US20160376871A1 - Valve actuator - Google Patents

Valve actuator Download PDF

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Publication number
US20160376871A1
US20160376871A1 US14/902,137 US201414902137A US2016376871A1 US 20160376871 A1 US20160376871 A1 US 20160376871A1 US 201414902137 A US201414902137 A US 201414902137A US 2016376871 A1 US2016376871 A1 US 2016376871A1
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United States
Prior art keywords
actuator
tubular body
port
fluid
chamber
Prior art date
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Abandoned
Application number
US14/902,137
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English (en)
Inventor
Ted Jee Voon
Andre Willy
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Managed Pressure Operations Pte Ltd
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Managed Pressure Operations Pte Ltd
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Application filed by Managed Pressure Operations Pte Ltd filed Critical Managed Pressure Operations Pte Ltd
Assigned to Managed Pressure Operations Pte. Ltd. reassignment Managed Pressure Operations Pte. Ltd. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: VOON, Ted Jee, WILLY, ANDRE
Publication of US20160376871A1 publication Critical patent/US20160376871A1/en
Abandoned legal-status Critical Current

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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B21/00—Methods or apparatus for flushing boreholes, e.g. by use of exhaust air from motor
    • E21B21/10—Valve arrangements in drilling-fluid circulation systems
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B34/00—Valve arrangements for boreholes or wells
    • E21B34/06—Valve arrangements for boreholes or wells in wells
    • E21B34/10—Valve arrangements for boreholes or wells in wells operated by control fluid supplied from outside the borehole
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B21/00—Methods or apparatus for flushing boreholes, e.g. by use of exhaust air from motor
    • E21B21/10—Valve arrangements in drilling-fluid circulation systems
    • E21B21/103—Down-hole by-pass valve arrangements, i.e. between the inside of the drill string and the annulus
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B21/00—Methods or apparatus for flushing boreholes, e.g. by use of exhaust air from motor
    • E21B21/10—Valve arrangements in drilling-fluid circulation systems
    • E21B21/106—Valve arrangements outside the borehole, e.g. kelly valves
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B34/00—Valve arrangements for boreholes or wells
    • E21B34/06—Valve arrangements for boreholes or wells in wells
    • E21B34/14—Valve arrangements for boreholes or wells in wells operated by movement of tools, e.g. sleeve valves operated by pistons or wire line tools
    • E21B2034/007—
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B2200/00—Special features related to earth drilling for obtaining oil, gas or water
    • E21B2200/04—Ball valves
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B2200/00—Special features related to earth drilling for obtaining oil, gas or water
    • E21B2200/06—Sleeve valves

