EP3025010A2 - Actionneur de soupape - Google Patents

Actionneur de soupape

Info

Publication number
EP3025010A2
EP3025010A2 EP14725534.3A EP14725534A EP3025010A2 EP 3025010 A2 EP3025010 A2 EP 3025010A2 EP 14725534 A EP14725534 A EP 14725534A EP 3025010 A2 EP3025010 A2 EP 3025010A2
Authority
EP
European Patent Office
Prior art keywords
actuator
tubular body
port
fluid
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14725534.3A
Other languages
German (de)
English (en)
Other versions
EP3025010B1 (fr
Inventor
Ted Jee VOON
Andre Willy
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grant Prideco LP
Original Assignee
Managed Pressure Operations Pte Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Managed Pressure Operations Pte Ltd filed Critical Managed Pressure Operations Pte Ltd
Publication of EP3025010A2 publication Critical patent/EP3025010A2/fr
Application granted granted Critical
Publication of EP3025010B1 publication Critical patent/EP3025010B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • 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
    • 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 overground 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.
  • 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 10a provided in the wall of the drill string 10. This is best illustrated in Figure 1 c, and simply comprises an annular space between the two parts 18, 10a.
  • Two ports 40a, 40b are provided through the drill string 10 into this chamber 38, one at each end of the chamber 38.
  • the first port 40a is closest to a second end 18b 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 40a 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 40b acts in the opposite direction to counterbalance the effect of pressurised fluid at the first port 40a.
  • the actuator 18 therefore acts as a double acting piston with one pressure port 40a 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. In other words the actuator 18 is operated by means of a pressure differential across the first and second ports 40a, 40b.
  • Figure 1 a illustrates the actuator 18 when supply of pressurised fluid to the port 40b has pushed it away from the main valve member 16, so that the actuator 18 closes the side port 14, whilst Figure 1 b illustrates the sleeve 18 when supply of pressurised fluid to the port 40a 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".
  • 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
  • first and second directions is/are generally parallel to the longitudinal axis of the tubular body. In one embodiment, 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
  • 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
  • movement of the actuator in the second direction brings the actuator into the closed position
  • the main valve member into the open position 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 Q 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.
  • FIGURES 2a and 2b 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 Figure 2a and in the first direction in Figure 2b
  • FIGURES 3a and 3b 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 Figure 3a and in the first direction in Figure 3b
  • FIGURES 4a and 4b 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 Figure 4a and in the first direction in Figure 4b.
  • a fluid pressure operated actuator assembly comprising a tubular body 1 10 having a wall enclosing a main passage 1 12 which extends generally parallel to a longitudinal axis of the tubular body 1 10, an actuator 1 18 located in and movable along the main passage 1 12, a first direction chamber 138a and a second direction chamber 138b formed between the wall of the tubular body 1 10 and the actuator 1 18.
  • the tubular body 1 10 may be part of a drill string or may comprise a sub for mounting in a drill string.
  • both the tubular body 1 10 and actuator 1 18 are tubular with a generally circular cross-section.
  • the first direction chamber 138a and the second direction chamber 138b are formed in an annular space around the actuator 1 18 between an exterior surface of the actuator 1 18 and an interior surface of the tubular body 1 10. This space is divided into the first direction chamber 138a and second direction chamber 138b by means of a seal 141 which substantially prevents flow of fluid between the chambers 138a 138b.
  • Two further seals 1 18a, 130a are provided between the exterior surface of the actuator 1 18 and the interior surface of the tubular body 1 10, one at each end of the annular space.
  • the seals 1 18a, 130a, and 141 each comprise a pair of generally circular O-rings which are located in circumferential grooves around the exterior surface of the actuator 1 18. 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 1 18 and the tubular body 1 10 whilst allowing the actuator 1 18 to slide in the tubular body 1 10, could be used instead.
