WO2016106097A1 - Ensemble soupape - Google Patents

Ensemble soupape Download PDF

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Publication number
WO2016106097A1
WO2016106097A1 PCT/US2015/066494 US2015066494W WO2016106097A1 WO 2016106097 A1 WO2016106097 A1 WO 2016106097A1 US 2015066494 W US2015066494 W US 2015066494W WO 2016106097 A1 WO2016106097 A1 WO 2016106097A1
Authority
WO
WIPO (PCT)
Prior art keywords
cage
valve assembly
fluid
assembly
gate
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.)
Ceased
Application number
PCT/US2015/066494
Other languages
English (en)
Inventor
Hans Paul Hopper
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.)
Cameron International Corp
Original Assignee
Cameron International Corp
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
Priority claimed from GB1423195.5A external-priority patent/GB2533640B/en
Application filed by Cameron International Corp filed Critical Cameron International Corp
Publication of WO2016106097A1 publication Critical patent/WO2016106097A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • E21B34/02—Valve arrangements for boreholes or wells in well heads
    • E21B34/04—Valve arrangements for boreholes or wells in well heads in underwater well heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
    • F16K3/16—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together
    • F16K3/18—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members
    • F16K3/188—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with special arrangements for separating the sealing faces or for pressing them together by movement of the closure members by means of hydraulic forces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
    • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
    • F16K3/246—Combination of a sliding valve and a lift valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/04—Devices for relieving the pressure on the sealing faces for sliding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/08—Means in valves for absorbing fluid energy for decreasing pressure or noise level and having a throttling member separate from the closure member, e.g. screens, slots, labyrinths

Definitions

  • the present invention relates to a valve assembly, in particular to a valve assembly in which fluid pressure across the valve is required to be equalized before the position of the valve is changed, such as a gate valve or a ball valve.
  • the valve assembly of the present invention finds particular use in wellhead assemblies and the control of fluids produced from subterranean wells, in particular in subsea locations.
  • Check valves are used to allow fluid flow in a given direction, typically once a predetermined threshold pressure has been achieved and the valve is 'cracked', but to prevent the flow of fluids in the reverse direction.
  • Various designs of check valve are known and operated, including ball check valves, diaphragm check valves and swing check valves.
  • Valves such as gate valves and ball valves, are generally used in situations where the fluid pressure upstream of the valve is generally the same as the fluid pressure downstream of the valve, as noted above.
  • Valves In use, when changing the position of the valve, for example when closing an open valve or opening a closed valve, it is necessary to equalize the pressure of fluid on the upstream and downstream sides of the valve.
  • Conventional valve designs do not in general provide for the pressure to be equalized in this manner without movement of the valve itself.
  • valve assembly in particular for use in the control of fluids produced from a subterranean well, for example in a wellhead assembly.
  • Figure 1 is a cross-sectional view of an embodiment of a pressure equalizing valve assembly for use in the valve assembly of the present invention
  • Figure 2 is a cut-away, cross-sectional view of the lower housing of the pressure equalizing valve assembly of Figure 1 ;
  • Figure 3 is a diagrammatical cross-sectional view of the lower housing of the pressure equalizing valve assembly along the line Ill-Ill of Figure 2;
  • Figures 4a, 4b, 4c and 4d are diagrammatical cross-sectional views of the channel in the inner wall of the lower housing of the pressure equalizing valve assembly of Figure 2, at the positions A, B, C and D respectively of Figure 3;
  • Figure 5 is a cross-sectional view of the lower housing of the pressure equalizing valve assembly of Figure 1 , showing the flow control assembly therein;
  • Figure 6 is a cross-sectional view of a portion of the flow control assembly of Figure 1 in the fully closed position
  • Figure 7 is an enlarged cross-sectional view of the seating
  • Figure 8 is a cross-sectional view as in Figure 6, but with the flow control assembly in a position intermediate between the fully closed position and the fully open position;
  • Figure 9 is a cross-sectional view of a valve assembly according to one embodiment of the present invention and comprising two pressure equalizing valve assemblies of the general configuration of Figures 1 to 8 in the gate assembly thereof;
  • Figure 10 is a cross-sectional view of the gate assembly of the valve assembly of Figure 9.
  • Fluids are produced from subterranean wells at high pressures. Fluids, such as gas and oil, together with fluids introduced into the well during drilling and completion operations, such as water and muds, can be produced from the well at pressures up to 10,000 psi and higher. Accordingly, the control of fluids produced from a well represents a significant task for a valve assembly, which must be able to operate in a very harsh environment.
  • valve assembly could be provided which may be used to control both the pressure of a fluid stream or the flowrate of the fluid stream, depending upon the operational requirements of the valve.
  • valve assembly could offer a reliable shut- off capability, that is reduce fluid flow through the valve to zero without fluid leakage past the valve or a risk of failure of the valve.
  • the valve assembly must be able to equalize the fluid pressure difference across the valve at high fluid pressures, for example a pressure drop across the valve of 3,000 psi or higher.
  • the present invention provides an improved design of valve, in particular a gate valve, for the control of fluid flow.
  • the valve assembly of the present invention finds particular use in the control of fluids produced from subterranean wells, especially use in a wellhead assembly.
  • the reliability of the valve assembly is such that it may be used in wellhead assemblies in remote and/or hard to reach locations, such as wellhead installations on the seabed.