Definitions

  • the present invention relates to a valve actuator, particularly, but not exclusively, for use in actuating a rotatable valve member mounted in a tubular used in oil or gas drilling and/or production.
  • the drilling of a borehole or well is typically carried out using a steel pipe known as a drill pipe or drill string with a drill bit on the lowermost end.
  • the drill string comprises a series of tubular sections, which are connected end to end.
  • the entire drill string may be rotated using a rotary table, or using an over-ground drilling motor mounted on top of the drill pipe, typically known as a ‘top-drive’, or the drill bit may be rotated independently of the drill string using a fluid powered motor or motors mounted in the drill string just above the drill bit.
  • a flow of mud is used to carry the debris created by the drilling process out of the borehole. Mud is pumped down the drill string to pass through the drill bit, and returns to the surface via the annular space between the outer diameter of the drill string and the borehole (generally referred to as the annulus).
  • the mud flow also serves to cool the drill bit, and to pressurise the borehole, thus substantially preventing inflow of fluids from formations penetrated by the drill string from entering into the borehole.
  • Mud is a very broad drilling term and in this context it is used to describe any fluid or fluid mixture used during drilling and covers a broad spectrum from air, nitrogen, misted fluids in air or nitrogen, foamed fluids with air or nitrogen, aerated or nitrified fluids to heavily weighted mixtures of oil and or water with solid particles.
  • the mud is typically pumped into the drill string using one or more positive displacement pumps which are connected to the top of the drill string via a pipe and manifold.
  • the main mud flow into the well bore is achieved by pumping mud into a main, axial, passage at the very top end of the drill string
  • Stopping mud flow in the middle of the drilling process is problematic for a number of reasons, and it has been proposed to facilitate continuous pumping of mud through the drill string by the provision of a side passage, typically in each section of drill string. This means that mud can be pumped into the drill string via the side passage whilst the top of the drill string is closed, the top drive disconnected and the new section of drill string being connected.
  • a side passage which is closed using a plug, and a valve member which is pivotable between a first position in which the side passage is closed whilst the main passage of the drill string is open, and a second position in which the side passage is open whilst the main passage is closed.
  • the valve is retained in the first position, but when it is time to increase the length of the drill string, the plug is removed from the side passage, and a hose, which extends from the pump, connected to the side passage, and a valve in the hose opened so that pumping of mud into the drill string via the side passage commences.
  • a valve in the main hose from the pump to the top of the drill string is then closed, and the pressure of the mud at the side passage causes the valve member to move from the first position to the second position, and hence to close the main passage of the drill string.
  • the main hose is then disconnected, the new section of tubing mounted on the drill string, and the main hose connected to the top of the new section.
  • the valve in the main hose is opened so that pumping of mud into the top of the drill string is recommenced, and the valve in the hose to the side passage closed.
  • the resulting pressure of mud entering the top of the drill string causes the valve member to return to its first position, which allows the hose to be removed from the side passage, without substantial leakage of mud from the drill string.
  • the side passage may then be sealed permanently, for example by welding or screwing a plug into the side passage, before this section of drill string is lowered into the well.
  • This process is commonly referred to as continuous circulation drilling.
  • valve members instead of providing a single valve member which is operable to close either the side passage or the main passage of the drill string, it is known to provide two separate valve members—a main valve member which is operable to close the main passage, and an auxiliary valve member which is operable to close the side passage.
  • the separate valve members may each have its own actuation mechanism, for example as disclosed in WO2010/046653.
  • FIGS. 1 a and 1 b A further alternative arrangement in which the actuator for the main valve member is combined with the auxiliary valve member is disclosed in WO2012/085597. This arrangement is illustrated in FIGS. 1 a and 1 b.
  • the main valve member 16 comprises a ball which is mounted in the main passage 12 of the drill string 10 , and which is rotatable about an axis generally perpendicular to the longitudinal axis of the drill string, between an open position in which flow of fluid along the main passage 12 is permitted, and a closed position in which it prevents flow of fluid along the main passage 12 .
  • Rotation of the ball 16 between the open position and the closed position is achieved using a tubular actuator 18 , which is also mounted within the main passage 12 of the drill string 10 , coaxially with the drill string 10 .
  • the actuator 18 is connected to the ball 16 such that sliding movement of the 18 in the drill string 10 causes the ball 16 to move between the closed position and the open position.
  • the actuator 18 also acts to block or unblock the side passage 14 as it slides along the drill string, and is configured to open the side passage 14 when the main valve 16 is in the closed position, and to close the side passage 14 when the main valve 16 is in the open position.
  • the actuator 18 is hydraulically actuated by mean of an actuation chamber 38 which is provided between the actuator 18 and a lining 10 a provided in the wall of the drill string 10 . This is best illustrated in FIG. 1 c , and simply comprises an annular space between the two parts 18 , 10 a .
  • Two ports 40 a , 40 b are provided through the drill string 10 into this chamber 38 , one at each end of the chamber 38 .
  • the first port 40 a is closest to a second end 18 b of the actuator 18 (nearest the main valve member 16 ).
  • the chamber 38 is divided into two by a seal 41 which is mounted on the exterior surface of the actuator 18 .
  • the seal 41 comprises 2 O-rings.
  • the seal 41 substantially prevents flow of fluid between the two parts of the chamber 38 whilst permitting the actuator 18 to slide inside the drill string 10 .
  • the seal 41 ensures that flow of pressurised fluid into this chamber 38 via the first port 40 a causes the actuator 18 to move towards the main valve member 16 , whilst flow of pressurised fluid into the actuation chamber 38 via the second port 40 b acts in the opposite direction to counterbalance the effect of pressurised fluid at the first port 40 a .
  • the actuator 18 therefore acts as a double acting piston with one pressure port 40 a to move the actuator 18 towards the main valve member 16 and one pressure port to move the actuator 18 away from the main valve member 16 .
  • the actuator 18 is operated by means of a pressure differential across the first and second ports 40 a , 40 b.
  • FIG. 1 a illustrates the actuator 18 when supply of pressurised fluid to the port 40 b has pushed it away from the main valve member 16 , so that the actuator 18 closes the side port 14
