VÁLVULA

Abstract

A valve comprising a housing (12) which has an exterior and which encloses an interior space, the housing being provided with an inlet port (28, fig 4) and an outlet port (29), both of which provide a conduit between the exterior and interior space of the housing, the valve further comprising a main valve seat (14) and a main valve member (16) which is located in the interior space of the valve housing, the main valve member being movable relative to the valve housing between a closed position in which it engages with the main valve seat and blocks flow of fluid between the inlet port and the outlet port, and an open position in which it is not engaged with the main valve seat and the inlet port is fluidly connected to the outlet port, the main valve member having a passage (24) which extends through the main valve member and provides a conduit for flow of fluid between the inlet port and the outlet port when the main valve member is in the open position, characterised in that the valve further comprises an auxiliary valve member (31) which is movable relative to the main valve member (16) between a closed position in which the auxiliary valve member blocks the passage thereby restricting flow of fluid along the passage, and an open position in which substantially unrestricted flow of fluid along the passage is permitted.

Description

1 / 32 VALVE

[0001] The present invention relates to a valve suitable for use in injecting fluid into a wellbore, typically an offshore wellbore for oil production, particularly, but not exclusively, for use in a pneumatic lift / gas injection system. BACKGROUND

[0002] In hydrocarbon production, when a well hole is drilled into an earthen formation containing hydrocarbons, the fluid pressure in the formation may be sufficient to cause hydrocarbons from the formation to flow up the well hole to the surface. In some wells, however, the formation pressure is insufficient to do this, and hydrocarbon production from the well requires the use of an artificial lift system to supplement the formation pressure to lift the hydrocarbons from the formation to the surface.

[0003] Such an artificial lift system is a “pneumatic lift” system in which a high-pressure gas is injected into a production tubing that extends down the wellbore into the formation. The high-pressure gas may be supplied through the annular space between the production tubing and the wellbore casing and injected into the production tubing through one or more pneumatic lift valves that are arranged in the production tubing at the required depth in the wellbore. The pneumatic lift valve(s) may be arranged in the production tubing itself or may be arranged in mandrels with side pockets.

[0004] Publications that may be useful for Petition 870250084509, dated 09 / 19 / 2025, page 12 / 65 2 / 32 understanding the background includes W02007091898, WO2019 / 004838, and WO2019 / 074374. W02004 / 092537, CA 02461485.

[0005] Typically, such valves include a valve member that is linearly movable in and out of engagement with a valve seat to control the flow of fluid from the annular space into the production piping and are configured to be pressure-operated, i.e., to open when the pressure in the annular space exceeds a predetermined level. Frequently, a spring or other resilient propulsion element is provided to induce the valve member to engage with the valve seat, the valve being configured so that the valve member will move out of engagement with the valve seat when the fluid pressure in the annular space is sufficient to overcome the propulsion force of the spring. Such valves are, however, prone to chatter when the valve member repeatedly moves in and out of engagement with the valve seat.This wobble of the valve member in the valve seat can, over time, cause damage to the valve device, for example, spring fatigue failure or wear of the valve seat or valve member, which prevents the valve member from providing a hermetic seal to the fluid when engaged with the valve seat.

[0006] The present application relates to a novel valve configuration suitable for use in a pneumatic lifting system, which can reduce or alleviate the problem of valve vibration when in use. SUMMARY

[0007] According to a first embodiment, we supply a valve comprising a housing that has Petition 870250084509, dated 09 / 19 / 2025, p. 13 / 65 3 / 32 an exterior and enclosing an interior space, the housing being provided with an inlet orifice and an outlet orifice, both providing a conduit between the exterior and interior space of the housing, the valve further comprising a main valve seat and a main valve member situated in the interior space of the valve housing, the main valve member being movable between a closed position in which it engages with the main valve seat and blocks the flow of fluid between the inlet orifice and the outlet orifice and an open position in which it is not engaged with the main valve seat and the inlet orifice is fluidly connected with the outlet orifice and having a passage that fluidly connects the inlet orifice and the outlet orifice when the main valve member is in the open position,It is characterized by the fact that the valve additionally comprises an auxiliary valve member that is movable relative to the main valve member between a closed position, in which the auxiliary valve member blocks the passage, thereby limiting the flow of fluid along the passage, and an open position, in which substantially unrestricted fluid flow is permitted along the passage.

