves 220, they adopt the first compressed inclined configurations shown in Fig. 23 generally aligned with a diagonal, with their outer ends pushing outward from the grooves 220 furthest from the outer end of the mandrel 210 and closer to (and pointing toward) the shoulder 231, while the inner ends are secured in a corner of the inner end of the groove, closer to the outer end of the mandrel 210 and axially further away from the shoulder 231 than the outer ends of the springs (and facing away from the shoulder 231). This movement is compressing the springs along their minor axes, rather than their major axes, so that they compress easily into the grooves 220. As it moves inward, the chamfered face on the inner end of the larger diameter section of the spring sleeve piston 230 is eventually pressed against the chamfered face at the outer end of the cylindrical projection in mandrel 210 to limit axial movement. Support sleeve 250 may be pushed inward at this point by fluid pressure or the like during or after reset to cover all springs 240 and maintain springs 240a-d in this first inclined configuration. The axial movement of the support sleeve 250 can be driven by fluid pressure through a separate control line, as described in the previous examples. When all springs 240 have adopted the first compressed and inclined configuration shown in Fig. 23 and are covered by the support sleeve 250, the fluid pressure forcing the piston sleeve 230 inward toward the inner end of the mandrel 210 is reduced, allowing that the spring 235 actuates the piston 230 in the first direction, from right to left in the drawings, externally over the mandrel 210 to the position of Fig 23.

[00101] In Fig 23, the innermost (first) groove on the inner end of the housing spring 240 of the mandrel 240 is shown aligned axially with the nose of the inner end of the piston sleeve 230, which supports and compresses the springs within the grooves. , as described previously.

[00102] In the initial configuration ready for actuation, each spring 240 adopts an energized elliptical configuration. The stroke of the piston sleeve 230 and the support sleeve 250 secured the springs 240 in the first configuration, with the main shaft of each spring 240 having an inner end disposed in the groove 220 facing the outer end of the mandrel 210 and spaced radially closer. to the chuck shaft that the outer end of the spring protruding from the groove 220 through the open end of the groove 220, facing the inner end of the chuck and shoulder 231. The inner end of the spring 240 is further away (in a axial direction) of the shoulder 231 than the outer end of the spring 240. In this first configuration, each spring 240 resists additional compression along its main axis, as previously described. Spring 240a is held in this first configuration, in compression along its main axis by the nose. As the piston sleeve 230 moves in a first right-to-left direction, the shoulder 231 engages with the outer end of the spring main shaft 240a projecting from the groove 220 and facing the shoulder 231, and In this arrangement, the spring 240a cannot compress further in the groove 220 along its main axis and resists further movement of the shoulder 231 (and therefore the piston sleeve 230) in the first direction (e.g., toward the outer end of chuck 210 from right to left in this example). The piston 230 can withdraw in the second opposite direction in the bore, but cannot advance beyond this point without interrupting (i.e., breaking) the spring 240a.

[00103] Withdrawing the piston sleeve 230 back into the hole in the second direction, as shown in the transition from Fig 23 to Fig 24, drives the piston sleeve 230 back from left to right toward the inner end of the mandrel 210 to uncover the open end of the first groove housing of the first spring 240a, with the seals 234a, b and c further isolating the inlet and outlet 212, 213 and preventing any flow of fluid therethrough. As piston sleeve 230 retracts in the second direction, spring 240a expands out of groove 220 to a rest or neutral configuration as previously described, and can now be moved, e.g., rotated, in groove 220 to turn to a second energized inclined configuration, driven by the return movement of the piston sleeve 230 axially toward the outer end of the mandrel 210 in the first right-to-left direction in the drawings. As the nose passes the open inner end of the groove housing the first spring 240a, the nose pushes the unsupported, protruding outer end of the spring 240a into a second alternative energized inclined configuration in which the main axis of the spring 240a is now aligned. with the opposite diagonal in the groove 220 compared to the original configuration adopted by the other springs 240b, c, d.

[00104] Shoulder 231 again engages with the outer end of spring 240a, projecting from groove 220, but as spring 240a has changed orientation from the first to the second configuration, shoulder 231 compresses the minor axis rather than the main, so that the piston sleeve 230 continues to move until the spring 240a passes the shoulder 231.

