Patent Application
20180202475
The field of the disclosure relates generally to oil and gas downhole pump assemblies and, more specifically, to hydraulic actuators for use in oil and gas pumping operations.
At least some known rod pumps are used in oil and gas wells, for example, to pump fluids from subterranean depths towards the surface. In operation, a pump assembly is placed within a well casing, well fluid enters the casing through perforations, and mechanical lift forces the fluids from subterranean depths towards the surface. For example, at least some known rod pumps utilize a downhole pump with complicated geometry, which by reciprocating action of a rod string, lifts the well fluid towards the surface.
In some known oil and gas well pump systems, one or more actuators may be used to facilitate the reciprocating action required for pumping fluid. In certain known systems, such actuators rely on one or more electronic components for providing power and/or control. However, due to the harsh conditions inherent in downhole pumping operations, electronic components can be subject to reduced reliability, significantly reducing the operational life of the actuator and increasing costs and downtime for repairs and replacements. Moreover, operators must rely on batteries with limited lifespans, expensive downhole generators, and/or long power supply lines to provide adequate power to the electronic components.
In one aspect, a hydraulic actuator for a downhole pump is provided. The hydraulic actuator includes a piston housing having a head end and a base end opposite the head end. A drive piston disposed within the piston housing is movable between a first piston position proximate to the head end and a second piston position proximate to the base end. The hydraulic actuator further includes a control valve positionable between a first control valve position and a second control valve position. In the first control valve position, the control valve is configured to direct fluid into the base end, and in the second control valve position, the control valve is configured to direct fluid into the head end. The hydraulic actuator also includes a mechanical position feedback system configured to translate the control valve from the first control valve position to the second control valve position in response to the drive piston moving to the first piston position. The mechanical position feedback system further translates the control valve from the second control valve position to the first control valve position in response to the drive piston moving to the second piston position.
In a further aspect, a downhole pump system is provided. The downhole pump system includes a piston rod pump assembly and a hydraulic actuator coupled to the piston rod pump assembly. The hydraulic actuator includes a piston housing having a head end and a base end opposite the head end. A drive piston disposed within the piston housing is movable between a first piston position proximate to the head end and a second piston position proximate to the base end. The hydraulic actuator further includes a control valve positionable between a first control valve position and a second control valve position. In the first control valve position, the control valve is configured to direct fluid into the base end, and in the second control valve position, the control valve is configured to direct fluid into the head end. The hydraulic actuator also includes a mechanical position feedback system configured to translate the control valve from the first control valve position to the second control valve position in response to the drive piston moving to the first piston position. The mechanical position feedback system further translates the control valve from the second control valve position to the first control valve position in response to the drive piston moving to the second piston position.
In another aspect, a method of controlling a hydraulic actuator is provided. The hydraulic actuator includes a piston housing having a head end and a base end opposite the head end. The hydraulic actuator further includes a drive piston disposed within the piston housing and movable between a first piston position proximate to the head end and a second piston position proximate to the base end. The hydraulic actuator also includes a control valve positionable between a first control valve position and a second control valve position. In the first control valve position, the control valve directs fluid into the base end of the piston housing. In the second control valve position, the control valve directs fluid into the head end of the piston housing. The method includes determining, using a mechanical position feedback system, that the drive piston has moved into the second piston position. The method further includes transitioning, in response to determining that the piston has moved into the second position, the control valve from the second control valve position to the first control valve position. The method also includes determining that the piston has moved into the first piston position and transitioning, in response to determining that the piston has moved into the first piston position, the control valve from the first control valve position to the second control valve position.
These and other features, aspects, and advantages of the present disclosure will become better understood when the following detailed description is read with reference to the accompanying drawings in which like characters represent like parts throughout the drawings, wherein:
Unless otherwise indicated, the drawings provided herein are meant to illustrate features of embodiments of the disclosure. These features are believed to be applicable in a wide variety of systems comprising one or more embodiments of the disclosure. As such, the drawings are not meant to include all conventional features known by those of ordinary skill in the art to be required for the practice of the embodiments disclosed herein.
In the following specification and the claims, reference will be made to a number of terms, which shall be defined to have the following meanings.
The singular forms “a”, “an”, and “the” include plural references unless the context clearly dictates otherwise.