  • the seals could equally be mounted on the tubular body 1 10 rather than on the actuator 1 18.
  • the tubular body 1 10 is provided with a first port 140a which communicates with a first control passage 139a extending through the wall of the tubular body 1 10 from the first port 140a to the first direction chamber 138a, a second port 140b which communicates with a second control passage 139b extending through the wall of the tubular body 1 10 from the second port 140b to the second direction chamber 138b and a third port 140c which communicates with a third control passage 139c extending through the wall of the tubular body 1 10 from the third port 140c to the second control passage 139b.
  • the first and second control passages 139a, 139b extend through the wall of the tubular body generally perpendicular to its longitudinal axis.
  • the third passage 139c is inclined at angle of less than 45° to the longitudinal axis of the tubular body.
  • the first and second control passages 139a, 139b are co-planar and so both can be seen in the cross-sections illustrated in Figures 2a and 2b.
  • the third control passage 139c necessarily extends along a different plane and so is shown in dashed lines in these Figures.
  • the first, second and third ports 140a, 140b, 140c are spaced along the longitudinal axis of the tubular body 1 10 so that if the first port 140a is considered to lie on a first imaginary plane, the second port 140b on a second imaginary plane and the third port 140c 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 1 10, 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 138a exceeds the pressure of fluid in the second direction chamber 138b, the pressure of fluid in the first direction chamber 138a exerts a force on the actuator 1 18 which acts to push the actuator 1 18 in a first direction along the main passage 1 12 in the tubular body 1 10, and when the pressure of fluid in the second direction chamber 138b exceeds the pressure of fluid in the first direction chamber 138a, the pressure of fluid in the second direction chamber 138b exerts a force on the actuator 1 18 which acts to push the actuator 1 18 in a second, opposite, direction along the main passage 1 12 in the tubular body 1 10.
  • this is achieved by providing the interior of the tubular body 1 10 with a portion of increased internal diameter 1 10a. At either end of this portion 1 10a, the interior surface of the tubular body 1 10 forms a shoulder 1 10b, 1 10c where the internal diameter of the tubular body 1 10 decreases slightly.
  • the actuator 1 18 is substantially longer than the portion of increased internal diameter 1 10a and the outer diameter of the actuator 1 18 is less than the internal diameter of the tubular body 1 10 either side of the portion of increased internal diameter 1 10a.
  • the first direction and second direction chambers 138a, 138b are formed between the actuator 1 18 and the portion of increased internal diameter 1 10a, and the seal 141 extends outwardly of the exterior surface of the actuator 1 18 to engage with the interior surface of increased internal diameter portion 1 10a of the tubular body 1 10.
  • the first direction chamber 138a is thus formed between the exterior surface of the actuator 1 18, the first shoulder 1 10b, part of the increased internal diameter portion of the tubular body 1 10, and the seal 141 .
  • the second direction chamber 138b is formed between the exterior surface of the actuator 1 18, the second shoulder 1 10c, part of the increased internal diameter portion of the tubular body 1 10, and the seal 141 .
  • the fluid pressure pushes the seal 141 away from the first shoulder 1 10b to increase the volume of the first direction chamber 138a.
  • the actuator 1 18 is therefore pushed in the first direction.
  • the fluid pressure in the second direction chamber 138b pushes the seal 141 away from the second shoulder 1 10c to increase the volume of the second direction chamber 138b.
  • the actuator 1 18 is thus pushed in the second direction.
  • the actuator 1 18 therefore acts as a double acting piston with a first port 140a to move the actuator 1 18 in a first direction along the main passage 1 12 in the tubular body 1 10 (in this example to the left in Figures 2a and 2b) and a second port 140b or a third port 140c to move the sleeve 18 in a second direction along the main passage 1 12 in the tubular body 1 10 (in this example to the right in Figures 2a and 2b).
  • 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 140c.