[00105] Movement of the piston sleeve 230 toward the outer end of the mandrel 210 engages the support sleeve 250 against the outer end of the piston sleeve 230 and causes the support sleeve 250 to slide axially relative to the mandrel 210 until that the support sleeve 250 uncovers the next recess supporting the spring 240b, in the same first compressed inclined configuration as described previously.

[00106] Thus, it can be seen that moving the piston sleeve 230 through the free end of a groove 220 first in one direction and then in the opposite direction can change the spring 240 within the groove from a compressed inclined position to a neutral position. and then to an opposite compressed inclined position. Changing the spring 240 between different inclined configurations, from a first configuration in which the spring 240 engages with the piston sleeve 230 and resists the passage of the piston sleeve 230 past the groove 220, to a second configuration in which the spring 240 fits with the piston sleeve 230 and allows the passage of the piston sleeve 230 through the groove 220 holding the spring 240 is used in this example to stop the movement of the piston sleeve 230 at defined positions in the bore as previously described, until the position final cycle is reached as shown in Figure 26. In the final cycle before the position of Fig. 26, when the fluid pressure is reduced, the pressure force pushes the piston sleeve 230 axially past all springs 240a, b, c and d, which are all in the neutral position and offer little or no resistance to the passage of the piston sleeve 230. Thus, the piston sleeve 230 moves under the force of the compressed spring 235 until the seal 234b is unloaded and the valve is open, allowing fluid flows from inlet 212 to outlet 213.

[00107] Valve 201 can be reset by moving piston sleeve 230 axially back toward the inner end of mandrel 210 in a reset stroke. The support sleeve 250 can be moved with it as previously described. At this stage, the pressure can be released and the piston sleeve 230 will return under the force of the spring 235 to the position of Fig 23, where it is restrained by the first compressed inclined configuration of the spring 240a.

[00108] In the third example, the recesses and springs are provided in the fixed member, and the shoulder is provided in the actuating member, but, as described in the second example, this arrangement can be reversed.

[00109] Referring now to Figures 31-46, a fourth example of an actuator assembly in the form of a valve 301 has similar characteristics to valve 1, which is referenced with the same number, but increased by 300. The skilled artisan is directed to the first example described here for a complete description of similar parts; Also the features of the present example can be applied to the first example. The valve 301 has a fixed member in the form of a tubular housing 310 having box and pin connections at opposite ends for connecting in-line with a string of tubing, with a tubular bore 310b receiving an actuating member in this example assuming the in the form of a piston 330 that is centered and sealed in bore 310b of housing 310 as previously described. As in the first example, the shoulder 331 is located in the piston actuating member and the recesses and springs are located in the fixed housing member 310, but, as previously described, these can be reversed.

[00110] In the fourth example, the inward travel of piston 330 is limited by a ramp at the inner end of the piston head and an outwardly facing shoulder on housing 310. Housing 310 has a cover 310c, which is connected to the housing by a screw thread. The cap 310c retains within the bore 310b a housing sleeve 311, having a central bore which is coaxial with the bore 310b of the housing 310, in which the piston 330 slides axially. The housing sleeve 311 has grooves and springs 340a, b and c as described for the housing sleeve 11.

[00111] One difference between the first and fourth examples is the arrangement, in this fourth example, of a tubular hole through the piston 330, coaxial with the housing hole 310, and allowing a flow path through the valve, so that it can be connected according to a conduit such as a pipe string. This allows valve 301 to be used as a circulation valve. To this end, the inner end of the piston 330 has radial channels 330a, b and c, arranged in the walls of the piston 330 and spaced axially along it; The piston 330 slides in bore 310b of the housing to move radial channels 330a, b, c sequentially in and out of alignment with an exit port 313 on the side of housing 310. The piston 330 is sealed in bore 310b by seal 334a, b which controls the flow of fluid through outlet port 313 in a manner similar to that described for seals 34. Piston 330 is moved axially in housing 310 by spring 335 in a manner similar to that described for the first example.

[00112] Another difference between the fourth and first example concerns the shoulder 331, which is more clearly shown in the expanded view of Fig 45, which is an expanded view of the Fig 32 position of the valve 301.