“Optional” or “optionally” means that the subsequently described event or circumstance may or may not occur, and that the description includes instances where the event occurs and instances where it does not.
Approximating language, as used herein throughout the specification and claims, may be applied to modify any quantitative representation that could permissibly vary without resulting in a change in the basic function to which it is related. Accordingly, a value modified by a term or terms, such as “about”, “approximately”, and “substantially”, are not to be limited to the precise value specified. In at least some instances, the approximating language may correspond to the precision of an instrument for measuring the value. Here and throughout the specification and claims, range limitations may be combined and/or interchanged; such ranges are identified and include all the sub-ranges contained therein unless context or language indicates otherwise.
The actuator assemblies and associated methods described herein facilitate extending pump operation in harsh oil and gas well environments. Specifically, actuator assemblies described herein include a control valve configured to induce reciprocating motion of piston assemblies. To do so, the control valve alternately directs pressurized hydraulic fluid into a head end and base end of the piston section, inducing corresponding movement of a drive piston disposed within the piston section. The control valve is switched between two configurations, each configuration corresponding to a different fluid flow path, in response to feedback provided by a mechanical position feedback system. The mechanical position feedback system is configured to induce transition of the control valve in response to the drive piston travelling to a first piston position corresponding to a head end of the piston section and a second piston position corresponding to a base end of the piston section.
Pump assembly 110 includes a piston rod pump assembly 112 and a hydraulic actuator 114 configured to actuate piston rod pump assembly 112. Hydraulic actuator 114 generally includes a hydraulic power section 116, a control section 118, and a piston section 120. During operation, a drive piston 122 disposed within piston section 120 is driven by hydraulic power section 116 subject to control by control section 118. More specifically, power section 116 provides pressurized hydraulic fluid to drive piston 122 while control section 118 dynamically redirects the pressurized hydraulic fluid provided by power section 116 to facilitate reciprocation of drive piston 122.
During operation, and with reference to
Control valve 230 switches between the first control valve position and the second control valve position in response to position feedback provided by mechanical position feedback system 240. In the exemplary embodiment, mechanical position feedback system 240 includes a first mini piston cylinder 232, a second mini piston cylinder 234, and a mechanical linkage 238. Mechanical linkage 238 further includes a piston rod 254 coupled to drive piston 122 and an extension 256 coupled to piston rod 254. Accordingly, as drive piston 122 translates between first piston position 250 and second piston position 252, extension 256 similarly translates.
First mini piston cylinder 232 and second mini piston cylinder 234 are coupled in fluid communication with control valve 230 through a first hydraulic control line 258 and a second hydraulic control line 260, respectively. In the exemplary embodiment, control valve 230 is a two-position, detented, four-way directional valve. Alternatively, control valve 230 may be a three-position, detented, four-way valve or any other valve configuration that enables pump system 100 to function as described herein. In the exemplary embodiment, control valve 230 includes an internal mechanical detent that facilitates holding the valve in position until a minimum pilot fluid pressure is applied to a pilot port (not shown) of control valve 230. For example, in the exemplary embodiment, control valve 230 is switched between the first control valve position and the second control valve position by applying the minimum pilot fluid pressure to a pilot port, where control valve 230 remains in that position, with no pilot fluid pressure applied, until a new pilot fluid pressure signal is temporarily applied to the opposite pilot port. More specifically, control valve 230 is configured to transition into the first control valve position in response to a predetermined fluid pressure within first hydraulic control line 258, and to transition into the second control valve position in response to a predetermined fluid pressure within second hydraulic control line 260.
During operation, the predetermined fluid pressures within first hydraulic control line 258 and second hydraulic control line 260 are facilitated by extension 256 actuating first mini piston cylinder 232 and second mini piston cylinder 234, respectively. More specifically, first mini piston cylinder 232 and second mini piston cylinder 234 are disposed relative to each other and to extension 256 such that extension 256 actuates first mini piston cylinder 232 when drive piston 122 translates into first piston position 250, and actuates second mini piston cylinder 234 when drive piston 122 translates into second piston position 252.
In the exemplary embodiment, control valve 230 is configured to remain in position until the predetermined fluid pressure within one of first hydraulic control line 258 and second hydraulic control line 260 is achieved. Accordingly, control valve 230 continues to direct fluid into head end 246 and base end 248 until drive piston 122 is substantially in second piston position 234 and first piston position 232, respectively.