  • the present invention provides a gate valve assembly comprising: [0024] a gate valve having a gate assembly moveable between a closed position and an open position, in use the gate valve having an upstream side and a downstream side;
  • the gate assembly comprising a pressure equalizing assembly for equalizing the fluid pressure across the gate valve, the pressure equalizing assembly comprising a pressure equalizing valve assembly;
  • the pressure equalizing valve assembly comprises:
  • a flow control assembly disposed within the valve housing between the first and second ports, whereby fluid entering the valve housing is caused to flow through the flow control assembly, the flow control assembly comprising:
  • a cage having apertures therethrough to provide passage for fluid passing from the inlet to the outlet;
  • a closure assembly having a closure member moveable with respect to the cage between a first closed position, in which the closure member closes the apertures in the cage, and a second open position, in which the apertures in the cage are open.
  • the valve assembly comprises a gate valve.
  • the gate valve is a valve which, in use, requires that pressure across the valve is equalized before the position of the valve is changed, in particular when the valve is moved from one of the open and the closed position to the other.
  • Such gate valves are known in the art and are commercially available.
  • the gate valve has an upstream side and a downstream side.
  • the assembly of the present invention employs such gate valves and provides an improved means for equalizing the pressure between the upstream side of the gate valve and the downstream side of the gate valve.
  • the valve assembly of the present invention comprises a pressure equalizing assembly for equalizing the pressure difference between the upstream and downstream sides of the gate valve.
  • the gate valve comprises a gate assembly having a gate, movement of which within the body of the valve provides control of the fluid flowing through the gate valve, as is known in the art.
  • the gate assembly comprises a pressure equalizing assembly.
  • the pressure equalizing valve assembly is used to equalize fluid pressure on either side of the gate valve, in particular on either side of the gate assembly of the valve.
  • the pressure equalizing valve assembly is operated to allow the flow of fluid through the gate assembly of the gate valve under the action of the pressure differential across the gate, to equalize the pressure on either side of the gate, thereby allowing the gate to be moved.
  • the principle of the present invention relies upon the pressure equalizing valve assembly being one that can be operated, in particular opened, closed and used to control the flow of fluid through the pressure equalizing valve, under conditions of a high differential fluid pressure across the pressure equalizing valve assembly, in contrast to the gate valve.
  • the present invention may employ any form of valve assembly as the pressure equalizing valve, provided it is able to operate under a high fluid pressure differential between the upstream side and
  • the preferred aspect of the present invention employs a particular form of flow valve assembly as the pressure equalizing valve assembly, that is a valve assembly comprising a cage having apertures through which fluid is allowed to flow and a closure member to selectively open and close the apertures, thereby controlling the flow of fluid therethrough.
  • the housing has a first port for fluid and a second port for fluid, with a flow control assembly disposed within the housing between the fluid ports.
  • the assembly may be oriented such that fluid enters one of the fluid ports and leaves through the other fluid port, depending upon the embodiment of the present invention.
  • the pressure equalizing valve assembly is arranged whereby all the fluid entering the housing through one of the ports is caused to flow through the flow control assembly to leave the housing through the other port.
  • the first port is in fluid flow connection with the outside of the cage, such that fluid entering the housing through the first port is provided to the exterior of the cage and flows through the apertures of the wall of the cage to the interior thereof.
  • the second port is in fluid flow connection with the interior of the cage, such that fluid entering the housing through the second port is provided to the interior of the cage and flows through the apertures in the wall of the cage to the outside of the cage.
  • the housing comprises a cavity therein connected to the first port, the flow control assembly being disposed within the cavity, preferably centrally, such that the cavity extends around the flow control assembly.
  • the first port is arranged in the housing to extend tangentially to the walls of the cavity. It has been found that such an arrangement having a tangential entry provides an improved fluid control when using the closure member/cage arrangement of the valve assembly of the present invention.
  • the first port has the form of an opening in the wall of the cavity, disposed to direct fluid into a channel or groove having the form of an involute and extending around the outer wall of the cavity.
  • the channel or groove is formed to have a progressively smaller cross-sectional area, in order to progressively introduce fluid into the cavity around the flow control assembly. In this way, an even distribution of fluid around the flow control assembly is obtained.
  • the pressure equalizing valve assembly comprises a first port and a second port for fluid to enter and leave the valve housing. Between the ports is disposed a flow control assembly, operable to control the flow rate and/or pressure of fluid passing through the pressure equalizing valve assembly.
  • the flow control assembly comprises a cage having apertures therethrough, through which fluid is caused to flow. The apertures are opened and closed as described hereafter. The control of the flow of fluid is obtained by selecting the number and/or size of apertures that are open for fluid passage.
  • the cage may have any suitable form, but is preferably in the form of a generally cylindrical tube, with apertures extending through the wall of the tube.
  • connection with the second port in embodiments in which the first port is acting as the fluid inlet, fluid enters the housing through the first port, flows through the apertures into the cage interior and leaves the housing through the second port.
  • the second port in embodiments in which the second port is acting as the fluid inlet, fluid enters the housing through the second port, flows into the interior of the cage, passes through the apertures in the cage wall and leaves the housing through the first port.
  • the apertures may extend through the wall of the cage and be arranged around the cage in any suitable pattern.
  • Known patterns for the apertures include overlapping rows of apertures of different sizes.
  • the apertures are arranged in a plurality of rows, each row containing one or more apertures, with adjacent rows being separated by a land or region having no apertures therethrough. This arrangement improves the accuracy of the control of fluid flow, by allowing a closure member, such as a plug or sleeve, to lie with its end face extending across the land, thereby leaving the apertures either fully open or fully closed, depending upon their position relative to the closure member.