[00113] As best shown in Fig 45, the outer end of the piston 330 is a head with an outer diameter larger than the center section of the piston 330 with a plateau section, a nose and an inwardly facing ramp, as previously described. The head has a shoulder 331 facing the outer end and a shoulder 331b facing the inner end of the bore 310b. Between shoulders 331, 331b, the plateau section has a stepped profile, where the outer diameter of the plateau moves radially inward, as best shown in Fig 45.

[00114] In the initial position of Fig 31, the piston 330 is pressed by spring 335 against the first spring 340a, which engages the shoulder 331 in a similar manner to that described previously, with each spring 340 energized in the first inclined compressed configuration. The piston 330 therefore cannot move any further in the first direction, out of the hole, in the direction of the arrow in Fig 31. The increase in pressure to drive the piston 330 back into the hole in the second direction from left to right in the hole 310b uncovers the open end of the first groove housing the first spring 340a and drives the ramp at the inner end of the head against an outwardly facing shoulder in hole 310b that limits axial displacement in the second direction (in the direction of the arrow shown in Fig. 32). In this position, seals 334a, b still isolate outlet 313 and prevent any fluid flow therethrough. As the piston 330 withdraws into bore 310b in the second direction and the support sleeve 350 remains static, the open end of the spline housing spring 340a is uncovered, so that the spring 340a is not supported in its diameter. internal and therefore expands into the housing sleeve bore in a rest or neutral configuration. When the fluid pressure acting on the piston 330 to hold it in the position of Fig 32 is reduced so that the fluid pressure force is below the force of the spring 335, the piston 330 is pushed out of the bore by the spring. , moving once again in a first direction from right to left in the drawings (see arrow in Fig 33), pushing the unsupported, protruding outer end of spring 340a in the first direction, to the second alternative energized inclined configuration, which is retained by the stepped shape of the head region between the shoulders 331 and 331b as the piston 330 moves in the first direction, pressing the spring 340a further into the groove and allowing the shoulder 331 to pass in the first direction after the compressed spring 340a in the second inclined compressed configuration. The piston head also reengages the inner end of the static support sleeve 350, pushing it out into the bore in a manner essentially similar to the transition between Figs. 2-5, except that instead of the first spring 340a reverting to its rest or neutral configuration once the shoulder passes through, it is held in the second configuration by the stepped profile of the piston plateau 330 and of course the structural differences described. anteriorly from hole 330b and outlet channels 330a, b, c in piston 330.

[00115] In position Fig 33, piston 330 is checked against continuous axial movement in the first direction (of the arrow in Fig 33) by spring 340b, engaged against the outer face of shoulder 331 in the first configuration. In this position, the seals 334a, b no longer isolate the outlet port 313 and the narrower channel 330a is aligned with it, allowing flow from the hole 330b out of the valve 301, but obstructing it to its lowest flow rate.

[00116] Whereas, in the transitions between the configurations shown in Figure 5-7 it is necessary for the piston 30 in the first example to move axially to the initial position shown in Figure 6, the fourth example is different, as the remaining first spring 340a in the second configuration it acts as a stop in the opposite direction to resist axial movement of the piston 330 in the second direction beyond the position shown in Fig 34, in which the spring 340a is engaged with the shoulder 331b, without requiring additional movement of the piston 330 all the way. way back to the position in Fig. 32 . Therefore, the reduction of fluid pressure acting on piston 330 after the position of Fig 34 causes spring 335 to move piston 330 once again in the first direction (see arrow in Fig 35), so that shoulder 331 engages the third spring 340c and stops, with the second channel 330b aligned with the outlet port 313, obstructing flow therethrough at a slightly higher flow rate than the narrower channel 330a.

[00117] A further increase in fluid pressure again drives piston 330 in the second direction back into hole 310b to reach the position shown in Fig 36, which uncovers the open end of the groove housing in the last spring 340c (as best seen in Fig 46, which is a close-up view of the piston 330 in Fig. 36), which adopts the neutral position, while the spring 340b is maintained in the second configuration by the stepped profile. Note that, as it is no longer necessary, the first spring 340a is not supported by the head in the position of Fig 36 and is also in the neutral position. Note also that the spring 340b in the second configuration engages with the inner face of the shoulder 331, also at the same angle as the outer face that engages the springs 340 when the piston is moving in the first direction, therefore stopping the movement of reset piston 330 in the second direction to the position of Fig. 36. From this position, fluid pressure is then reduced again, allowing spring force to return piston 30 in the first direction, as shown in Fig 37. Upon reaching In this final position, the piston 330 passes the third spring 340c in its neutral position, until the outer end of the support sleeve 350 abuts an inwardly facing shoulder of the housing, at which point the piston 330 continues outward movement in the first direction. is secured, and the full bore end channel 330c is aligned with the outlet port 313, allowing maximum flow of fluid through the column, through bore 310b of the housing and bore 330b of the piston 330.