  • FIG. 1 b illustrates the sleeve 18 when supply of pressurised fluid to the port 40 a has pushed it towards the main valve member 16 , thus opening the side port 14 .
  • Pump in sub which is used in the event of an emergency, for example to facilitate the provision of additional mud pressure required to control a sudden surge in well-bore pressure due to fluid inflow from a formation penetrated by the well entering the well in what is known as a “kick”.
  • This invention relates to an alternative configuration of actuator assembly suitable for use in such a valve arrangement, where operation of the valve is achieved by the sliding of an actuator sleeve relative to the drill string.
  • a fluid pressure operated actuator assembly comprising a tubular body having a wall, with an interior surface and an exterior surface and enclosing a main passage which extends generally parallel to a longitudinal axis of the tubular body, an actuator located in and movable along the main passage, a first direction chamber formed between the wall of the tubular body and the actuator, and at least one second direction chamber formed between the tubular body and the actuator, wherein the assembly is configured such that when the pressure of fluid in the first direction chamber exceeds the pressure of fluid in the or each second direction chamber by a predetermined amount, the pressure of fluid in the first direction chamber exerts a force on the actuator which acts to push the actuator in a first direction relative to the tubular body, and when the pressure of fluid in the or at least one of the second direction chamber(s) exceeds the pressure of fluid in the first direction chamber by a predetermined amount, the pressure of fluid in the second direction chamber(s) exerts a force on the actuator which acts to push the actuator in a second
  • the longitudinal axis of the tubular body extends generally normal to the first plane, second plane and third plane.
  • one or both of the first and second directions is/are generally parallel to the longitudinal axis of the tubular body.
  • the first direction is generally opposite to the second direction.
  • the actuator is connected to a main valve member in such a way that movement of the actuator in the first direction and second direction causes the valve member to move.
  • the main valve member may be movable between a closed position in which the main valve member closes the main passage of the tubular body and an open position in which the main passage of the tubular body is open.
  • the movement of the main valve member caused by the movement of the actuator in the first direction and second direction may comprise rotation.
  • the main valve member moves to the closed position when the actuator moves in the first direction and to the open position when the actuator moves in the second direction.
  • the main valve member may comprise a ball valve member.
  • the actuator may be connected to valve member by means of a track and pin arrangement whereby a pin extends from on of the valve member or actuator into a slot or groove provided in the other of the valve member or actuator, the pin moving along the slot or groove as the actuator slides in the tubular body and the valve member rotates.
  • the tubular body is provided with a side passage which extends through the wall of the tubular body from the exterior of the tubular body into the main passage, and the actuator is movable between a closed position in which the actuator substantially prevents flow of fluid along the side passage, and an open position in which flow of fluid along the side passage is permitted.
  • movement of the actuator in the first direction may bring the actuator into the open position
  • movement of the actuator in the second direction may bring the actuator into the closed position.
  • a main valve member is also provided as described above, movement of the actuator in the first direction may bring the actuator into the open position and the main valve member into the closed position, whilst movement of the actuator in the second direction brings the actuator into the closed position, and the main valve member into the open position.
  • the passage from the third port may connect to the passage from the second port into the or one of the second direction chamber(s).
  • the first direction chamber and the or each second direction chamber may be formed in a space between an exterior surface of the actuator and an interior surface of the wall of the tubular body. This space may extend around the entire perimeter of the actuator. This space may be divided into the first direction chamber and second direction chamber by means of a seal which substantially prevents flow of fluid between the chambers whilst allowing the actuator to move along the main passage of the tubular body. This space may be divided into the first direction chamber and two second direction chambers by means of a seal arrangement which substantially prevents flow of fluid between the chambers whilst allowing the actuator to move along the main passage of the tubular body. The first direction chamber may be located between the two second direction chambers.
  • the passages from the first port, second port and third port into their respective chambers may extend through the tubular body generally perpendicular to its longitudinal axis.
  • at least one of the passages from the first port, second port and third port into their respective chambers may extend through the tubular body generally at an angle of less than 90° to its longitudinal axis.
  • the actuator assembly is configured such that if the pressure in the first direction chamber equals the pressure in the or both second direction chamber(s), there is no net force acting on the actuator, if the pressure in the first direction exceeds the pressure in the or both the second direction chamber(s), there is a net force acting on the actuator pushing the actuator in the first direction, and if the pressure in the first direction chamber is less than the pressure in the or either one of the second direction chamber(s), there is a net force acting on the actuator pushing the actuator the second direction.
  • the actuator assembly is configured such that when the pressure in the first direction chamber equals the pressure in the or both second direction chamber(s), there is a net force acting on the actuator.
  • the actuator assembly may be configured such that this net force tends to push the actuator in the second direction.
  • FIGS. 2 a and 2 b show a longitudinal cross-section through a portion of one embodiment of actuator assembly according to the invention, the actuator having been moved in the second direction in FIG. 2 a and in the first direction in FIG. 2 b,
  • FIGS. 3 a and 3 b show a longitudinal cross-section through a portion of an alternative embodiment of actuator assembly according to the invention, the actuator having been moved in the second direction in FIG. 3 a and in the first direction in FIG. 3 b , AND
  • FIGS. 4 a and 4 b show a longitudinal cross-section through a portion of an alternative embodiment of actuator assembly according to the invention, the actuator having been moved in the second direction in FIG. 4 a and in the first direction in FIG. 4 b.
  • a fluid pressure operated actuator assembly comprising a tubular body 110 having a wall enclosing a main passage 112 which extends generally parallel to a longitudinal axis of the tubular body 110 , an actuator 118 located in and movable along the main passage 112 , a first direction chamber 138 a and a second direction chamber 138 b formed between the wall of the tubular body 110 and the actuator 118 .