[0008] The main valve member further advantageously comprises an auxiliary valve seat with which the auxiliary valve member engages when in the closed position to block fluid flow along the passage, the auxiliary valve seat being integrated with or fixed to the main valve member.

[0009] The auxiliary valve member may be supplied in the passage. Petition 870250084509, dated 09 / 19 / 2025, page 14 / 65 4 / 32

[0010] The valve may additionally comprise a main resilient propulsion element, such as a spring, which acts on the valve member to induce the valve member to the closed position. In this case, the main resilient propulsion element may extend between the housing and the valve member.

[0011] The valve may additionally comprise an auxiliary propulsion element which induces the auxiliary valve member to the closed position. Where the valve has a resilient propulsion element, the auxiliary propulsion element is advantageously configured to provide a greater propulsion force than the main resilient propulsion element.

[0012] The main valve member can be linearly movable between the open and closed positions.

[0013] The main valve member may have a longitudinal geometric axis and generally move parallel to the longitudinal geometric axis between the open and closed positions. In this case, the passage, or at least part of the passage, may extend from a first end of the main valve member generally parallel to the longitudinal geometric axis.

[0014] The main valve member may divide the interior space of the housing into an inlet volume and an outlet volume, the inlet volume comprising the portion of the interior volume of the housing to which the inlet orifice is connected when the main valve member is in its closed position and the outlet volume comprising the portion of the interior volume of the housing to which the outlet orifice is connected when the valve member is closed. Petition 870250084509, dated 09 / 19 / 2025, page 15 / 65 5 / 32 The main valve is in its closed position.

[0015] The valve may further comprise a choke portion that is movable between a fully open position in which the cross-sectional area available for fluid flow along the inlet orifice is maximized and a variety of active positions in which the choke portion restricts fluid flow along the inlet orifice. The choke portion may also be movable to a fully closed position in which the choke portion blocks the inlet orifice and thus substantially prevents fluid flow between the exterior of the valve housing and the interior volume of the valve housing through the inlet orifice.

[0016] The housing may comprise a choke portion which may be situated in the inlet volume. In addition, the auxiliary valve member may be connected to the choke portion such that the auxiliary valve member moves relative to the valve housing with the choke portion. In this case, advantageously, the choke portion and the auxiliary valve member are configured such that the auxiliary valve member moves in the opposite direction to the main valve member when the choke portion moves towards the fully open position.

[0017] Advantageously, the auxiliary valve portion is tapered so that its cross-sectional area increases from a proximal end towards a distal end, the proximal end being closer to the main valve member than Petition 870250084509, dated 09 / 19 / 2025, page 16 / 65 6 / 32 the distal end.

[0018] The valve can be supplied in a fluid injection system for use in a hydrocarbon well.

[0019] According to another embodiment we supply a fluid injection system comprising a valve having any feature or combination of features described above and the pipe having a side wall enclosing a main passage and a side passage extending through the side wall to the main passage, the valve being mounted on the pipe so that the outlet volume of the valve is in fluid communication with the side passage.

[0020] According to another embodiment, we supply a fluid injection system comprising a valve having any feature or combination of features described above and a side-pocketed mandrel having a main passage that is aligned with the main passage of the pipe and a laterally offset side-pocketed hole, the main hole and the laterally offset side-pocketed hole being separated by an inner wall, wherein the valve is disposed in the side-pocketed hole, the valve inlet orifice being in fluid communication with the outside of the side-pocketed mandrel through an inlet opening and the valve outlet orifice being in communication with the main passage through an outlet conduit.