  • the apertures in the cage are preferably arranged in rows.
  • the arrangement and relationship of apertures in adjacent rows may be any suitable or preferred pattern.
  • the centers of the apertures in adjacent rows of the cage are offset from each other circumferentially around the exterior surface of the cage.
  • the apertures are arranged such that adjacent apertures in adjacent rows extend in a helical pattern along and around the cage. This is a particularly preferred arrangement when the apertures are angled in the aforementioned preferred manner.
  • This arrangement is of particular advantage when the assembly is being used to process fluid streams produced from subterranean wells, in particular fluid streams comprising a plurality of liquid phases, especially oil and water, and a gas phase.
  • the apertures may extend through the cage in any suitable direction.
  • the apertures extend radially inwards through the cage wall.
  • the apertures extend inwards, in a plane perpendicular to the longitudinal axis of the cage, but at an angle to the radial direction, in order to direct the fluid entering the cage in a circular flow pattern within the cage cavity.
  • the apertures extend through the cage wall and open tangentially to the inner surface of the wall.
  • the apertures extend through the cage wall at an angle to the plane perpendicular to the longitudinal axis of the cage and at an angle to the radial direction.
  • the apertures extend at an angle to the plane perpendicular to the longitudinal axis in either the upstream direction or downstream direction of fluid within the cage. In this way, the fluid is caused to flow in a helical flow pattern within the cage.
  • the apertures may be angled to avoid the fluid stream from one aperture contacting the fluid stream from an adjacent aperture.
  • the flow control assembly comprises means to open and close the apertures extending through the cage, in order to control the flow of fluid through the valve assembly.
  • the flow control assembly comprises a closure assembly having a closure member.
  • the closure member is moveable with respect to the cage, so as to open and close the apertures in the cage wall, thereby varying the cross-sectional area of the apertures available for the flow of fluid through the wall of the cage.
  • the closure member may be disposed within the cage and be moveable with respect to the cage and the apertures extending through the wall of the cage. In this arrangement, the closure member acts to open or close the apertures by closing and sealing the inner end of each aperture.
  • the closure member is moveable between a first position, in which it obscures and closes all the apertures in the cage, and a second position, in which it overlies and obscures none of the apertures in the cage.
  • the closure member may be positioned between the first and second positions, such that a portion of the apertures are open for the passage of fluid therethrough, and the remainder of the apertures are closed to the flow of fluid. The flow of fluid through the valve assembly may thus be controlled by the appropriate position of the closure member within the cage.
  • the closure member within the cage may have any suitable form.
  • the closure member in the case of a generally cylindrical tubular cage, may be a cylindrical sleeve or a cylindrical plug, the outer diameter of which corresponds to the inner diameter of the cage.
  • the closure member may be disposed outside the cage and be moveable with respect to the cage and the apertures extending through the wall of the cage.
  • the closure member acts to open or close the apertures by closing and sealing the outer end of each aperture.
  • the closure member is moveable between a first position, in which it obscures and closes all the apertures in the cage, and a second position, in which it overlies and obscures none of the apertures in the cage.
  • the closure member may be positioned between the first and second positions outside the cage, such that a portion of the apertures are open for the passage of fluid therethrough, and the remainder of the apertures are closed to the flow of fluid.
  • the flow of fluid through the valve assembly may thus be controlled by the appropriate position of the closure member outside the cage.
  • the closure member outside the cage may have any suitable form.
  • the closure member in the case of a generally cylindrical tubular cage, the closure member may be a cylindrical sleeve, the inner diameter of which corresponds to the outer diameter of the cage.
  • the pressure equalizing valve assembly comprises a first closure member disposed within the cage, as described above, and a second closure member disposed outside the cage, as described above.
  • the first and second closure members may be moved independently from one another, relative to the cage.
  • the pressure equalizing valve assembly will further comprise an actuator assembly for each of the first and second closure members.
  • the first and second closure members are moved together, preferably by being connected to one another, by a single actuator assembly. This arrangement offers certain advantages, as described hereinafter.
  • Both the first and second closure members may be used to control the flow of fluid through the pressure equalizing valve assembly.
  • the first and second closure members are sized relative to one another and the cage that, when moved together, at a given position of the closure assembly, the first and second closure members are closing the same apertures through the cage wall and leaving the same apertures open for fluid flow.
  • a given aperture will either be open at both its inner and outer ends or will be closed at both its inner and outer ends.
  • the first and second closure members are sized and arranged differently with respect to one another and the cage, such that in a given position of the closure assembly, the first and second closure members are obscuring and closing a different number of apertures.
  • one of the first or second closure members is arranged such that, as the closure members are moved from the first, closed position, the said one closure member begins to open the respective ends apertures in the cage wall, while the other ends of the same apertures remain closed.
  • the said one closure member acts as a shut-off member, responsible for shutting off the flow of fluid through the valve assembly, while the other closure member is acting to control the flow of the fluid through the apertures in the cage.
  • the other closure member acts as the flow control member, the position of which is responsible for determining the flow of fluid through the cage and the valve assembly.
  • the member acting as the shut-off member is the second closure member, disposed outside the cage, while the flow control member is the first closure member disposed within the cage.
  • first and second closure members may be moveable independently of one another.
  • a preferred closure assembly is one in which the first and second closure members are moveable together, more preferably by being connected.
  • the first and second closure members extend from a single support member, such that movement of the support member causes corresponding movement of both the first and second closure members.
  • the support member is in the form of a piston moveable within a chamber.