  • the tubular body 110 may be part of a drill string or may comprise a sub for mounting in a drill string.
  • both the tubular body 110 and actuator 118 are tubular with a generally circular cross-section.
  • the first direction chamber 138 a and the second direction chamber 138 b are formed in an annular space around the actuator 118 between an exterior surface of the actuator 118 and an interior surface of the tubular body 110 .
  • This space is divided into the first direction chamber 138 a and second direction chamber 138 b by means of a seal 141 which substantially prevents flow of fluid between the chambers 138 a 138 b .
  • Two further seals 118 a , 130 a are provided between the exterior surface of the actuator 118 and the interior surface of the tubular body 110 , one at each end of the annular space.
  • the seals 118 a , 130 a , and 141 each comprise a pair of generally circular O-rings which are located in circumferential grooves around the exterior surface of the actuator 118 . It should be appreciated, however, that the invention is not restricted to the use of this particular type of seal, and any other type of seal which substantially prevents flow of fluid between the actuator 118 and the tubular body 110 whilst allowing the actuator 118 to slide in the tubular body 110 , could be used instead.
  • the seals could equally be mounted on the tubular body 110 rather than on the actuator 118 .
  • the tubular body 110 is provided with a first port 140 a which communicates with a first control passage 139 a extending through the wall of the tubular body 110 from the first port 140 a to the first direction chamber 138 a , a second port 140 b which communicates with a second control passage 139 b extending through the wall of the tubular body 110 from the second port 140 b to the second direction chamber 138 b and a third port 140 c which communicates with a third control passage 139 c extending through the wall of the tubular body 110 from the third port 140 c to the second control passage 139 b .
  • first and second control passages 139 a , 139 b extend through the wall of the tubular body generally perpendicular to its longitudinal axis.
  • the third passage 139 c is inclined at angle of less than 45° to the longitudinal axis of the tubular body.
  • the first and second control passages 139 a , 139 b are co-planar and so both can be seen in the cross-sections illustrated in FIGS. 2 a and 2 b .
  • the third control passage 139 c necessarily extends along a different plane and so is shown in dashed lines in these Figures.
  • the first, second and third ports 140 a , 140 b , 140 c are spaced along the longitudinal axis of the tubular body 110 so that if the first port 140 a is considered to lie on a first imaginary plane, the second port 140 b on a second imaginary plane and the third port 140 c on a third imaginary plane, the first plane, second plane and third plane being generally parallel to one another and generally normal to the longitudinal axis of the tubular body 110 , the first plane lies between the second plane and the third plane.
  • the actuator assembly is configured such that when the pressure of fluid in the first direction chamber 138 a exceeds the pressure of fluid in the second direction chamber 138 b , the pressure of fluid in the first direction chamber 138 a exerts a force on the actuator 118 which acts to push the actuator 118 in a first direction along the main passage 112 in the tubular body 110 , and when the pressure of fluid in the second direction chamber 138 b exceeds the pressure of fluid in the first direction chamber 138 a , the pressure of fluid in the second direction chamber 138 b exerts a force on the actuator 118 which acts to push the actuator 118 in a second, opposite, direction along the main passage 112 in the tubular body 110 .
  • this is achieved by providing the interior of the tubular body 110 with a portion of increased internal diameter 110 a .
  • the interior surface of the tubular body 110 forms a shoulder 110 b , 110 c where the internal diameter of the tubular body 110 decreases slightly.
  • the actuator 118 is substantially longer than the portion of increased internal diameter 110 a and the outer diameter of the actuator 118 is less than the internal diameter of the tubular body 110 either side of the portion of increased internal diameter 110 a .
  • the first direction and second direction chambers 138 a , 138 b are formed between the actuator 118 and the portion of increased internal diameter 110 a , and the seal 141 extends outwardly of the exterior surface of the actuator 118 to engage with the interior surface of increased internal diameter portion 110 a of the tubular body 110 .
  • the first direction chamber 138 a is thus formed between the exterior surface of the actuator 118 , the first shoulder 110 b , part of the increased internal diameter portion of the tubular body 110 , and the seal 141 .
  • the second direction chamber 138 b is formed between the exterior surface of the actuator 118 , the second shoulder 110 c , part of the increased internal diameter portion of the tubular body 110 , and the seal 141 .
  • the fluid pressure pushes the seal 141 away from the first shoulder 110 b to increase the volume of the first direction chamber 138 a .
  • the actuator 118 is therefore pushed in the first direction.
  • the fluid pressure in the second direction chamber 138 b pushes the seal 141 away from the second shoulder 110 c to increase the volume of the second direction chamber 138 b .
  • the actuator 118 is thus pushed in the second direction.
  • the actuator 118 therefore acts as a double acting piston with a first port 140 a to move the actuator 118 in a first direction along the main passage 112 in the tubular body 110 (in this example to the left in FIGS. 2 a and 2 b ) and a second port 140 b or a third port 140 c to move the sleeve 18 in a second direction along the main passage 112 in the tubular body 110 (in this example to the right in FIGS. 2 a and 2 b ).
  • this embodiment differs from the prior art actuator described in WO2012/085597, and GB 2 413 373, for examples, by virtue of the provision of the third port 140 c .
  • the third port 140 c may be advantageous as it may assist in preventing unwanted movement of the actuator 118 when the exterior of the tubular body 110 is exposed to a pressure differential. This is particularly important where the tubular body is portion of a drill string, or a sub mounted in a drill string, and the drill string is used in managed pressure drilling (MPD).
  • MPD managed pressure drilling
  • Managed pressure drilling is a style of drilling in which the bottom hole pressure (BHP) is maintained through various methods including fluid level maintenance, effective fluid density manipulation, applied back pressure, and potentially combinations of these and other practices.
  • BHP bottom hole pressure
  • RCD rotating control device
  • An RCD clamps around the drill string to main fluid pressure differential in the annulus around the drill string (typically there is higher pressure below the RCD), whilst allowing the drill string to rotate as required for drilling.
  • the RCD is intended as a means of isolating one part of the wellbore from another during drilling operations, and can be inserted at any point in a riser string, depending on the application, for the purpose of dual gradient drilling (DGD) or applying back pressure to the riser annulus, or other purposes.
  • DGD dual gradient drilling