  • the third port 140c may be advantageous as it may assist in preventing unwanted movement of the actuator 1 18 when the exterior of the tubular body 1 10 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 travelled 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 40a, 40b is relatively short. This means that as the portion of the drill string containing these ports 40a, 40b 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. Where an RCD is used, there may exist a point in the riser where, when the portion of the drill string including the ports 40a, 40b passes through, differential pressure may be seen from above or below, which exceeds the actuating pressure of the actuator 18. This may, therefore, result in unintended movement of the actuating sleeve 18. The provision of the third port 140c may prevent this as will be described below.
  • the actuator 1 18 should be arranged such that its default or rest position is as illustrated in Figure 2b, and is adopted by virtue of the supply of pressurised fluid to the second and/or third ports 140b, 140c.
  • a pressure discontinuity such as one introduced by an RCD
  • the second port 140b is exposed to high pressure (the high pressure also being communicated to the third port 140c), whilst the first port 140a is at low pressure.
  • the high pressure at the second and third ports 140b, 140c will act to maintain the actuator 1 18 in its rest / default position.
  • the first port 140a 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 140b, 140c the actuator 1 18 will not move. As the pressure discontinuity passes, the pressure at all three ports 140a, 140b, 140c is substantially equal.
  • the third port 140c is exposed to high pressure (which is also communicated to the second port 140b), whilst the first port 140a is at low pressure.
  • the high pressure at the second and third ports 140b, 140c will act to maintain the actuator 1 18 in its rest / default position.
  • the first port 140a 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 140c, the actuator 1 18 will still not move.
  • the actuator 1 18 will not be moved from its default or rest position by the pressure discontinuity, whichever end of the tubular body 1 10 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 1 10 is provided with a side passage 1 14 which extends from the exterior of the body 1 10 into the main passage 1 12.
  • the actuator 1 18 is provided with a further seal 130b which provide a substantially fluid tight seal between the actuator 1 18 and the tubular body 1 10 to ensure that, when the actuator is in a closed position (illustrated in Figure 2b), the actuator substantially prevents flow of fluid along the side passage 1 14.
  • this further seal 130b 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 1 18.
  • the further seal 130b and the seal 130a provided to contain fluid pressure in the first direction chamber 138a are spaced such that when the actuator 1 18 is in the closed position, the side port 1 14 lies between the two seals 130a, 130b.
  • 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 1 18 and the tubular body 1 10 whilst allowing the actuator 1 18 to slide in the tubular body 1 10, could be used instead.
  • movement of the actuator 1 18 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 140a.
  • movement of the actuator 1 18 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 140b, 140c.
  • Figure 2a illustrates the actuator 1 18 when supply of pressurised fluid to the first port 140a has pushed it in the first direction, thus opening the side port 1 14, whilst Figure 2b illustrates the actuator 1 18 when supply of pressurised fluid to the second or third port 140b, 140c has pushed it in the second direction, so that the actuator 1 18 closes the side port 1 14.
  • the actuator assembly could equally be configured such that the opposite is true - i.e. movement of the actuator 1 18 from the closed position to the open position comprises movement in the second direction etc, so that the actuator 1 18 is brought to or maintained in the open position when it passes through a pressure discontinuity.
  • the actuator 1 18 is connected to a main valve member (not shown) in such a way that movement of the actuator 1 18 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 1 12 of the tubular body 1 10 and an open position in which the main passage 1 12 of the tubular body 1 10 is open.
  • the movement of the main valve member caused by the movement of the actuator 1 18 in the first direction and second direction may comprise rotation, and the main valve member may be a ball valve.
  • the actuator 1 18 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 1 18 slides in the tubular body 1 10 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 1 18 slides in the tubular body 1 10 and the valve member rotates.
  • Various possible mechanisms whereby the actuator 1 18 could be connected to the main valve member so that sliding movement of the actuator 1 18 causes the main valve member to rotate are described in WO 2012/085597, GB 2 413 373, US 3,236,255, GB 1 416 085, US 3,703,193 and US 3,871 ,447.
  • the main valve member moves to its closed position when the actuator 1 18 moves in the first direction, which movement is, as described above, achieved by supply of pressurised fluid to the first port 140a.