  • the chamber is in fluid connection with fluid be processed through the valve, more preferably by means of a conduit extending through the closure assembly, thereby providing the chamber with fluid being processed at the prevailing pressure of the fluid.
  • the closure assembly comprises a closure member moveable within the cage, the closure member having a conduit extending longitudinally therethrough to connect the chamber with the interior of the cage, thereby allowing fluid to be provided to the chamber from the interior of the cage and at the fluid pressure prevailing within the cage.
  • the pressure equalizing valve assembly further comprises means to move the closure assembly. Suitable actuators for moving the closure assembly are known in the art and may be employed. More preferably, the means for moving the closure assembly are linked to means for moving the gate of the gate assembly, such that movement of the gate results in movement of the closure assembly. In a preferred embodiment, the closure assembly of the pressure equalizing valve assembly is moved by the gate of the gate valve. In particular, movement of the gate from the fully closed position, in which both the gate and the pressure equalizing valve assembly are fully closed and fluid does not flow through the gate valve, first moves the closure assembly of the pressure equalizing valve assembly to open apertures in the cage of the flow control assembly.
  • the pressure equalizing valve assembly is moveable with the gate, more preferably being arranged within the gate assembly.
  • one of the first and second closure members acts as a shut-off member, that is to close the pressure equalizing valve assembly and prevent the flow of fluid therethrough.
  • a preferred arrangement is to have the second closure member, disposed outside the cage, as the shut-off member.
  • the relevant member is provided with a seat which is engaged by a sealing surface of the member when in the first or closed position.
  • the second member is provided with a seat extending around the cage, which is engaged by a sealing surface of the second member when in the first or closed position.
  • the surface of the seat preferably extends at an acute angle to the longitudinal axis of the closure member and the cage, whereby solid particles that fall onto or come to rest on the surface of the seat are caused to move off the seat, for example under the action of gravity.
  • the seat may be kept relatively clean of debris, limiting damage to the sealing surfaces of the seat and the closure member and improving the fluid seal between the seat and the closure member.
  • a seat may be provided to be contacted by each of the closure members, with each closure member having a respective seat disposed to be contacted by a sealing surface of the closure member when the closure member is in the first, closed position. More preferably, a seat is provided for one of the first or second closure members only.
  • the seat is formed within the cage, to be contacted by a sealing surface of the first closure member.
  • the seat may be formed as a shoulder within the cage member, with which the first closure member is brought into contact, when moving into the first, closed position.
  • the seat is preferably formed as an angled shoulder within the cage, such that solid debris on the cage is directed inwards towards the center of the cage member.
  • the seat is preferably formed outside the cage, so as to be contacted by the second member.
  • one preferred arrangement for the closure assembly of the valve assembly of the present invention comprises a generally cylindrical tubular cage, with a second closure member in the form of a cylindrical sleeve extending around the outer surface of the cage.
  • the seat arrangement for the second enclosure member, disposed outside, that is on the upstream side of the cage member, is preferably formed and interacts with the second closure member in manner that allows the fluid pressure on the inlet side of the cage to bear against the second closure member and force the sealing portion of the second closure member into contact with the sealing surface of the seat. In this way, the fluid seal between the second closure member and the seat is assisted by the inlet fluid pressure, when the first port is acting as the fluid inlet.
  • One preferred design of seat assembly for the second closure member comprises a seat having a sealing surface extending at an angle to the longitudinal axis of the cage. Most preferably, the sealing surface of the seat extends away from the cage at an acute angle to the longitudinal axis of the cage in the direction of movement of the second closure member when moving into the first, closed position.
  • the second closure member is provided with a complimentary sealing surface, in particular on the end surface of the sleeve.
  • the complimentary sealing surface may comprise a single surface extending at an appropriate angle so as to form a seal with the angle sealing surface of the seat, when the sleeve is in the first, closed position.
  • the sleeve may comprise a compound surface having at least two surface portions extending at an obtuse angle to one another.
  • the ridge formed by the compound surfaces contacts the sealing surface of the seat and provides the seal, to prevent the flow of fluid through the cage.
  • the ridge is caused to move across the sealing surface of the seat, removing damage caused to the surface by the erosive effects of the fluid.
  • the pressure equalizing valve assembly used in the valve assembly of present invention is particularly suitable for controlling the flow of fluid streams at high pressure through the gate valve, in particular when the fluid streams produced by a subterranean well or the fluid streams flowing into and out of a wellhead assembly.
  • a particular problem arises with the actuation of the pressure equalizing valve assembly and the movement of the components exposed to the fluid stream.
  • the actuating mechanism must move the valve components against the action of the fluid pressure. This can place significant strain on the actuating mechanism, requiring the actuator to be increased in power to cope with the additional burden. This burden increases as the operating pressure of the pressure equalizing valve assembly increases.
  • the closure assembly of the pressure equalizing valve assembly arranged so as to be biased by the fluid pressure into the closed position.
  • the closure assembly is biased into the closed position by the action of fluid pressure within the interior of the cage. This may be achieved, for example by the aforementioned arrangement of having the closure assembly comprise a chamber connected by a conduit to the interior of the cage, for example by having the conduit extend through a closure member moveable within the cage.
  • the gate assembly comprises a moveable gate, for controlling the flow of fluid through the gate valve.
  • the gate is moved by an actuator.
  • Suitable actuators for moving the gate of the gate valve are known in the art and are commercially available. Suitable actuators include electric actuators and hydraulic actuators.
  • the gate valve assembly of the present invention comprises a gate assembly disposed between the upstream side of the gate valve and the downstream side of the gate valve.