[00118] Valve 301 can be reset by moving support sleeve 350 (which pushes the piston in front of it) axially back into the bore in the second direction (shown by the arrow in Fig 32) in a reset stroke to the inner end one or other of the shoulders 331, 331b have passed through the grooves housing the springs and all the springs 340 have been reset to their first compressed inclined configurations, shown in Fig 31. Optionally, the support sleeve can be moved by a piston (which may be an integral part of the support sleeve or may be a separate item and may optionally incorporate differential sealed areas) which may be activated by a separate control line providing fluid pressure to move the support sleeve axially in hole 310b. Once the springs 340 have been reset beyond the positions of Fig 31, the pressure can be released and the piston 330 will return the assembly under the force of spring 335 to the position of Fig 31, where it is restrained by the first inclined compression spring configuration. 340a.

[00119] Referring now to Figures 47-52, a fifth example of an actuator assembly in the form of a valve 401 has similar characteristics to valve 1, which is referenced with the same number, but increased by 400. The skilled artisan is directed to the first example described here for a complete description of similar parts; Also the characteristics of the present example can be applied to the first example. Valve 401 is essentially the same as valve 1, with a completely identical inner end (not shown in Figs. 47-50 for brevity, but shown in Fig. 51) with the differences between valves 1 and 401 residing on the piston head and shoulder. The previous description of the first example is referred to for a complete description. The shoulder of the fifth example is similar to the shoulder 331 of the fourth example 301, but has a single shoulder with outer and inner faces with a steep angle on each face capable of engaging a spring and checking the movement of the piston in different directions. In this example, the shoulder is symmetrical.

[00120] The outer end of the piston 430 (best seen in Fig 52) has a head with an outer diameter larger than the central section of the piston 430 with a plateau section, a nose and an inwardly facing ramp, as previously described. The head has a symmetrical shoulder 431 having an outer face facing the outer end of the bore 410b and the inner face facing the inner end of the bore 410b.

[00121] In the initial position of Fig 47, the piston 430 is pressed by the spring against the first spring 440a, which engages the shoulder 431 in a similar manner to that described previously, with each spring 440 energized in the first inclined compressed configuration. The piston 430 therefore cannot move any further in the first direction, out of the hole, in the direction of the arrow in Fig 47. The increase in pressure to drive the piston 430 back into the hole in the second direction from left to right in the Hole 410b uncovers the open end of the first groove housing the first spring 440a and drives the ramp at the inner end of the head against an outwardly facing shoulder in hole 410b that limits axial displacement in the second direction. In this position, the seals still isolate the inlet and outlet. As the piston 430 withdraws into bore 410b in the second direction and the support sleeve 450 remains static, the open end of the spline housing spring 440a is uncovered, so that the spring 440a is not supported in its diameter. internal and therefore expands into the housing sleeve bore in a rest or neutral configuration. When the fluid pressure is reduced, the piston 430 is pushed out of the bore by the spring, moving once again in the first right-to-left direction in the drawings (see arrow in Fig. 48), pushing the outer end unsupported and protruding from spring 440a in the first direction, to the second alternative energized inclined configuration, which is retained by the head plateau as piston 430 moves in the first direction, pressing spring 440a further into the groove and allowing passage of the shoulder 431 in the first direction after the compressed spring 440a in the second inclined compressed configuration. The piston head also reengages the inner end of the static support sleeve 450, pushing it further out into the bore in a manner essentially similar to the transitions previously described in the fourth example, so that the first spring 440a is maintained in the second configuration. through the piston plateau 430.