  • the main valve moves to its open position when the actuator 1 18 moves in the second direction, which movement is, as described above, achieved by supply of pressurised fluid to the second or third port 140b, 140c.
  • the main valve member is brought to or maintained in its open position when the tubular body 1 10 passes through a pressure discontinuity such as created by an RCD in a managed pressure drilling situation.
  • the actuator 1 18 may either facilitate the opening or closing of a side port 1 14 through the tubular body 1 10 or control the opening or closing of a main valve member, it is possible for the actuator 1 18 to do both.
  • both a side port 1 14 and main valve member as described above may be provided.
  • the assembly is advantageously configured such that movement of the actuator 1 18 in the first direction brings the actuator 1 18 into the open position and the main valve member into the closed position, whilst movement of the actuator 1 18 in the second direction brings the actuator 1 18 into the closed position, and the main valve member into the open position.
  • FIG. 3a and 3b An alternative embodiment of actuator assembly is illustrated in Figures 3a and 3b.
  • two second direction chambers 138b, 138c are provided, the second port 138b connecting the exterior of the tubular body 1 10 with the first second direction chamber 138b and the third port 138c connecting the exterior of the tubular body 1 10 with the second second direction chamber 138c.
  • the first direction chamber 138a is located between the two second direction chambers 130b, 138c.
  • the passages from the first port 140a, second port 140b, and third port 140c into their respective chambers 138a, 138b, 138c extend through the tubular body 1 10 generally perpendicular to its longitudinal axis.
  • both the tubular body 1 10 and actuator 1 18 are tubular with a generally circular cross-section.
  • the first direction chamber 138a and the second direction chambers 138b, 138c are formed in an annular space around the actuator 1 18 between an exterior surface of the actuator 1 18 and an interior surface of the tubular body 1 10.
  • This space is divided into the first direction chamber 138a and two second direction chambers 138b, 138d by means of three seals 141 , 143, 145 which substantially prevent flow of fluid between the chambers 138a 138b, 138c.
  • two further seals 1 18a, 130a are provided between the exterior surface of the actuator 1 18 and the interior surface of the tubular body 1 10, one at each end of the annular space.
  • the seals 1 18a, 130a, 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 1 18. 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 138a, 138b, 138c whilst allowing the actuator 1 18 to slide in the tubular body 1 10, could be used instead.
  • the seals could equally be mounted on the tubular body 1 10 rather than on the actuator 1 18.
  • the actuator assembly is configured such that when the pressure of fluid in the first direction chamber 138a exceeds the pressure of fluid both of the second direction chambers 138b, 138c, the pressure of fluid in the first direction chamber 138a exerts a force on the actuator 1 18 which acts to push the actuator 1 18 in a first direction along the main passage 1 12 in the tubular body 1 10, and when the pressure of fluid in either of the second direction chambers 138b, 138c exceeds the pressure of fluid in the first direction chamber 138a, the pressure of fluid in the second direction chamber in question 138b, 138c exerts a force on the actuator 1 18 which acts to push the actuator 1 18 in a second, opposite, direction along the main passage 1 12 in the tubular body 1 10.
  • this is achieved by providing the interior of the tubular body 1 10 with two portions of increased internal diameter 1 10a, 1 10a'. At either end of these portions 1 10a, 1 10a', the interior surface of the tubular body 1 10 forms a shoulder 1 10b, 1 10c, 1 10d, 1 10e where the internal diameter of the tubular body 1 10 decreases slightly.
  • the actuator 1 18 is substantially longer than both the portions of increased internal diameter 1 10a, 1 10a' together, and the outer diameter of the actuator 1 18 is less than the internal diameter of the tubular body 1 10 either side of the portions of increased internal diameter 1 10a, 1 10a'.
  • the first direction and second direction chambers 138a, 138b, 138c are formed between the actuator 1 18 and the portions of increased internal diameter 1 10a, 1 10a', and two of the seals 141 , 145 extend outwardly of the exterior surface of the actuator 1 18 to engage with the interior surface of increased internal diameter portions 1 10a, 1 10a' of the tubular body 1 10, one being located in each portion of increased internal diameter 1 10a, 1 10a'.
  • the middle seal 143 engages with a portion of the internal surface of the tubular wall 1 10 between the two portions of increased internal diameter 1 10a, 1 10a'.