[0021] The outlet pipe can be provided in the inner wall. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] These and other features make Petition 870250084509, dated 09 / 19 / 2025, page 17 / 65 7 / 32 will become evident from the following description of illustrative embodiments, given as non-exclusive examples, with reference to the attached drawings, in which

[0023] Figure 1 is an illustration of a longitudinal cross-section through a valve embodiment according to the invention with the main valve member and auxiliary valve member both in the closed position,

[0024] Figure 2 is an illustration of a longitudinal cross-section through the valve illustrated in Figure 1 with the main valve member in the open position and the auxiliary valve member in its closed position.

[0025] Figure 3 is an illustration of a longitudinal cross-section through the valve illustrated in Figure 1 with the main valve member and auxiliary valve member both in their open positions.

[0026] Figure 4 is an illustration of a longitudinal cross-section through an alternative embodiment of a valve according to the invention with the choke portion, main valve member and auxiliary valve member in their closed positions,

[0027] Figure 5 is an illustration of a longitudinal cross-section through the valve illustrated in Figure 4 with the choke portion, main valve member and auxiliary valve member in their open positions,

[0028] Figure 6 is an illustration of a longitudinal cross-section through an additional alternative embodiment of a valve according to the invention with a choke portion, main valve member and Petition 870250084509, dated 09 / 19 / 2025, page 18 / 65 8 / 32 auxiliary valve member all in their closed positions,

[0029] Figure 7 is an illustration of a longitudinal cross-section through the valve illustrated in Figure 6 with the choke portion and main valve member in their open positions and the auxiliary valve member in the closed position,

[0030] Figure 8 is an illustration of a longitudinal cross-section through the valve illustrated in Figure 6 with the choke portion, main valve member and auxiliary valve member all in their fully open positions,

[0031] Figure 9 is an illustration of an enlarged portion of the valve illustrated in Figure 8,

[0032] Figure 10 is a schematic illustration of a fluid injection system for a hydrocarbon well including a valve according to the invention.

[0033] Figure 11 is a schematic illustration of a mandrel with a side pocket of the fluid injection system illustrated in Figure 10. DETAILED DESCRIPTION

[0034] The following illustration may use terms such as horizontal, vertical, side, “forward and backward, up and down, top, bottom, inside, outside, forward, backward, etc. These terms generally refer to the views and orientations as shown in the drawings and which are associated with normal use of the invention. The terms are used for the reader's convenience only and shall not be limiting.

[0035] With reference now to figures 1 - 3, a valve 10 is shown which is suitable for use in a Petition 870250084509, dated 09 / 19 / 2025, p. 19 / 65 9 / 32 pneumatic lifting valve in a hydrocarbon production system. The valve 10 comprises a housing 12 which has an exterior and which encloses an interior space. In this embodiment, the housing 12 and the interior space are generally cylindrical and have a longitudinal geometric axis A.

[0036] The valve 10 further comprises a main valve seat 14 and a main valve member 16 which is situated in the interior space of the valve housing 12 and which divides the interior space into an inlet volume 18a and an outlet volume 18b. The main valve seat 14 is fixed relative to the valve housing 12. In this example, the main valve seat 14 is provided in a shoulder 20 which is integral with the housing 12 and which extends radially into the housing 12 into the interior space thereof. The main valve seat 14 comprises a seating surface which faces the outlet volume 18b and in this example is inclined at an angle of approximately 45° relative to the longitudinal geometric axis A.

[0037] The main valve member 16 is movable between a closed position in which it engages with the main valve seat 14 and blocks fluid flow between the inlet volume 18a and the outlet volume 18b, and an open position in which it is not engaged with the main valve seat 14 and the inlet volume 18a is fluidly connected to the outlet volume 18b. In this embodiment, a seal 22 is provided to ensure a fluid-tight or substantially fluid-tight seal between the main valve member 16 and the main valve seat 14 when the main valve member 16 is in the closed position. The valve Petition 870250084509, dated 09 / 19 / 2025, page 20 / 65 Figure 1 illustrates the 10 / 32 valve member in the closed position and in the open position in Figures 2 and 3.