In certain embodiments, hydraulic actuator 114 includes features configured to reduce impact forces of components as drive piston 122 reciprocates within piston housing 236. For example, each of first mini piston cylinder 232 and second mini piston cylinder 234 include a spring 262 and 264, respectively, configured to facilitate decelerating first mini piston cylinder 232 and second mini piston cylinder 234 during actuation by extension 256. Similarly, piston housing 236 may further include deceleration features configured to decelerate drive piston 122 as it approaches head end 246 and base end 248. For example, piston housing 236 defines a plurality of longitudinal grooves 266 proximate to head end 246 and base end 248 such that as drive piston 122 approaches head end 246 and base end 248, a pressure differential across drive piston 122 is reduced due to leakage of the fluid through groove 266, causing deceleration of drive piston 122. In alternative embodiments, piston housing 236 includes other deceleration features for example, and without limitation, springs and bumpers disposed in head end 246 and base end 248 to facilitate deceleration of drive piston 122 and/or hydraulic cushioning features including a tapered piston bore and similar tapered features on drive piston 122.
During operation, drive piston 422 reciprocates between a first piston position 450 proximate to a head end 446 of piston housing 436 and a second piston position 452 proximate to a base end 448 of piston housing 436. To facilitate reciprocation of drive piston 422, control valve 230 is configured to alternatively direct fluid from actuator pump 226 to head end 446 and base end 448 in response to the position of drive piston 422. More specifically, as described herein, control valve 230 is configured to operate in a first control valve position in which pressurized fluid provided by actuator pump 226 is directed into head end 446 and a second control valve position in which the pressurized fluid is directed into base end 448. As pressurized fluid is provided into head end 446, drive piston 422 is moved to second piston position 452 proximate to base end 448. Similarly, as pressurized fluid is provided into base end 448, drive piston 422 is moved to first piston position 450 proximate to head end 446. Accordingly, as control valve 230 alternates between the first control valve position and the second control valve position, drive piston 422 reciprocates within piston housing 436.
Control valve 230 switches between the first control valve position and the second control valve position in response to position feedback provided by mechanical position feedback system 440. In hydraulic actuator 400, mechanical position feedback system 440 includes first mini piston cylinder 432, second mini piston cylinder 434, and cable 462. First mini piston cylinder 432 and second mini piston cylinder 434 are coupled in fluid communication with control valve 230 through a first hydraulic control line 458 and a second hydraulic control line 460, respectively. Control valve 230 is further configured to switch into the first control valve position in response to a predetermined fluid pressure within first hydraulic control line 458 and to switch into the second control valve position in response to a predetermined fluid pressure within second hydraulic control line 460.
In the exemplary embodiment, first mini piston cylinder 432 and second mini piston cylinder 434 are disposed in head end 446 of piston housing 436, and actuate in response to drive piston 422 moving into first piston position 450 and second piston position 452. When actuated, first mini piston cylinder 432 causes an increase in pressure within first hydraulic control line 458. First mini piston cylinder 432 is configured to actuate by being depressed by drive piston 422 as drive piston 422 moves into first piston position 450. Similarly, second mini piston cylinder 434 is configured to cause an increase in pressure within second hydraulic control line 460 when actuated. Second mini piston cylinder 434 is configured to be actuated by being pulled by drive piston 422 as drive piston 422 moves into second piston position 452 by cable 462.
During operation, drive piston 522 reciprocates between a first piston position 550 proximate to a head end 546 of piston housing 536 and a second piston position 552 proximate to a base end 548 of piston housing 536. To facilitate reciprocation of drive piston 522, control valve 230 is configured to alternatively direct fluid from actuator pump 226 to head end 546 and base end 548 in response to the position of drive piston 522. More specifically, control valve 230 is configured to operate in a first control valve position in which pressurized fluid provided by actuator pump 226 is directed into head end 546 and a second control valve position in which the pressurized fluid is directed into base end 548. As the pressurized fluid is provided into head end 546, drive piston 522 moves to second piston position 552 proximate to base end 448. Similarly, as the pressurized fluid is provided into base end 548, drive piston 522 moves to first piston position 550 proximate to head end 546. Accordingly, as control valve 230 alternates between the first control valve position and the second control valve position, drive piston 522 reciprocates within piston housing 536.