  • the first direction chamber 138a is formed between the exterior surface of the actuator 1 18, the first shoulder 1 10b, the middle seal 143, part of the first increased internal diameter portion 1 10a of the tubular body 1 10, and the seal 141 .
  • the first second direction chamber 138b is formed between the exterior surface of the actuator 1 18, the end seal 1 18a, the second shoulder 1 10c, part of the first increased internal diameter portion 1 10a of the tubular body 1 10, and the seal 141 .
  • the second direction chamber 138c is formed between the exterior surface of the actuator 1 18, the middle seal 143, the third shoulder 1 10d, part of the second increased internal diameter portion 1 10a' of the tubular body 1 10, and the seal 145.
  • the fluid pressure pushes the seal 141 away from the first shoulder 1 10b to increase the volume of the first direction chamber 138a.
  • the actuator 1 18 is therefore pushed in the first direction.
  • the fluid pressure in the first second direction chamber 138b pushes the seal 141 away from the second shoulder 1 10c to increase the volume of the second direction chamber 138b.
  • the actuator 1 18 is thus pushed in the second direction.
  • the fluid pressure in the second second direction chamber 138c pushes the seal 145 away from the third shoulder 1 10d to increase the volume of the second second direction chamber 138c.
  • the actuator 1 18 therefore acts as a double acting piston with a first port 140a to move the actuator 1 18 in a first direction along the main passage 1 12 in the tubular body 1 10 (in this example to the left in Figures 3a and 3b) and a second port 140b or a third port 140c to move the sleeve 18 in a second direction along the main passage 1 12 in the tubular body 1 10 (in this example to the right in Figures 3a and 3b).
  • the effect of fluid pressure at the first, second and third ports 140a, 140b, 140c is exactly the same as in the embodiment described in relation to Figures 2a and 2b, and any or all of the additional features of the earlier embodiment can also be applied to this embodiment.
  • FIG. 4a and 4b A further alternative embodiment of the invention is illustrated in Figures 4a and 4b.
  • This embodiment is very similar to the embodiment described with reference to Figures 3a and 3b, in that it too has a second second direction chamber 138c - the difference lies in relation to the order of the chambers 138a, 138b, 138c.
  • the first direction chamber 138a is located between the two second direction chambers 138b, 138c
  • the two second direction chambers 138b, 138c are next to one another.
  • the control passage 139a to the first direction chamber 138a and the control passage 139c to the second second direction chamber 138c extend diagonally through the wall of the tubular body 1 10.
  • the control passage 139b to the first second direction chamber 138b extends through the tubular body 1 10 generally perpendicular to its longitudinal axis.
  • this arrangement of the chambers is achieved by providing the interior of the tubular body 1 10 with three portions of increased internal diameter 1 10a, 1 10a', 1 10a". At either end of each of these portions 1 10a, 1 10a', 1 10a", the interior surface of the tubular body 1 10 forms a shoulder 1 10b, 1 10c, 1 10d, 1 10e where the internal diameter of the tubular body 1 10 changes slightly.
  • the internal diameter of the tubular body 1 10 in the first and third increased diameter portions 1 10a, 1 10a is less than the internal diameter of the tubular body 1 10 in the second increased diameter portion 1 10a'.
  • the second increased diameter portion 1 10a' lies directly between the first and third increased internal diameter portions 1 10a, 1 10a".
  • the actuator 1 18 is substantially longer than all the portions of increased internal diameter 1 10a, 1 10a', 1 10a" together, and the outer diameter of the actuator 1 18 is less than the internal diameter of the tubular body 1 10 either side of the portions of increased internal diameter 1 10a, 1 10a', 1 10a".
  • the first direction and second direction chambers 138a, 138b, 138c are formed between the actuator 1 18 and the portions of increased internal diameter 1 10a, 1 10a', and the three seals 141 , 143, 145 extend outwardly of the exterior surface of the actuator 1 18 to engage with the interior surface of increased internal diameter portions 1 10a, 1 10a', 1 10a" of the tubular body 1 10, one being located in each portion of increased internal diameter 1 10a, 1 10a', 1 10a".
  • the seal 141 engages with the first increased diameter portion 1 10a
  • the middle seal 143 engages with the second increased internal diameter 1 10a'
  • the final seal 145 engages with the third increased diameter portion 1 10a".