[0038] In this embodiment, the movement of the main valve member 16 between the open position and the closed position comprises linear movement generally parallel to the longitudinal geometric axis A.

[0039] In this example, the main valve member 16 is generally cylindrical.

[0040] The main valve member 16 has a working area that is in contact with fluid in the inlet volume 16a, the working area being arranged so that the force exerted by pressurized fluid in the inlet volume 18a induces the main valve member 16 in the opposite direction to the main valve seat 14.

[0041] In this embodiment, the main valve member 16 has an outer surface 26 and a first end of the main valve member 16 has an enlarged outer diameter head portion 16a, a reduced outer diameter intermediate portion 16b and an enlarged outer diameter tail portion 16c. The portion of the outer surface 26 that connects the head portion 16a and the intermediate portion 16b forms a sealing surface 26a that engages with the main valve seat 14 when the main valve member 16 is in the closed position and the main valve member 16 is arranged so that the head portion 16a extends into the outlet volume 18b. The angle of inclination of the sealing surface 26a with respect to the longitudinal geometric axis A corresponds to the angle of inclination of the sealing surface of the valve seat 14. The tail portion 16c of the valve member Petition 870250084509, dated 09 / 19 / 2025, page 21 / 65 11 / 32 main 16 extends into the input volume 18a.

[0042] It will therefore be recognized that the main valve member 16 is configured and arranged in relation to the main valve seat 14 in such a way that if the pressure in the outlet volume 18b exceeds the pressure in the inlet volume 18a, the main valve member 16 is pushed by the fluid pressure in the outlet volume 18b into its closed position.

[0043] The valve device 10 further comprises a main resilient propulsion element, which in this example is a helical spring 23 (hereinafter referred to as the main spring 23) that acts on the main valve member 16 to induce it into the closed position. The main spring 23 is arranged around the intermediate portion 16b of the main valve member 16 and extends between the shoulder 20 of the valve housing 12 and a shoulder 26b on the outer surface 26 of the main valve member 26 that connects the intermediate portion 16b to the tail portion 16c.

[0044] In this example, the valve 10 is provided with a stop 25 which engages with the main valve member 16 to limit the movement of the sealing surface 26a in the opposite direction to the main valve seat 14. When the main valve member 16 engages with the stop 25, the main valve member 16 is thus in its fully open position. In this particular embodiment, the head portion 16a engages with the stop 25 and the stop 25 is an end face of the housing 12.

[0045] In this mode, the fluid connection between the inlet volume 18a and the outlet volume 18b is obtained through a passage 24 that extends through the Petition 870250084509, dated 09 / 19 / 2025, page 22 / 65 12 / 32 main valve member 16. Passage 24 fluidly connects the inlet volume 18a and the outlet volume 18b when the main valve member 16 is in the open position. In this example, a first part 24a of passage 24 extends from the tail portion 16c of the main valve member 16 generally parallel to the longitudinal geometric axis A.

[0046] Also in this embodiment, a second part 24b of passage 24 extends radially outward from the first part 24a of passage 24, to connect the first part 24a of passage with the outer surface 26 of the intermediate portion 16b of the main valve member 16. The second part 24b of passage 24 may extend at an angle of up to 90° with respect to the longitudinal geometric axis A, but in this example it extends at an angle of approximately 45° with respect to the longitudinal geometric axis A. Furthermore, although the main valve member 16 may have a single passage 24, in this embodiment there are multiple second parts 24b of passage 24 that are spaced around the circumference of the main valve member 16.

[0047] Valve 10 is additionally provided with an inlet orifice (not shown in figures 1 - 3) extending through housing 12 to connect inlet volume 18a with the outside of housing 12 and an outlet orifice 29 extending through housing 12 to connect outlet volume 18b with the outside of housing 12.