Control valve 230 switches between the first control valve position and the second control valve position in response to position feedback provided by mechanical position feedback system 540. In hydraulic actuator 500, mechanical position feedback system 540 includes extension 556 and mechanical linkage 538. During operation, extension 556 contacts mechanical linkage 538 as drive piston 522 moves into first piston position 550 and second piston position 552, causing mechanical linkage 538 to translate. Due to the coupling of mechanical linkage 538 to control valve 230, translation of mechanical linkage 538 facilitates transition of control valve 230 between the first control valve position and the second control valve position. Furthermore, as described herein, control valve 230 includes an internal mechanical detent that facilitates holding the valve in position. In certain embodiments, mechanical linkage 538 is supported by a linear bearing 564 configured to maintain alignment and reduce friction during translation of mechanical linkage 538.
Method 600 includes determining 602, using mechanical position feedback system 240, that drive piston 122 has moved into second piston position 252. For example, in hydraulic actuator 114, mechanical position feedback system 240 includes extension 256 coupled to piston rod 254 that is in turn coupled to drive piston 122. As drive piston 122 moves into second piston position 252, extension 256 is configured to actuate first mini piston cylinder 232.
Method 600 further includes transitioning 604, in response to determining that drive piston 122 has moved into second piston position 252, control valve 230 into the first control valve position. In the first control valve position, control valve 230 is configured to direct fluid into base end 248 of piston housing 236. In hydraulic actuator 114, for example, first mini piston cylinder 232 is coupled to control valve 230 by a first hydraulic control line 258. Accordingly, when first mini piston cylinder 232 is actuated by extension 256, pressure within first hydraulic control line 258 is increased, facilitating transition of control valve 230 into the first control valve position.
Method 600 also includes determining 606, using mechanical position feedback system 240, that drive piston 122 has moved into first piston position 250. For example, in hydraulic actuator 114, as drive piston 122 translates into first piston position 250, extension 256 is configured to actuate a second mini piston cylinder 234.
Method 600 further includes transitioning 608, in response to determining that drive piston 122 has moved into first piston position 250, control valve 230 into the second control valve position. In the second control valve position, control valve 230 is configured to direct fluid into head end 246 of piston housing 236. In hydraulic actuator 114, for example, second mini piston cylinder 234 is coupled to control valve 230 by a second hydraulic control line 260. Accordingly, when second mini piston cylinder 234 is actuated by extension 256, pressure within second hydraulic control line 260 is increased, facilitating transition of control valve 230 into the second control valve position. As indicated in
The actuator assemblies described herein facilitate extending pump operation in harsh oil and gas well environments. Specifically, the actuator assemblies described herein facilitate reciprocation of a drive piston using hydraulic power and a mechanical position feedback system. The mechanical positional feedback system is configured to translate a control valve to alternately direct fluid into a head end and a base end of a piston housing. As the drive piston reaches either the head end or the base end, the mechanical position feedback system switches the control valve to direct fluid into the piston housing to facilitate movement of the drive piston in the opposite direction.
An exemplary technical effect of the methods, systems, and section described herein includes at least one of: (a) improving reliability of actuator assemblies as compared to electronically controlled actuator assemblies; (b) improving the operational life of actuator assemblies; (c) improving the service life of downhole pump systems including actuator assemblies; and (d) reducing downhole pump operating costs.
Exemplary embodiments of methods, systems, and apparatus for actuator assemblies are not limited to the specific embodiments described herein, but rather, components of systems and/or steps of the methods may be utilized independently and separately from other components and/or steps described herein. For example, the methods, systems, and apparatus may also be used in combination with other pumping systems outside of the oil and gas industry. Rather, the exemplary embodiment can be implemented and utilized in connection with many other applications, equipment, and systems that may benefit from improved reciprocating actuator assemblies.
Although specific features of various embodiments of the disclosure may be shown in some drawings and not in others, this is for convenience only. In accordance with the principles of the disclosure, any feature of a drawing may be referenced and/or claimed in combination with any feature of any other drawing.
This written description uses examples to disclose the embodiments, including the best mode, and also to enable any person skilled in the art to practice the embodiments, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the disclosure is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they have structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal language of the claims.