  • the first direction chamber 138a is formed between the exterior surface of the actuator 1 18, the middle seal 143, part of the third increased internal diameter portion 1 10a" of the tubular body 1 10, the end shoulder 1 10e and the seal 145.
  • the first second direction chamber 138b is formed between the exterior surface of the actuator 1 18, the shoulder 1 10c, the end seal 1 18a, part of the first increased internal diameter portion 1 10a of the tubular body 1 10, and the first seal 141 .
  • the second second direction chamber 138c is formed between the exterior surface of the actuator 1 18, the shoulder 1 10b, the first seal 141 , part of the second increased internal diameter portion 1 10a' of the tubular body 1 10, and the middle seal 143.
  • the fluid pressure pushes the seal 143 away from the first shoulder 1 10d to increase the volume of the first direction chamber 138a.
  • the actuator 1 18 is therefore pushed in the first direction.
  • the fluid pressure in the first second direction chamber 138b pushes the seal 141 away from the shoulder 1 10c to increase the volume of the second direction chamber 138b.
  • the actuator 1 18 is thus pushed in the second direction.
  • the fluid pressure in the second second direction chamber 138c pushes the seal 143 away from the shoulder 1 10b to increase the volume of the second second direction chamber 138c.
  • the actuator 1 18 therefore acts as a double acting piston with a first port 140a to move the actuator 1 18 in a first direction along the main passage 1 12 in the tubular body 1 10 (in this example to the left in Figures 4a and 4b) and a second port 140b or a third port 140c to move the sleeve 18 in a second direction along the main passage 1 12 in the tubular body 1 10 (in this example to the right in Figures 4a and 4b).
  • the effect of fluid pressure at the first, second and third ports 140a, 140b, 140c is exactly the same as in the embodiment described in relation to Figures 2a and 2b, and any or all of the additional features of the earlier embodiment can also be applied to this embodiment.
  • a pressure discontinuity such as one introduced by an RCD
  • the second port 140b is exposed to high pressure whilst the first and third ports 140a, 140c are at low pressure.
  • the high pressure at the second port 140b will only act to maintain the actuator 1 18 in its rest / default position.
  • the first port 140a will then also be exposed to the high pressure, but as this is balanced by the same high pressure at the second port 140b, the actuator 1 18 will not move.
  • the third port 140c will also be exposed to the high pressure, so the pressure at all three ports 140a, 140b, 140c is substantially equal.
  • the third port 140c is exposed to high pressure whilst the first and second ports 140a, 140b are at low pressure.
  • the high pressure at the third port 140c will only act to maintain the actuator 1 18 in its rest / default position.
  • the first port 140a will then also be exposed to the high pressure, but as this is balanced by the same high pressure at the third port 140c, the actuator 1 18 will still not move.
  • the second port 140b will also be exposed to the high pressure, so the pressure at all three ports 140a, 140b, 140c is substantially equal.
  • the embodiments described in relation to Figures 3a, 3b, 4a and 4b has an advantage over the embodiments described in relation to Figures 2a and 2b when passed through a device such as an RCD which seals around the tubular body 1 10 to maintain a pressure discontinuity either side of the RCD.
  • a device such as an RCD which seals around the tubular body 1 10 to maintain a pressure discontinuity either side of the RCD.
  • the actuator assembly is configured such that the first direction and second direction chamber(s) 138a, 138b, 138c are pressure balanced.
  • first direction and second direction chamber(s) 138a, 138b, 138c are configured in such a way that the cross-sectional area of the first direction chamber 138a perpendicular to the first direction is equal to the cross-sectional area of the or each second direction chamber 138b, 138c 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 138a equals the pressure in the or both second direction chamber(s), there is a net force acting on the actuator 1 18. In this case, it is preferable for this net force to push the actuator 1 18 in the second direction. If this is the case, it will be appreciated that to move the actuator 1 18 in the first direction, it will be necessary to increase the fluid pressure in the first direction chamber 138a relative to the fluid pressure in the or both of the second direction chamber(s) 138b, 138c so that the fluid pressure in the first direction chamber 138a exceeds the pressure in the or both of the second direction chamber(s) 138b, 138c by a predetermined margin.
  • the actuator 1 18 once the actuator 1 18 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 138a 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) 138b, 138c.