[0048] A valve having all the features described above can function as a pneumatic lift valve. When there is no fluid supply. Petition 870250084509, dated 09 / 19 / 2025, p. 23 / 65 13 / 32 pressurized to the inlet volume 18a through the inlet orifice 28, the main spring 23 induces the main valve member 16 to the closed position. When pressurized fluid is supplied to the inlet volume 18a at a pressure sufficient to overcome the propulsive force of the main spring 23 and the force acting on the head portion 16a of the main valve member 16 from the pressurized fluid in the outlet volume 18b, inducing the main valve member 16 to engage with the main valve seat 14, the fluid pressure in the inlet volume 18a acts on the working area of ​​the main valve member 16 to move it to the open position so that the seating surface 26a moves out of contact with the valve seat 14. Fluid can therefore flow from the inlet volume 16a to the outlet volume 18b through the passage 24, and the space between the seating surface 26a and the valve seat 14.

[0049] The resulting drop in pressure in the inlet volume 18a at the opening of the main valve member 16 may, however, allow the main spring 23 to push the main valve member 16 back to the closed position. Then, after pressure builds up in the inlet volume 18a, the main valve member 16 opens and the cycle repeats. The resulting repeated beating of the main valve member 16 against the main valve seat 14 is known as shudder, and occurs most likely when the fluid flow rate into the inlet volume 18a through the inlet orifice is low. Such valve shudder is problematic as it can cause spring fatigue failure and damage to the sealing surface 26a. Petition 870250084509, dated 09 / 19 / 2025, page 24 / 65 14 / 32 of the main valve member 16 and / or the seat element 22, both of which may result in a loss of effective sealing function and fluid leakage between the inlet volume 18a and the outlet volume 18b when the valve member 16 is in the closed position.

[0050] To address this problem, the valve 10 further comprises an auxiliary valve 30 comprising an auxiliary valve member 31 that is movable relative to the main valve member 16 between a closed position in which the auxiliary valve member 16 blocks the passage 24, thereby preventing fluid flow along the passage 24, and an open position in which fluid flow is permitted along the passage 24. The auxiliary valve 30 is configured such that a working area of ​​the main valve member 16 is still in contact with fluid in the inlet volume 18 even when the auxiliary valve 30 is closed, the working area of ​​the main valve member 16 being arranged so that the force exerted by pressurized fluid on the working area induces the main valve member 16 in the opposite direction to the valve seat 14.

[0051] In this embodiment, the auxiliary valve 30 is provided in passage 24 (in this embodiment in the first portion 24a of passage 24), and the main valve member 16 further comprises an auxiliary valve seat 32 with which the auxiliary valve member 31 engages when in the closed position to block the flow of fluid along passage 24. The auxiliary valve seat 32 may be fixed to the main valve member 16, but in this example it is integral with the main valve member 16. Specifically, in this example, the auxiliary valve seat Petition 870250084509, dated 09 / 19 / 2025, page 25 / 65 15 / 32 comprises an annular shoulder extending from the tail portion 16c of the main valve member 16, radially into the first portion 24a of passage 24.

[0052] The auxiliary valve member 31 is supported in the first portion 24a of passage 24 via an auxiliary valve support 34, which is also located in the first part 24a of passage 24 and fixed to the tail portion 16c of the main valve member 16.

[0053] In this embodiment, the auxiliary valve 30 is a trigger valve and the auxiliary valve member 31 is configured to move linearly along the passage 24 in a direction generally parallel to the longitudinal geometric axis A between its open and closed positions. The auxiliary valve member 31 has a disc 31a and a stem 31b. The disc 31a engages with the auxiliary valve seat 32 when the valve member 31 is in its closed position to block the passage 24. The stem 31b is situated in an opening provided in the auxiliary valve holder 34 which allows the auxiliary valve member 31 to move linearly along the passage 24.