  • the RCD therefore creates an irregularity or discontinuity in the overall pressure profile of the well, which, in practical terms, may mean that as the drill string is inserted into the well, a point on the drill string may experience a sudden increase in pressure by 500 psi or more having traveled only 6 inches or less.
  • This differential pressure may act from below a drill string element, i.e. the area of high pressure being lower than the area of low pressure. Differential pressure may also act from above, however, for example if the riser and RCD is configured more toward well control.
  • valve assembly described in WO2012/085597 is reliable in conventional single fluid gradient environments, as the distance between the first and second ports 40 a , 40 b is relatively short. This means that as the portion of the drill string containing these ports 40 a , 40 b is advanced into the well, any pressure differential across the ports as a result of the pressure gradient in the annulus is negligible, and is not sufficient to move the actuator 18 . This may not be the case, however, if the drill string were to pass through a discontinuity in the pressure gradient such as one introduced by an RCD.
  • the actuator 118 should be arranged such that its default or rest position is as illustrated in FIG. 2 b , and is adopted by virtue of the supply of pressurised fluid to the second and/or third ports 140 b , 140 c .
  • a pressure discontinuity such as one introduced by an RCD
  • the second port 140 b is exposed to high pressure (the high pressure also being communicated to the third port 140 c ), whilst the first port 140 a is at low pressure.
  • the high pressure at the second and third ports 140 b , 140 c will act to maintain the actuator 118 in its rest/default position.
  • the first port 140 a will then also be exposed to the high pressure, but as this is balanced by the same high pressure at the second and third ports 140 b , 140 c the actuator 118 will not move.
  • the pressure at all three ports 140 a , 140 b , 140 c is substantially equal.
  • the third port 140 c is exposed to high pressure (which is also communicated to the second port 140 b ), whilst the first port 140 a is at low pressure.
  • the high pressure at the second and third ports 140 b , 140 c will act to maintain the actuator 118 in its rest/default position.
  • the first port 140 a will then also be exposed to the high pressure, but as this is balanced by the same high pressure at the second and third port 140 c , the actuator 118 will still not move.
  • the actuator 118 will not be moved from its default or rest position by the pressure discontinuity, whichever end of the tubular body 110 is exposed to the high pressure first, and the actuator assembly can therefore cope with pressure differential from above and below without unintended actuation.
  • the tubular body 110 is provided with a side passage 114 which extends from the exterior of the body 110 into the main passage 112 .
  • the actuator 118 is provided with a further seal 130 b which provide a substantially fluid tight seal between the actuator 118 and the tubular body 110 to ensure that, when the actuator is in a closed position (illustrated in FIG. 2 b ), the actuator substantially prevents flow of fluid along the side passage 114 .
  • this further seal 130 b comprises two seals each of which is a generally circular O-ring which are located in circumferential grooves around the exterior surface of the actuator 118 .
  • the further seal 130 b and the seal 130 a provided to contain fluid pressure in the first direction chamber 138 a are spaced such that when the actuator 118 is in the closed position, the side port 114 lies between the two seals 130 a , 130 b .
  • the invention is not restricted to the use of this particular type of seal, and any other type of seal which substantially prevents flow of fluid between the actuator 118 and the tubular body 110 whilst allowing the actuator 118 to slide in the tubular body 110 , could be used instead.
  • movement of the actuator 118 from the closed position to the open position comprises movement in the first direction, which movement is, as described above, achieved by supply of pressurised fluid to the first port 140 a .
  • movement of the actuator 118 from the open position to the closed position comprises movement in the second direction, which movement is, as described above, achieved by supply of pressurised fluid to the second or third port 140 b , 140 c .
  • FIG. 2 a illustrates the actuator 118 when supply of pressurised fluid to the first port 140 a has pushed it in the first direction, thus opening the side port 114
  • FIG. 2 b illustrates the actuator 118 when supply of pressurised fluid to the second or third port 140 b , 140 c has pushed it in the second direction, so that the actuator 118 closes the side port 114 .
  • the actuator assembly could equally be configured such that the opposite is true—i.e. movement of the actuator 118 from the closed position to the open position comprises movement in the second direction etc, so that the actuator 118 is brought to or maintained in the open position when it passes through a pressure discontinuity.
  • the actuator 118 is connected to a main valve member (not shown) in such a way that movement of the actuator 118 in the first direction and second direction causes the main valve member to move.
  • the main valve member may be movable between a closed position in which the main valve member closes the main passage 112 of the tubular body 110 and an open position in which the main passage 112 of the tubular body 110 is open.
  • the movement of the main valve member caused by the movement of the actuator 118 in the first direction and second direction may comprise rotation, and the main valve member may be a ball valve.
  • the actuator 118 is connected to valve member by means of a track and pin arrangement whereby a pin extends from one of the valve member or actuator into a slot or groove provided in the other of the valve member or actuator, the pin moving along the slot or groove as the actuator 118 slides in the tubular body 110 and the valve member rotates.
  • a pin extends from one of the valve member or actuator into a slot or groove provided in the other of the valve member or actuator, the pin moving along the slot or groove as the actuator 118 slides in the tubular body 110 and the valve member rotates.
  • Various possible mechanisms whereby the actuator 118 could be connected to the main valve member so that sliding movement of the actuator 118 causes the main valve member to rotate are described in WO 2012/085597, GB 2 413 373, U.S. Pat. No. 3,236,255, GB 1 416 085, U.S. Pat. No. 3,703,193 and U.S. Pat. No. 3,871,447.
  • the main valve member moves to its closed position when the actuator 118 moves in the first direction, which movement is, as described above, achieved by supply of pressurised fluid to the first port 140 a .
  • the main valve moves to its open position when the actuator 118 moves in the second direction, which movement is, as described above, achieved by supply of pressurised fluid to the second or third port 140 b , 140 c .
  • the main valve member is brought to or maintained in its open position when the tubular body 110 passes through a pressure discontinuity such as created by an RCD in a managed pressure drilling situation.
  • the actuator 118 may either facilitate the opening or closing of a side port 114 through the tubular body 110 or control the opening or closing of a main valve member, it is possible for the actuator 118 to do both.