[00122] In the position of Fig 48, the piston 430 is checked against continuous axial movement in the first direction (of the arrow in Fig 48) by the spring 440b, engaged against the outer face of the shoulder 431 in the first configuration. Like the fourth example, transitions of piston 430 in alternating directions do not require movement of piston 430 all the way to bore 410b. The remaining first spring 440a in the second configuration acts as a stop in the opposite direction to resist axial movement of the piston 430 in the second direction beyond the position shown in Fig. 49, in which the spring 440a is engaged with the inner face of the shoulder 431, without require additional movement of the 430 piston back to the bore. Therefore, the reduction in fluid pressure acting on piston 430 after the position of Fig 49 causes the spring to move piston 430 once again in the first direction (see arrow in Fig 50), so that shoulder 431 engages with the third spring 440c and stops.

[00123] A further increase in fluid pressure again drives piston 430 in the second direction back into bore 410b to uncover the open end of the groove housing in third spring 440c, which adopts the neutral position while spring 440b is held in the second configuration through the profiled region of the plateau. Note that the first spring 440a is not supported by the head in the position of Fig 50 and is also in the neutral position. Also note that the spring 440b in the second configuration engages with the inner face of the shoulder 431, in this example also at the same angle as the outer face that engaged the springs 440 when the piston is moving in the first direction, therefore stopping the reset movement. of piston 430 in the second direction. This reciprocating movement of the piston 430 continues with the piston only withdrawing one step during reset pressurization, until the inner end of the piston moves axially a distance sufficient to alter the flow paths at the inner end of the piston 430.

[00124] Valve 401 can be reset by moving support sleeve 450 as previously described for other examples.

Claims (26)