[0054] It must be recognized that although in this embodiment, the auxiliary valve member 31 is situated in passage 24, this need not be the case. The auxiliary valve seat 32 may be provided at one end of the main valve member 16 around the end of passage 24. In this case, the auxiliary valve member 31 may be situated in the inlet volume adjacent to the end of the main valve member 16 and movable for engagement with the auxiliary valve seat 32 while remaining Petition 870250084509, dated 09 / 19 / 2025, page 26 / 65 16 / 32 outside passage 24.

[0055] In this embodiment, the auxiliary valve 30 additionally comprises an auxiliary propulsion element, in this example a helical spring 36 (hereinafter referred to as the auxiliary spring), which induces the auxiliary valve member 31 to the closed position. In this example, the spring 36 is situated around the stem 31 and extends between the auxiliary valve support 34 and the disc 31a of the auxiliary valve member 31.

[0056] When the auxiliary valve member 31 is in its closed position, a portion of the disc surface 31, limited by the contact line between the disc 31 and the auxiliary valve seat 32 (hereinafter referred to as the auxiliary valve working area), is exposed to fluid in the inlet volume 18a. The fluid pressure in the inlet volume 18a acts on this working area to overcome the propulsion force of the auxiliary spring 36 and push the auxiliary valve member 31 in the opposite direction to the auxiliary seat 32.

[0057] Valve 10 operates as follows.

[0058] When the pressure in the inlet volume 18a is low, springs 23, 36 induce the main and auxiliary valve members 16, 31 respectively to their closed positions, as illustrated in figure 1. In this configuration, the fluid flow between the inlet volume 18a and the outlet volume 18b is blocked by both the main valve member 16 and the auxiliary valve member 31. The working area of ​​the auxiliary valve 30 and an extreme face of the tail portion 16c of the main valve member 16 are in direct contact with fluid in the inlet volume 18a and therefore form a combined valve working area. Petition 870250084509, dated 09 / 19 / 2025, page 27 / 65 17 / 32

[0059] As the pressure in the inlet volume 18a increases, the force on the valve member 16 resulting from the contact between the fluid in the inlet volume 18a and the combined valve working area increases until it is high enough to overcome the propulsion force of the main spring 23 and the force of the pressurized fluid in the outlet volume 18b acting on the head portion 16a of the main valve member 16. When this occurs, the main valve member 16 moves from its closed position to its open position. The auxiliary valve 30 moves with the main valve member 16, however, and remains in its closed position. This configuration is illustrated in Figure 2. In this configuration, the fluid flow between the inlet volume 18a and the outlet volume 18b is blocked by the auxiliary valve 30 only, since this prevents fluid flow along passage 24.

[0060] Springs 23, 36 are configured so that the propulsion force of the main spring 23 is overcome before the propulsion force of the auxiliary spring 36. It will be recognized that the working area of ​​the auxiliary valve 30 is smaller than the combined valve working area, the force exerted by the fluid pressure in the inlet volume 18a on the auxiliary valve member 31 is only less than the force on the main valve member 16. As such, this can be achieved by configuring the auxiliary spring 36 to have a spring force that is greater than, equal to, or slightly less than the spring force of the main spring 23.

[0061] As the pressure in the inlet volume 18a increases further, eventually, the force from the fluid pressure in the inlet volume 18a on the area of Petition 870250084509, dated 09 / 19 / 2025, page 28 / 65 18 / 32 The operation of auxiliary valve 30 is sufficient to overcome the propulsive force of auxiliary spring 36. When this occurs, the auxiliary valve member 31 moves from its closed position to its open position. This configuration is illustrated in Figure 3. In this configuration, fluid flow is permitted between inlet volume 18a and outlet volume 18b along passage 24.

[0062] This process is reversed if the pressure in the inlet volume 18a decreases.

[0063] An alternative embodiment of the valve according to the invention is illustrated in figures 4 and 5.