  • the gate assembly comprises the pressure equalizing valve assembly.
  • the gate assembly may be provided with a single pressure equalizing valve assembly.
  • the pressure equalizing valve assembly may be arranged such that the second port is connected to the upstream side of the gate valve, that is the side of the gate valve with the highest fluid pressure, and the first port is connected to the downstream side of the gate valve, that is the side of the gate valve with the lower pressure.
  • the pressure equalizing valve assembly is arranged to have the first port connected to the upstream or high pressure side of the gate valve, while the second port is connected to the downstream or lower pressure side of the gate valve.
  • the gate assembly is provided with two pressure equalizing valve assemblies.
  • the pressure equalizing valve assemblies may be arranged to accommodate a reversal of the fluid flow through the gate valve and still provide efficient pressure equalization across the gate valve, when in use.
  • the first pressure equalizing valve assembly is arranged to have its second port connected to the upstream or higher pressure side of the gate valve and the second pressure equalizing valve assembly is arranged to have its second port connected to the downstream or lower pressure side of the gate valve.
  • the first ports of the first and second pressure equalizing valve assemblies are connected.
  • the closure assemblies of both valves are moved together, preferably by being connected to and acted upon by a single, common actuator.
  • the common actuator is the gate of the gate assembly, whereby movement of the gate results in movement of both closure assemblies.
  • the gate is connected to each closure assembly so as to provide an equal force to the closure members, in particular to apply an equal force acting to close and hold closed the closure members.
  • the connection between the gate and each closure assembly comprises a resilient connecting member.
  • FIG. 1 there is shown one embodiment of a pressure equalizing valve assembly, generally indicated as 2.
  • the pressure equalizing valve assembly of Figure 1 is one that may be used in the valve assembly of the present invention, either directly or with minor modifications.
  • the pressure equalizing valve assembly 2 comprises a generally cylindrical lower housing 4 and a generally cylindrical upper housing 6.
  • the upper housing 6 has a flange 8 formed around its lower end portion, allowing the upper housing 6 to be mounted to the lower housing 4 by means of bolts 10 in a conventional manner.
  • the lower housing 4 comprises a generally cylindrical flow chamber 12 formed therein and has a first port 14 for fluid and a second port 16 for fluid.
  • Fluid may enter or leave the housing 4 through either of the first and second ports 14, 16, depending upon the arrangement of the pressure equalizing valve assembly.
  • the inlet 14 has a generally circular cross-section in the portion more distant from the lower housing 4, transitioning smoothly to a generally rectangular feed section in its portion closest to the lower housing 4 and immediately before the flow chamber 12.
  • the first port 14 is arranged laterally to open in the side of the flow chamber 12, as shown in Figure 1
  • the second port 16 is arranged axially in the lower portion of the lower housing 4, as also shown in Figure 1.
  • Fluid may be led to or removed from the first port 14 by a conventional pipe (not shown for clarity).
  • fluid may be led to or away from the second port 16 through a conventional pipe 18, mounted to the lower portion of the lower housing by means of a flange 20 and bolts 22, again of conventional design.
  • the second port 16 may be provided with a conduit, for example a passage or bore formed in the gate assembly of the valve assembly, in particular when the pressure equalizing valve assembly 2 is incorporated within the gate assembly of the gate valve, as described hereinafter.
  • the upper housing 6 comprises a first, generally cylindrical chamber 24 therein in its lower region which opens into the flow chamber 12 in the lower housing 4.
  • the upper housing 6 further comprises a second, generally cylindrical chamber 26 therein in its upper region.
  • the second chamber 26 is sealed from the first chamber as described hereinafter.
  • An actuator assembly 30, of known design and commercially available, may be mounted to the upper end of the upper housing 6 by bolts 32, in conventional manner.
  • the actuator assembly 30 may comprise any suitable form of actuator, for example a hydraulic, electro- hydraulic or electric actuator. Electric actuators are preferred.
  • actuation of the pressure equalizing valve assembly may be provided by movement of the gate of the gate assembly, as described hereinafter.
  • the pressure equalizing valve assembly valve assembly 2 further comprises a flow control assembly, generally indicated as 34, disposed within the flow chamber 12 of the lower housing, the flow control assembly 34 having a closure assembly, generally indicated as 36.
  • a flow control assembly generally indicated as 34
  • the flow control assembly 34 having a closure assembly, generally indicated as 36.
  • Components of the closure assembly 36 extend into the first chamber 24 in the upper housing 6 and into the second chamber 26 of the upper housing 6.
  • the closure assembly 36 is sealed to the interior of the upper housing 6 at the junction between the first and second chambers 24, 26. Details of the flow control assembly and the closure assembly are described hereinafter.
  • a shaft 38 extends from the actuator assembly 30 and connects with the upper end of the closure assembly 36.
  • the first port 14 opens into the flow chamber 12 of the lower housing 4 and is disposed in the side of the lower housing, so as to direct incoming fluid laterally into the flow chamber 12.
  • Figure 2 there is shown a cut-away cross-sectional view of the lower housing 4, with a portion of the flow control assembly 34 removed, to show details of the fluid inlet arrangement of the flow chamber 12.
  • Figure 3 A diagrammatical cross-sectional view along the line Ill-Ill of Figure 2 is shown in Figure 3.
  • the inner wall of the lower housing 4 defining the flow chamber 12 is formed with a channel 46 therein.
  • the channel 46 is aligned with the orifice 44 and forms an involute path for fluid entering the flow chamber 12.