1. Actuator assembly for an oil, gas or water well, characterized in that it comprises: a fixed member (10, 110, 210, 310, 410) having an axis; an actuating member (30, 130, 230, 330, 430) being axially movable with respect to the fixed member (10, 110, 210, 310, 410); a plurality of open-end recesses (20, 120, 220) in one of the fixed member (10, 110, 210, 310, 410) and the actuating member (30, 130, 230, 330, 430) in which each recess (20, 120, 220) at least partially houses an inclined helical spring (40, 140, 240, 340, 440); and a shoulder extending radially (31, 131, 231, 331, 431) over the other of the fixed member (10, 110, 210, 310, 410) and the actuating member (30, 130, 230, 330, 430 ) adapted to engage an inclined helical spring (40, 140, 240, 340, 440) housed within a recess (20, 120, 220); and a support member (50, 150, 250, 350, 450) adapted to cover the open ends of the recesses (20, 120, 220) and being axially movable in different axial positions relative to the recesses (20, 120, 220) to discover open ends of different recesses (20, 120, 220) at different axial positions of the support member (50, 150, 250, 350, 450). 2. Actuator assembly according to claim 1, characterized by the fact that the actuation member (30, 130, 230, 330, 430) is movable with respect to the support member (50, 150, 250, 350, 450). 3. Actuator assembly according to claim 2, characterized by the fact that when the actuating member (30, 130, 230, 330, 430) moves relative to the supporting member (50, 150, 250, 350 , 450) in one direction, the support member (50, 150, 250, 350, 450) maintains its position relative to the inclined coil spring (40, 140, 240, 340, 440). 4. Actuator assembly according to any one of claims 1 to 3, characterized in that the cover of the open end of a recess (20, 120, 220) maintains a minimum level of compression of the inclined helical spring (40, 140, 240, 340, 440) within the recess (20, 120, 220), and wherein uncovering the open end of a recess (20, 120, 220) allows expansion of the inclined helical spring (40, 140, 240 , 340, 440) of the recess (20, 120, 220). 5. Actuator assembly according to any one of claims 1 to 4, characterized in that the support member (50, 150, 250, 350, 450), the fixed member (10, 110, 210, 310, 410) and the actuating member (30, 130, 230, 330, 430) are concentric. 6. Actuator assembly according to any one of claims 1 to 5, characterized in that at least one inclined helical spring (40, 140, 240, 340, 440) is movable in the recess (20, 120, 220) between the first and second inclined configurations within the recess (20, 120, 220), with a main axis of the inclined coil spring (40, 140, 240, 340, 440) being inclined through a radius of the axis of the fixed member ( 10, 110, 210, 310, 410) in each of the first and second inclined configurations, wherein the inclined coil spring (40, 140, 240, 340, 440) is retained in one of the first and second configurations when the end is open of its recess (20, 120, 220) is covered, and wherein in the first inclined configuration, the main axis of the inclined helical spring (40, 140, 240, 340, 440) is generally aligned or parallel to a first diagonal of the recess (20, 120, 220), and wherein in the second inclined configuration, the main axis of the inclined helical spring (40, 140, 240, 340, 440) is generally aligned or parallel to a second diagonal of the recess (20, 120, 220). 7. Actuator assembly according to claim 6, characterized by the fact that in the first inclined configuration of the inclined helical spring (40, 140, 240, 340, 440), an outer end of the inclined helical spring (40, 140, 240, 340, 440) at the open end of the recess (20, 120, 220) is axially closer to the shoulder (31, 131, 231, 331, 431) than an inner end of the inclined coil spring (40, 140, 240 , 340, 440) at the inner end of the recess (20, 120, 220). 8. Actuator assembly according to claim 6 or 7, characterized in that engaging an inclined helical spring (40, 140, 240, 340, 440) in the first inclined configuration with the shoulder (31, 131, 231, 331, 431) resists compression of the inclined coil spring (40, 140, 240, 340, 440) in the recess (20, 120, 220) and resists axial movement of the shoulder (31, 131, 231, 331, 431 ) after the open end of the recess (20, 120, 220). 9. Actuator assembly according to any one of claims 6 to 8, characterized by the fact that in the first inclined configuration, the main axis of the inclined helical spring (40, 140, 240, 340, 440) is facing axially towards to the shoulder (31, 131, 231, 331, 431). 10. Actuator assembly according to any one of claims 6 to 9, characterized by the fact that in the second inclined configuration of the inclined helical spring (40, 140, 240, 340, 440), the inclined helical spring (40, 140 , 240, 340, 440) allows the compression of the inclined coil spring (40, 140, 240, 340, 440) in the recess (20, 120, 220), and in which the engagement of an inclined coil spring (40, 140, 240, 340, 440) in the second inclined configuration with the shoulder (31, 131, 231, 331, 431) allows axial movement of the shoulder (31, 131, 231, 331, 431) in addition to the inclined helical spring (40, 140 , 240, 340, 440). 11. Actuator assembly according to any one of claims 6 to 10, characterized in that the inclined helical spring (40, 140, 240, 340, 440) adopts a neutral configuration in transition between the two inclined configurations, and wherein in the neutral configuration of the inclined coil spring (40, 140, 240, 340, 440), the inclined coil spring (40, 140, 240, 340, 440) can be moved in the recess (20, 120, 220) between the two different inclined configurations by the axial movement of the actuating member (30, 130, 230, 330, 430) or the supporting member (50, 150, 250, 350, 450) relative to the inclined helical spring (40, 140, 240 , 340, 440). 12. Actuator assembly according to any one of claims 1 to 11, characterized in that when the shoulder (31, 131, 231, 331, 431) engages the end of the inclined helical spring (40, 140, 240, 340, 440) extending from the open end of the recess (20, 120, 220), a leading end of the actuation member (30, 130, 230, 330, 430) covers the open end of the recess (20, 120 , 220). 