  • both a side port 114 and main valve member as described above, may be provided.
  • the assembly is advantageously configured such that movement of the actuator 118 in the first direction brings the actuator 118 into the open position and the main valve member into the closed position, whilst movement of the actuator 118 in the second direction brings the actuator 118 into the closed position, and the main valve member into the open position.
  • FIGS. 3 a and 3 b An alternative embodiment of actuator assembly is illustrated in FIGS. 3 a and 3 b .
  • two second direction chambers 138 b , 138 c are provided, the second port 138 b connecting the exterior of the tubular body 110 with the first second direction chamber 138 b and the third port 138 c connecting the exterior of the tubular body 110 with the second second direction chamber 138 c .
  • the first direction chamber 138 a is located between the two second direction chambers 130 b , 138 c .
  • the passages from the first port 140 a , second port 140 b , and third port 140 c into their respective chambers 138 a , 138 b , 138 c extend through the tubular body 110 generally perpendicular to its longitudinal axis.
  • both the tubular body 110 and actuator 118 are tubular with a generally circular cross-section.
  • the first direction chamber 138 a and the second direction chambers 138 b , 138 c are formed in an annular space around the actuator 118 between an exterior surface of the actuator 118 and an interior surface of the tubular body 110 .
  • This space is divided into the first direction chamber 138 a and two second direction chambers 138 b , 138 d by means of three seals 141 , 143 , 145 which substantially prevent flow of fluid between the chambers 138 a 138 b , 138 c .
  • two further seals 118 a , 130 a are provided between the exterior surface of the actuator 118 and the interior surface of the tubular body 110 , one at each end of the annular space.
  • the seals 118 a , 130 a , 141 , 143 , 145 each comprise a pair of generally circular O-rings which are located in two circumferential grooves around the exterior surface of the actuator 118 . It should be appreciated, however, that this invention is not restricted to the use of this particular type of seal, and any other type of seal which substantially prevents flow of fluid from the chambers 138 a , 138 b , 138 c whilst allowing the actuator 118 to slide in the tubular body 110 , could be used instead.
  • the seals could equally be mounted on the tubular body 110 rather than on the actuator 118 .
  • the actuator assembly is configured such that when the pressure of fluid in the first direction chamber 138 a exceeds the pressure of fluid both of the second direction chambers 138 b , 138 c , the pressure of fluid in the first direction chamber 138 a exerts a force on the actuator 118 which acts to push the actuator 118 in a first direction along the main passage 112 in the tubular body 110 , and when the pressure of fluid in either of the second direction chambers 138 b , 138 c exceeds the pressure of fluid in the first direction chamber 138 a , the pressure of fluid in the second direction chamber in question 138 b , 138 c exerts a force on the actuator 118 which acts to push the actuator 118 in a second, opposite, direction along the main passage 112 in the tubular body 110 .
  • this is achieved by providing the interior of the tubular body 110 with two portions of increased internal diameter 110 a , 110 a ′. At either end of these portions 110 a , 110 a ′, the interior surface of the tubular body 110 forms a shoulder 110 b , 110 c , 110 d , 110 e where the internal diameter of the tubular body 110 decreases slightly.
  • the actuator 118 is substantially longer than both the portions of increased internal diameter 110 a , 110 a ′ together, and the outer diameter of the actuator 118 is less than the internal diameter of the tubular body 110 either side of the portions of increased internal diameter 110 a , 110 a ′.
  • the first direction and second direction chambers 138 a , 138 b , 138 c are formed between the actuator 118 and the portions of increased internal diameter 110 a , 110 a ′, and two of the seals 141 , 145 extend outwardly of the exterior surface of the actuator 118 to engage with the interior surface of increased internal diameter portions 110 a , 110 a ′ of the tubular body 110 , one being located in each portion of increased internal diameter 110 a , 110 a ′.
  • the middle seal 143 engages with a portion of the internal surface of the tubular wall 110 between the two portions of increased internal diameter 110 a , 110 a′.
  • the first direction chamber 138 a is formed between the exterior surface of the actuator 118 , the first shoulder 110 b , the middle seal 143 , part of the first increased internal diameter portion 110 a of the tubular body 110 , and the seal 141 .
  • the first second direction chamber 138 b is formed between the exterior surface of the actuator 118 , the end seal 118 a , the second shoulder 110 c , part of the first increased internal diameter portion 110 a of the tubular body 110 , and the seal 141 .
  • the second direction chamber 138 c is formed between the exterior surface of the actuator 118 , the middle seal 143 , the third shoulder 110 d , part of the second increased internal diameter portion 110 a ′ of the tubular body 110 , and the seal 145 .
  • the fluid pressure pushes the seal 141 away from the first shoulder 110 b to increase the volume of the first direction chamber 138 a .
  • the actuator 118 is therefore pushed in the first direction.
  • the fluid pressure in the first second direction chamber 138 b pushes the seal 141 away from the second shoulder 110 c to increase the volume of the second direction chamber 138 b .
  • the actuator 118 is thus pushed in the second direction.
  • the actuator 118 therefore acts as a double acting piston with a first port 140 a to move the actuator 118 in a first direction along the main passage 112 in the tubular body 110 (in this example to the left in FIGS. 3 a and 3 b ) and a second port 140 b or a third port 140 c to move the sleeve 18 in a second direction along the main passage 112 in the tubular body 110 (in this example to the right in FIGS. 3 a and 3 b ).
  • FIGS. 4 a and 4 b A further alternative embodiment of the invention is illustrated in FIGS. 4 a and 4 b .
  • This embodiment is very similar to the embodiment described with reference to FIGS. 3 a and 3 b , in that it too has a second second direction chamber 138 c —the difference lies in relation to the order of the chambers 138 a , 138 b , 138 c .
  • the first direction chamber 138 a is located between the two second direction chambers 138 b , 138 c
  • the two second direction chambers 138 b , 138 c are next to one another.
  • the control passage 139 a to the first direction chamber 138 a and the control passage 139 c to the second second direction chamber 138 c extend diagonally through the wall of the tubular body 110 .
  • the control passage 139 b to the first second direction chamber 138 b extends through the tubular body 110 generally perpendicular to its longitudinal axis.
  • this arrangement of the chambers is achieved by providing the interior of the tubular body 110 with three portions of increased internal diameter 110 a , 110 a ′, 110 a ′′. At either end of each of these portions 110 a , 110 a ′, 110 a ′′, the interior surface of the tubular body 110 forms a shoulder 110 b , 110 c , 110 d , 110 e where the internal diameter of the tubular body 110 changes slightly.