  • the channel 46 is extends circumferentially around the flow chamber 12, as shown in Figure 3.
  • the channel 46 decreases in cross-sectional area, travelling in the
  • FIG. 4a, 4b, 4c and 4d Details of the cross section of the channel 46 are shown in Figures 4a, 4b, 4c and 4d at the positions A, B, C and D of Figure 3, respectively.
  • the cross-sectional area of the channel 46 decreases in the direction of fluid flow circumferentially away from the inlet orifice 44.
  • This reduction in cross- sectional area of the channel 46 ensures that fluid leaves the channel as it travel circumferentially around the flow chamber 12, as noted above.
  • This reduction in cross-sectional area is achieved in the embodiment shown in Figures 2 and 3 by having the depth of the channel 46 decrease in the direction extending
  • this reduction in depth is accompanied by an increase in the width of the channel in the longitudinal direction of the lower housing 12.
  • This increase in width has the effect of distributing the fluid stream longitudinally within the flow chamber 12. This in turn ensures that the flow control assembly has an even exposure to the fluid stream to be controlled.
  • the reduction in cross-sectional area of the channel 46 is preferably gradual or progressive, as shown in Figures 2 and 3. In the embodiment shown, the cross-sectional area reduces by 25% for each 90° of turn of the fluid stream.
  • the cross-sectional area of the orifice 44 as shown in Figure 4a is A
  • the cross-sectional area of the channel at the positions shown in Figures 4b, 4c and 4d is 0.75A, 0.5A and 0.25A, respectively.
  • FIG. 5 there is shown a vertical cross-sectional view of the lower housing 4 of the pressure equalizing valve assembly 2 of Figure 1 , showing the flow control assembly 34.
  • the flow control assembly 34 comprises a cage 50 formed as a generally cylindrical tube extending longitudinally within the flow chamber 12.
  • the cage 50 has a plurality of apertures 52 extending therethrough.
  • the apertures 52 extend through the wall of the cage 50 at an angle to the longitudinal axis, that is in a downwards direction, as viewed in the figures.
  • the apertures 52 extend through the cage wall at an angle to the radial direction, so as to open tangentially to the inner surface of the cage.
  • the cage 50 has its lower end portion formed with a thread 54 on its outer surface.
  • the cage 50 is mounted within the flow chamber 12 by being screwed into a threaded boss 56 inserted into the lower end wall of the lower housing 12 adjacent the second port 16.
  • the interior of the cage 50 is in fluid flow communication with the second port 16 by means of a bore formed in the boss 56, such that fluid flowing through the apertures 52 in the cage 50 and entering the interior of the cage 50 may leave the valve assembly through the second port 16.
  • a plurality of balancing bores 66 extending longitudinally through the plug 60. Each balancing bore 66 opens into the interior of the cage 50.
  • the balancing bores 66 are features of the fluid balancing system in the valve assembly.
  • the plug 60 is shown in the fully closed position in Figures 1 and 5, that is the plug 60 extends within the cage 50 and covers or obscures the inner ends of all the apertures 52 in the cage 50. It will be noted that the lower or free end of the plug 60 extends within the boss 56, that is a significant distance past the lowest apertures 52 in the cage 50.
  • the plug 60 depends at its upper end from the lower end of a generally cylindrical piston 68.
  • the piston 68 extends upwards from the top of the cage 50, through the first chamber 24 in the upper housing 6 and into the second chamber 26, as shown in Figure 1.
  • the non-rotatable piston 68 engages with grooves in the wall of the first chamber 24 and is moveable longitudinally within the upper housing 6, that is vertically as shown in Figure 1 , in association with the plug 60.
  • Seals 70 are disposed in the inner wall of the upper housing 6 at the junction between the first chamber 24 and the second chamber 26.
  • the seals 70 of conventional or known configuration, allow the longitudinal movement of the piston 68 within the first and second chambers, but prevent fluid from passing between the first and second chambers 24, 26.
  • the piston 68 has a central longitudinal bore 72, communicating with the bore 62 in the plug 60 at its lower end and opening into the second chamber 26 at its upper end, to receive the shaft 38.
  • a plurality of fluid balancing bores 74 extend longitudinally within the piston 68, the lower end of each balancing bore 74 communicating with a corresponding balancing bore 66 in the plug 60, and the upper end of each fluid balancing bore 74 opening into the second chamber 26 within the upper housing 6.
  • the closure assembly 36 further comprises a sleeve assembly 80.
  • the sleeve assembly 80 is generally cylindrical and extends from the lower end of the piston 68 around and along the outer surface of the cage 50 such that the sleeve assembly 80 can obscure and cover the outer ends of the apertures 52 in the cage.
  • the sleeve assembly 80 is formed to be a close fit around the exterior surface of the cage 50, while still allowing the sleeve assembly 80 to move longitudinally with respect to the cage 50.
  • the sleeve assembly 80 comprises an inner sleeve 82 and an outer sleeve 84, both generally cylindrical in form.
  • the outer sleeve 84 is unitary with the piston 68.
  • the inner sleeve 82 extends within the outer sleeve and is retained by a threaded connection 86 at their respective lower ends. This arrangement allows the inner sleeve 82 to be formed from tungsten and the outer sleeve 84 to be formed from stainless steel.
  • the sleeve assembly By being attached to the piston 68, the sleeve assembly is moveable both with the piston 68 and the plug 60.
  • the sleeve assembly 80 moves together with the plug 60 under the action of the actuator assembly 30.