13. Actuator assembly according to any one of claims 1 to 12, characterized in that the support member (50, 150, 250, 350, 450) comprises a sleeve, with a hole with an axis. 14. Actuator assembly according to any one of claims 1 to 13, characterized in that the actuating member (30, 130, 230, 330, 430) comprises a piston sealed within a hole, and in which the actuation member is sealed within the hole by more than one seal (34, 134, 234, 334), dividing portions of the hole into different zones between the seals (34, 134, 234, 334). 15. Actuator assembly according to any one of claims 1 to 14, characterized in that the actuating member is axially tilted in a first direction by a resilient biasing device. 16. Actuator assembly according to claim 15, characterized by the fact that the axial movement of the actuating member (30, 130, 230, 330, 430) can be controlled by controlling a fluid pressure differential that opposes the strength of the resilient device. 17. Actuator assembly according to any one of claims 1 to 16, characterized in that the support member (50, 150, 250, 350, 450) can move axially relative to the inclined helical spring (40, 140, 240, 340, 440) in response to axial movement of the actuating member (30, 130, 230, 330, 430). 18. Actuator assembly according to any one of claims 1 to 17, characterized in that the shoulder (31, 131, 231, 331, 431) has first and second faces facing opposite directions, wherein the first face of the shoulder (31, 131, 231, 331, 431) is adapted to engage with an inclined helical spring (40, 140, 240, 340, 440) in a first configuration to lock the movement of the actuating member (30, 130, 230, 330, 430) in a first direction, and wherein the second face of the shoulder (31, 131, 231, 331, 431) is adapted to engage with an inclined helical spring (40, 140, 240, 340, 440) in a second configuration to lock movement of the actuating member (30, 130, 230, 330, 430) in a second direction. 19. Valve (1), characterized by the fact that it comprises an actuator assembly, as defined in any one of claims 1 to 18. 20. Method for actuating a tool for an oil, gas or water well, characterized in that the tool is an actuator assembly comprising: a fixed member (10, 110, 210, 310, 410) having an axis; an actuation member (30, 130, 230, 330, 430) movable axially with respect to the fixed member; a plurality of open-end recesses (20, 120, 220) in one of the fixed member (10, 110, 210, 310, 410) and the actuating member (30, 130, 230, 330, 430) in which each recess (20, 120, 220) at least partially houses an inclined helical spring (40, 140, 240, 340, 440); and a shoulder extending radially (31, 131, 231, 331, 431) over the other of the fixed member (10, 110, 210, 310, 410) and the actuating member (30, 130, 230, 330, 430 ) adapted to engage an inclined helical spring (40, 140, 240, 340, 440) housed within a recess (20, 120, 220); and a support member (50, 150, 250, 350, 450) adapted to cover the open ends of the recesses (20, 120, 220) and being axially movable in different axial positions relative to the recesses (20, 120, 220) ; and wherein the method includes: moving the actuating member (30, 130, 230, 330, 430) axially relative to the fixed member (10, 110, 210, 310, 410); move the support member (50, 150, 250, 350, 450) past at least a portion of an open end of a recess (20, 120, 220) housing an inclined coil spring (40, 140, 240, 340 , 340, 440); and restricting axial movement of the actuating member (30, 130, 230, 330, 430) by engaging the shoulder (31, 131, 231, 331, 431) with at least a portion of the inclined helical spring (40, 140, 240, 340, 440) extending from the open end of the recess (20, 120, 220). 21. Method according to claim 20, characterized by the fact that the actuating member (30, 130, 230, 330, 430) pushes the supporting member (50, 150, 250, 350, 450) between its different axial positions. 22. Method according to claim 20 or 21, characterized in that the actuation member (30, 130, 230, 330, 430) moves the support member (50, 150, 250, 350, 450) in only one direction in relation to the inclined coil spring (40, 140, 240, 340, 440). 23. Method according to any one of claims 20 to 22, characterized by the fact that when the actuation member (30, 130, 230, 330, 430) moves axially away from the support member (50, 150, 250, 350, 450), the support member (50, 150, 250, 350, 450) retains its position relative to the inclined coil spring (40, 140, 240, 340, 440) and does not move with the actuation member ( 30, 130, 230, 330, 430). 24. Method according to any one of claims 20 to 23, characterized by the fact that axial movement of the actuating member (30, 130, 230, 330, 430) in a first direction moves the support member (50, 150, 250, 350, 450) in the first direction, so that the supporting member (50, 150, 250, 350, 450) moves with the actuating member (30, 130, 230, 330, 430) in the first direction, and wherein upon subsequent axial movement of the actuating member (30, 130, 230, 330, 430) in a second direction opposite to the first direction, the actuating member (30, 130, 230, 330, 430) and the supporting member (50, 150, 250, 350, 450) separate, with the supporting member (50, 150, 250, 350, 450) optionally remaining static, and maintaining its position, while the actuating member (30 , 130, 230, 330, 430) moves axially away from the support member (50, 150, 250, 350, 450) in the second direction. 25. Method according to any one of claims 20 to 24, characterized in that it includes changing the configuration of the inclined helical springs (40, 140, 240, 340, 440) in the recesses (20, 120, 220) by movement of the actuating member (30, 130, 230, 330, 430) through the uncovered free ends of the recesses (20, 120, 220). 26. Method according to claim 25, characterized by the fact that it includes displacing the inclined helical springs (40, 140, 240, 340, 440) between different inclined positions by moving the actuating member (30, 130, 230, 330, 430) through the free ends of the recesses (20, 120, 220) first in one direction and then in the opposite direction.