  • the internal diameter of the tubular body 110 in the first and third increased diameter portions 110 a , 110 a ′′ is less than the internal diameter of the tubular body 110 in the second increased diameter portion 110 a ′.
  • the second increased diameter portion 110 a ′ lies directly between the first and third increased internal diameter portions 110 a , 110 a′′.
  • the actuator 118 is substantially longer than all the portions of increased internal diameter 110 a , 110 a ′, 110 a ′′ together, and the outer diameter of the actuator 118 is less than the internal diameter of the tubular body 110 either side of the portions of increased internal diameter 110 a , 110 a ′, 110 a ′′.
  • the first direction and second direction chambers 138 a , 138 b , 138 c are formed between the actuator 118 and the portions of increased internal diameter 110 a , 110 a ′, and the three seals 141 , 143 , 145 extend outwardly of the exterior surface of the actuator 118 to engage with the interior surface of increased internal diameter portions 110 a , 110 a ′, 110 a ′′ of the tubular body 110 , one being located in each portion of increased internal diameter 110 a , 110 a ′, 110 a ′′.
  • the seal 141 engages with the first increased diameter portion 110 a
  • the middle seal 143 engages with the second increased internal diameter 110 a ′
  • the final seal 145 engages with the third increased diameter portion 110 a′′.
  • the first direction chamber 138 a is formed between the exterior surface of the actuator 118 , the middle seal 143 , part of the third increased internal diameter portion 110 a ′′ of the tubular body 110 , the end shoulder 110 e and the seal 145 .
  • the first second direction chamber 138 b is formed between the exterior surface of the actuator 118 , the shoulder 110 c , the end seal 118 a , part of the first increased internal diameter portion 110 a of the tubular body 110 , and the first seal 141 .
  • the second second direction chamber 138 c is formed between the exterior surface of the actuator 118 , the shoulder 110 b , the first seal 141 , part of the second increased internal diameter portion 110 a ′ of the tubular body 110 , and the middle seal 143 .
  • the fluid pressure pushes the seal 143 away from the first shoulder 110 d to increase the volume of the first direction chamber 138 a .
  • the actuator 118 is therefore pushed in the first direction.
  • the fluid pressure in the first second direction chamber 138 b pushes the seal 141 away from the shoulder 110 c to increase the volume of the second direction chamber 138 b .
  • the actuator 118 is thus pushed in the second direction.
  • the actuator 118 therefore acts as a double acting piston with a first port 140 a to move the actuator 118 in a first direction along the main passage 112 in the tubular body 110 (in this example to the left in FIGS. 4 a and 4 b ) and a second port 140 b or a third port 140 c to move the sleeve 18 in a second direction along the main passage 112 in the tubular body 110 (in this example to the right in FIGS. 4 a and 4 b ).
  • the second port 140 b is exposed to high pressure whilst the first and third ports 140 a , 140 c are at low pressure.
  • the high pressure at the second port 140 b will only act to maintain the actuator 118 in its rest/default position.
  • the first port 140 a will then also be exposed to the high pressure, but as this is balanced by the same high pressure at the second port 140 b , the actuator 118 will not move.
  • the third port 140 c will also be exposed to the high pressure, so the pressure at all three ports 140 a , 140 b , 140 c is substantially equal.
  • the third port 140 c is exposed to high pressure whilst the first and second ports 140 a , 140 b are at low pressure.
  • the high pressure at the third port 140 c will only act to maintain the actuator 118 in its rest/default position.
  • the first port 140 a will then also be exposed to the high pressure, but as this is balanced by the same high pressure at the third port 140 c , the actuator 118 will still not move.
  • the second port 140 b will also be exposed to the high pressure, so the pressure at all three ports 140 a , 140 b , 140 c is substantially equal.
  • FIGS. 3 a , 3 b , 4 a and 4 b has an advantage over the embodiments described in relation to FIGS. 2 a and 2 b when passed through a device such as an RCD which seals around the tubular body 110 to maintain a pressure discontinuity either side of the RCD.
  • a device such as an RCD which seals around the tubular body 110 to maintain a pressure discontinuity either side of the RCD.
  • FIGS. 2 a and 2 b when one of the second port 140 b or third port 140 c is exposed to the high pressure at one side of the RCD, if the RCD seals do not close the other of the second port 140 b or third port 140 c , these ports provide a flow path for flow of fluid across the RCD. This cannot occur when the third port 140 c connects to a second second direction chamber 138 c.
  • the actuator assembly is configured such that the first direction and second direction chamber(s) 138 a , 138 b , 138 c are pressure balanced. This means that if the pressure in the first direction chamber 138 a equals the pressure in the or both second direction chamber(s) 138 b , 138 c , there is no net force acting on the actuator 118 , if the pressure in the first direction exceeds the pressure in the or both the second direction chamber(s), there is a net force acting on the actuator 118 pushing the actuator 118 in the first direction, and if the pressure in the first direction chamber 138 a is less than the pressure in the or either one of the second direction chamber(s) 138 b , 138 c , there is a net force acting on the actuator 118 pushing the actuator 118 in the second direction.
  • first direction and second direction chamber(s) 138 a , 138 b , 138 c are configured in such a way that the cross-sectional area of the first direction chamber 138 a perpendicular to the first direction is equal to the cross-sectional area of the or each second direction chamber 138 b , 138 c perpendicular to the second direction.
  • the actuator assembly may be configured in an non-pressure balanced fashion so that when the pressure in the first direction chamber 138 a equals the pressure in the or both second direction chamber(s), there is a net force acting on the actuator 118 .
  • this net force it is preferable for this net force to push the actuator 118 in the second direction. If this is the case, it will be appreciated that to move the actuator 118 in the first direction, it will be necessary to increase the fluid pressure in the first direction chamber 138 a relative to the fluid pressure in the or both of the second direction chamber(s) 138 b , 138 c so that the fluid pressure in the first direction chamber 138 a exceeds the pressure in the or both of the second direction chamber(s) 138 b , 138 c by a predetermined margin.
  • the actuator 118 once the actuator 118 has been moved in the first direction, it will be pushed back in the second direction once the fluid pressure in the first direction chamber 138 a falls below the level set by that predetermined margin, even if it still exceeds the pressure in the or both of the second direction chamber(s) 138 b , 138 c.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Mechanical Engineering (AREA)
  • Actuator (AREA)
  • Infusion, Injection, And Reservoir Apparatuses (AREA)
US14/902,137 2013-07-23 2014-05-19 Valve actuator Abandoned US20160376871A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB1313139.6 2013-07-23
GB1313139.6A GB2516468B (en) 2013-07-23 2013-07-23 Valve actuator
PCT/GB2014/051527 WO2015011434A2 (fr) 2013-07-23 2014-05-19 Actionneur de soupape