  • the control of the flow of fluid through the apertures 52 of the cage 50 is determined by the positions of the plug 60 and sleeve assembly 80 with respect to the cage.
  • the plug 60 extends a greater distance from the end of the piston 68 than the sleeve assembly 80. This arrangement in turn provides the plug 60 and the sleeve assembly 80 with different functions.
  • the sleeve assembly 80 primarily acts as a flow shut-off member, that is to ensure that the flow of fluid is prevented, when the assembly is in the fully closed position, as shown in Figure 5, for example.
  • the control of the flow of fluid through the cage 50, and hence through the entire assembly is primarily controlled by the plug 60.
  • the sleeve assembly 80 is provided with a sealing arrangement at its lower end, that is the end distal of the piston 68.
  • FIG 6 there is shown an enlarged view of a portion of the flow control assembly 34 of Figure 1 , in particular showing the lower or distal end of the sleeve assembly 80.
  • a seating ring 90 is mounted in the boss 56 by a threaded connection 92 and extends around the cage 50.
  • the seating ring 90 is formed from a seating material to allow a ridge on the closure member to bed in.
  • a seating surface 94 is formed by the surfaces of the boss 56 and the seating ring 90 exposed within the flow chamber 12.
  • the seating surface 94 extends at an angle to the radial direction, such that it slopes away from the free end of the sleeve assembly 80.
  • the action of the angled seating surface is twofold. First, by being angled, debris is prevented from collecting on the seating surface and stopped from preventing a fluid-tight seal being formed between the sleeve assembly 80 and the seating surface. Rather, solid particles and debris are collected in the lower region of the flow chamber 12, as viewed in Figure 6, around the base of the cage. Second, the angle of the seating surface 94 cooperates with the surfaces on the end of the sleeve assembly 80 to be self-sharpening, as is described herein below.
  • the seating surface 94 cooperates with the end portion of the sleeve assembly 80.
  • the free or distal end of the outer sleeve 84 is finished perpendicular to the longitudinal axis of the sleeve assembly, plug and cage.
  • the distal end of the inner sleeve 82 is formed with a compound surface comprising a first surface portion 96 radially outwards of a second surface portion 98.
  • the first surface portion 96 extends at an angle to the radial direction that is more acute than the angle of the seating surface 94.
  • the second surface portion 98 extends at an angle to the radial direction that is more obtuse than the angle of the seating surface 94.
  • the first and second surface portions 96, 98 meet at a ridge 100.
  • the details of the seating surface 94 and its cooperation with the surfaces at the distal end of the sleeve assembly 80 are shown in Figure 7.
  • This force normal to the seating surface 94, has a radially outwards component, which induces a hoop stress in the distal end portion of the sleeve assembly 80.
  • the action of the hoop stress is to force the ridge 100 radially outwards, against the seating surface 94, as indicated by arrows P in Figure 7. This in turn increases the effectiveness of the seal formed between the ridge 100 and the seating surface 94.
  • high hoop stresses can be generated, in turn causing the ridge 100 to bed into the seating surface 94.
  • the plug 60 and sleeve assembly 80 extend different longitudinal distances from the piston 68 and with respect to the cage 50.
  • the closure assembly 36 is moveable between a fully closed position, as shown in Figure 6, for example, to a fully open position.
  • the sleeve assembly 80 is sealed against the seating surface 94, as described above and shown in detail in Figure 7.
  • the plug 60 extends longitudinally within the cage 50, with its free end extending beyond the seating surface 94, as shown in Figure 6.
  • the plug 60 and the sleeve assembly 80 cover and obscure the inner and outer ends of the apertures 52 in the cage 50, respectively, thus preventing fluid flow through the assembly 2.
  • the sleeve assembly 80 has the primary function of shutting off fluid flow, by sealing against the seating surface 94, when in the fully closed position.
  • the actuator assembly 30 moves the closure assembly 36 longitudinally from the fully closed position
  • the sleeve assembly 80 is lifted from the seating surface 94, as shown in Figure 8.
  • the sleeve assembly 80 is moved to expose the outer ends of the apertures 52 closest to the seating surface 94.
  • the plug 60 extending longitudinally further than the sleeve assembly 80, still covers the inner ends of all the apertures 52 in the cage 50. As a result, fluid does not flow.
  • the cage 50 is provided with a plurality of apertures 52 therethrough, to allow fluid to flow from the flow chamber 12 to the outlet 16.
  • the apertures 52 may be of conventional design, form and
  • the apertures are preferably formed to lie in discrete rows, separated by lands and to extend at an angle to the radial direction and at an angle in the longitudinal direction to the perpendicular to the longitudinal axis.
  • the cage 50 comprises a plurality of apertures 52 extending through the wall of the cage, each aperture having an opening in both the inner and outer surface of the cage wall.
  • Each aperture extends at both an angle to the radial direction and at an angle in the longitudinal direction to the normal or perpendicular, as noted above.
  • the arrangement of the apertures causes fluid entering the cage 50 from the first port 14 to flow in a direction parallel to the inner wall and to flow in a circular pattern. This circular flow pattern prevents the incoming jets of fluid from opposing apertures from colliding within the cage. This in turn helps to maintain any separation of fluid phases that may be occurred or been induced upstream of the valve assembly and reduces the burden on fluid separation apparatus downstream of the assembly.
  • each aperture extends at an angle to the perpendicular or radial direction longitudinally in the direction of flow.