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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)

Abstract

L'invention concerne un ensemble actionneur fonctionnant par pression de fluide, comprenant : un corps tubulaire comportant une paroi, avec une surface intérieure et une surface extérieure, et entourant un passage principal s'étendant de manière généralement parallèle à l'axe longitudinal du corps tubulaire ; un actionneur placé dans le passage principal et pouvant se déplacer le long de celui-ci ; une première chambre directionnelle formée entre la paroi du corps tubulaire et l'actionneur ; et au moins une seconde chambre directionnelle formée entre le corps tubulaire et l'actionneur. L'ensemble est configuré de telle sorte que lorsque la pression du fluide dans la première chambre directionnelle dépasse la pression de fluide dans la seconde chambre directionnelle ou dans chacune d'elles selon une quantité prédéterminée, la pression de fluide dans la première chambre directionnelle exerce une force sur l'actionneur qui agit pour pousser l'actionneur dans une première direction par rapport au corps tubulaire, et lorsque la pression de fluide dans la seconde chambre directionnelle ou au moins une des secondes chambres directionnelles dépasse la pression de fluide dans la première chambre directionnelle selon une quantité prédéterminée, la pression de fluide dans la ou les secondes chambres directionnelles exerce une force sur l'actionneur qui agit pour pousser l'actionneur dans une seconde direction par rapport au corps tubulaire. L'ensemble est caractérisé en ce que la surface extérieure du corps tubulaire est pourvue d'un premier orifice qui communique avec un passage s'étendant à travers la paroi du corps tubulaire entre le premier orifice et la première chambre directionnelle, d'un deuxième orifice qui communique avec un passage s'étendant à travers la paroi du corps tubulaire entre le deuxième orifice et la ou l'une des secondes chambres directionnelles, et d'un troisième orifice qui communique avec un passage s'étendant à travers la paroi du corps tubulaire entre le troisième orifice et la ou l'autre des secondes chambres directionnelles. Le premier orifice s'étend sur un premier plan. Le deuxième orifice s'étend sur un deuxième plan. Le troisième orifice s'étend sur un troisième plan. Le premier plan, le deuxième plan, et le troisième plan sont en général parallèles les uns par rapport aux autres. Le premier plan s'étend entre le deuxième plan et le troisième plan.
EP14725534.3A 2013-07-23 2014-05-19 Actionneur de soupape Active EP3025010B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
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 (2)

Publication Number Publication Date
EP3025010A2 true EP3025010A2 (fr) 2016-06-01
EP3025010B1 EP3025010B1 (fr) 2022-12-07

Family

ID=49119150

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14725534.3A Active EP3025010B1 (fr) 2013-07-23 2014-05-19 Actionneur de soupape

Country Status (9)

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)

Families Citing this family (2)

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

Family Cites Families (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
CA2058659C (fr) * 1991-01-08 2001-02-20 Michael Richard Davies Actionneur hydraulique a action cyclique
US5782304A (en) * 1996-11-26 1998-07-21 Garcia-Soule; Virgilio Normally closed retainer valve with fail-safe pump through capability
US8113301B2 (en) * 2009-04-14 2012-02-14 Tesco Corporation Jetted underreamer assembly
GB201022004D0 (en) * 2010-12-24 2011-02-02 Managed Pressure Operations Drill pipe
US20130068472A1 (en) * 2011-09-19 2013-03-21 Baker Hughes Incorporated Hydraulic Three Position Stroker Tool

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
CN105408578A (zh) 2016-03-16
SG11201600514PA (en) 2016-02-26
AU2014294814B2 (en) 2018-02-01
WO2015011434A2 (fr) 2015-01-29
GB2516468A (en) 2015-01-28
CA2916904A1 (fr) 2015-01-29
US20160376871A1 (en) 2016-12-29
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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