Publications (1)

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US20160376871A1 true US20160376871A1 (en) 2016-12-29

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US14/902,137 Abandoned US20160376871A1 (en) 2013-07-23 2014-05-19 Valve actuator

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Country Link
US (1) US20160376871A1 (fr)
EP (1) EP3025010B1 (fr)
CN (1) CN105408578A (fr)
AU (1) AU2014294814B2 (fr)
CA (1) CA2916904C (fr)
GB (1) GB2516468B (fr)
MX (1) MX2016000817A (fr)
SG (1) SG11201600514PA (fr)
WO (1) WO2015011434A2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160281466A1 (en) * 2014-05-12 2016-09-29 Halliburton Energy Services, Inc. Gravel pack-circulating sleeve with hydraulic lock
US20190145220A1 (en) * 2017-11-15 2019-05-16 Schlumberger Technolgy Corporation Combined valve system and methodology

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4560004A (en) * 1984-05-30 1985-12-24 Halliburton Company Drill pipe tester - pressure balanced
US5222425A (en) * 1991-01-08 1993-06-29 Novatek Drills (Proprietary) Limited Cyclic hydraulic actuator
US5782304A (en) * 1996-11-26 1998-07-21 Garcia-Soule; Virgilio Normally closed retainer valve with fail-safe pump through capability
US20100258354A1 (en) * 2009-04-14 2010-10-14 Tesco Corporation Jetted Underreamer Assembly
WO2012085597A2 (fr) * 2010-12-24 2012-06-28 Managed Pressure Operations Pte. Limited Ensemble soupape
US20130068472A1 (en) * 2011-09-19 2013-03-21 Baker Hughes Incorporated Hydraulic Three Position Stroker Tool

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4560004A (en) * 1984-05-30 1985-12-24 Halliburton Company Drill pipe tester - pressure balanced
US5222425A (en) * 1991-01-08 1993-06-29 Novatek Drills (Proprietary) Limited Cyclic hydraulic actuator
US5782304A (en) * 1996-11-26 1998-07-21 Garcia-Soule; Virgilio Normally closed retainer valve with fail-safe pump through capability
US20100258354A1 (en) * 2009-04-14 2010-10-14 Tesco Corporation Jetted Underreamer Assembly
WO2012085597A2 (fr) * 2010-12-24 2012-06-28 Managed Pressure Operations Pte. Limited Ensemble soupape
US20130068472A1 (en) * 2011-09-19 2013-03-21 Baker Hughes Incorporated Hydraulic Three Position Stroker Tool

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160281466A1 (en) * 2014-05-12 2016-09-29 Halliburton Energy Services, Inc. Gravel pack-circulating sleeve with hydraulic lock
US10161219B2 (en) * 2014-05-12 2018-12-25 Halliburton Energy Services, Inc. Gravel pack-circulating sleeve with hydraulic lock
US20190145220A1 (en) * 2017-11-15 2019-05-16 Schlumberger Technolgy Corporation Combined valve system and methodology
US11773690B2 (en) * 2017-11-15 2023-10-03 Schlumberger Technology Corporation Combined valve system and methodology

Also Published As

Publication number Publication date
CN105408578A (zh) 2016-03-16
SG11201600514PA (en) 2016-02-26
AU2014294814B2 (en) 2018-02-01
EP3025010A2 (fr) 2016-06-01
WO2015011434A2 (fr) 2015-01-29
GB2516468A (en) 2015-01-28
CA2916904A1 (fr) 2015-01-29
EP3025010B1 (fr) 2022-12-07
MX2016000817A (es) 2016-05-24
AU2014294814A1 (en) 2016-01-21
GB201313139D0 (en) 2013-09-04
CA2916904C (fr) 2021-01-26
GB2516468B (en) 2020-02-19
WO2015011434A3 (fr) 2015-08-06

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