  • the apertures may extend at any suitable angle to the perpendicular or horizontal plane and the angle will depend upon such factors as the dimensions of the cage and valve assembly, and the nature and composition of the fluid being processed. In the arrangement shown in the figures, the apertures extend at an angle of 25° to the perpendicular or horizontal.
  • the angle of the apertures may range from 5° to 50°, more preferably from 10° to 40°.
  • the apertures are angled in the longitudinal direction sufficient to ensure that the jet of fluid entering the cage through one aperture and flowing in a circular pattern adjacent the inner wall of the cage avoids contacting the jet of fluid entering the cage through the adjacent aperture in the direction of travel of the fluid.
  • the arrangement of the apertures 52 induces the fluid to flow in a helical pattern within the cage in the general direction of flow within the cage 50, with the fluid being subjected to minimal shear.
  • the apertures 52 are arranged in discrete rows extending circumferentially around the cage, each row containing one or more apertures, more preferably at least two apertures.
  • the rows are separated by portions of the cage wall having no apertures, or 'lands' 150. This allows the plug 60 to be positioned such that its end surface does not extend across the inner opening of one or more apertures 52. In this way, fluid entering the cage 50 through the open apertures 52 adjacent the end of the plug 60 is not caused to flow or cut across the end surface of the plug 60, in turn reducing the erosion of the plug 60 by the fluid stream.
  • the endmost portion of the plug 60 may be provided with a taper, as shown in Figures 6 and 7, for example, in order to improve the flow pattern of the fluid in the region adjacent the end of the plug 60.
  • the valve assembly 202 comprises a gate assembly 220 disposed within the valve bodies 206, 208 between the upstream port 212 and the downstream port 214.
  • the gate assembly 220 is moveable within the valve bodies 206, 208 under the action of a rotary actuator 222.
  • the actuator 222 is connected to the gate assembly 220 by a rotatable stem 224 extending within a shaft 226 of the gate assembly 220. In operation, rotation of the stem 224 by the actuator 222 causes the gate assembly 220 to move between a closed position, as shown in Figure 9, and an open position.
  • valve assembly 220 In the open position, the valve assembly 220 is accommodated within a chamber 228 formed within the lower valve body 206, while the shaft 226 is accommodated within a chamber 230 formed in the upper valve body 208. Similarly, a chamber 232 is formed in the shaft 226, for accommodating the lower end portion of the stem 224, as viewed in the figure.
  • the flow of fluid through the gate assembly is controlled by the position of the closure assembly 264 of each of the pressure equalizing valve assemblies.
  • the fluid flow is controlled by the second pressure equalizing valve assembly 256, that is the pressure equalizing valve assembly having the fluid entering through its first port and leaving through its second port.
  • the first pressure equalizing valve assembly that is providing the major control over the flow of fluid through the gate assembly.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (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)
  • Sliding Valves (AREA)

Abstract

L'invention concerne un ensemble soupape à tiroir (2, 204) comprenant une soupape à tiroir pourvue d'un ensemble tiroir mobile entre une position fermée et une position ouverte, la soupape à tiroir ayant en mode d'utilisation une face amont et une face aval ; l'ensemble tiroir comprenant un ensemble d'équilibrage de pression destiné à la pression du fluide traversant la soupape à tiroir, l'ensemble d'équilibrage de pression comprenant un ensemble soupape d'équilibrage de pression ; l'ensemble soupape d'équilibrage de pression comprenant un boîtier de soupape (4, 6) ; un premier orifice (14) permettant au fluide d'entrer dans le boîtier de soupape ou de le quitter ; un deuxième orifice (16) permettant au fluide de quitter le boîtier de soupape ou d'y entrer ; un ensemble de réglage de débit (34) disposé dans le boîtier de soupape entre le premier orifice et le deuxième orifice, le fluide entrant dans le boîtier de soupape étant amené à traverser l'ensemble de réglage de débit, l'ensemble de réglage de débit comprenant une cage (50) pourvue d'ouvertures (52) destinées à procurer un passage au fluide s'écoulant du premier orifice au deuxième orifice ; et un ensemble de fermeture (36, 60, 80) doté d'un élément de fermeture mobile par rapport à la cage entre une première position de fermeture dans laquelle l'élément de fermeture ferme les ouvertures ménagées dans la cage, et une deuxième position dans laquelle les ouvertures ménagées dans la cage sont ouvertes. L'ensemble soupape à tiroir s'avère particulièrement utile dans une installation de tête de puits de pétrole et de gaz souterrain.
PCT/US2015/066494 2014-12-24 2015-12-17 Ensemble soupape Ceased WO2016106097A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GB1423195.5A GB2533640B (en) 2014-12-24 2014-12-24 Valve assembly
GB1423195.5 2014-12-24
US14/972,040 US10125570B2 (en) 2014-12-24 2015-12-16 Valve assembly
US14/972,040 2015-12-16

Publications (1)

Publication Number Publication Date
WO2016106097A1 true WO2016106097A1 (fr) 2016-06-30

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Application Number Title Priority Date Filing Date
PCT/US2015/066494 Ceased WO2016106097A1 (fr) 2014-12-24 2015-12-17 Ensemble soupape

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5431188A (en) * 1994-03-25 1995-07-11 Master Flo Valve, Inc. Flow trim for choke
US20140150881A1 (en) * 2007-09-26 2014-06-05 Cameron International Corporation Choke Assembly

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5431188A (en) * 1994-03-25 1995-07-11 Master Flo Valve, Inc. Flow trim for choke
US20140150881A1 (en) * 2007-09-26 2014-06-05 Cameron International Corporation Choke Assembly

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