[0064] This embodiment of valve 10' is very similar to the embodiment illustrated in figures 1 to 3, and the equivalent parts are labeled with the same reference numerals. The only difference is that, in this embodiment, the valve 10' additionally comprises a throttling portion 40 that is movable between a fully open position in which the cross-sectional area available for fluid flow along the inlet orifice 28 is maximized and a variety of active positions in which the throttling portion 40 restricts fluid flow along the inlet orifice 28. In this embodiment, the throttling portion 40 is also movable to a fully closed position in which the throttling portion 40 blocks the inlet orifice 28 and thus substantially prevents fluid flow between the exterior of the valve housing 12 and the inlet volume 18A through the inlet orifice 28.Valve 10' is illustrated with the choke 40 part in the fully closed position in Figure 4 and the fully open position in Figure 5. Petition 870250084509, dated 09 / 19 / 2025, p. 29 / 65 19 / 32

[0065] In this embodiment, the choke part 40 is located in the inlet volume 18a.

[0066] The throttling part 40 may comprise a tubular sleeve that is mounted around the outside of the housing 12 and that is sliding along the outside of the housing 12 to cover the inlet hole 28 to a greater or lesser extent.

[0067] In this example, however, the choke portion 40 is a tubular sleeve lining the inside of the valve housing 12 and sliding along the inside of the housing 12 to cover the inlet orifice 28 to a greater or lesser extent. A seal 42 is provided around the inner circumference of the valve housing 12 and the choke portion 40 is configured to engage with the seat 42 when in the fully closed position to substantially prevent fluid leakage from the inlet orifice 28 into the inlet volume 18a.

[0068] The valve 10' further comprises an actuator (not shown) which is operable to move the throttling part 40 between the fully open and fully closed positions. Typically, the actuator comprises an electric motor, but this need not be the case. It may be, for example, a hydraulically or pneumatically operated actuator.

[0069] The choke part 40 can be used to vary the fluid flow rate from the outside of the valve housing 12 into the inlet volume 18a or to completely close the connection between the outside of the housing 12 and the inlet volume 18a.

[0070] An additional alternative mode of Petition 870250084509, dated 09 / 19 / 2025, page 30 / 65 The 20 / 32 valve according to the invention is illustrated in Figures 6-8. This embodiment of the 10” valve again has many similarities with the 10’ valve described above and as shown in Figures 4 and 5, and again, the equivalent parts have the same reference numerals. In this case, the difference lies in the configuration of the auxiliary valve 30”, mainly in that the auxiliary valve member 31” is connected to the choke part 40 so that the auxiliary valve member 31” moves relative to the valve housing 12 with the choke part 40. As such, instead of being fixed to the main valve member 16, the auxiliary valve support 34” extends between the auxiliary valve member 31” and the choke part 40. Also in this example, the auxiliary valve member 31” is fixed relative to the choke 40, i.e., there is no possibility of relative movement between these two parts.In this example, the auxiliary valve support 34” comprises a tube extending from one end of the actuator 40 to the auxiliary valve member 31”.

[0071] In this example, the choke portion 40 and auxiliary valve member 31 are configured so that the auxiliary valve member 31” moves in the opposite direction to the head portion 16a of the main valve member 16 as the choke portion 40 moves from its fully closed position towards its fully open position.

[0072] The choke part 40 is connected to a piston part 44, the piston part 44 being connected to the actuator (not shown) by means of which the movement of the choke part 40 is effected. The piston part 44 Petition 870250084509, dated 09 / 19 / 2025, page 31 / 65 21 / 32 is configured to support the choke part 40, auxiliary valve member 31” and auxiliary valve support 34” in the housing 12, while allowing movement of these parts relative to the housing 12 along the geometric axis A. As mentioned above, the actuator may comprise an electric motor, or means of supplying pressurized fluid to support the piston part 44 to move the piston part 44 along the geometric axis A. A seal 46 is mounted on the inner surface of the housing 12 to provide a substantially fluid-tight seal between the housing 12 and the outer surface of the piston part 44. This seal therefore acts to prevent or at least substantially prevent leakage of fluid from the inlet volume 18a along the space between the piston part 44 and the housing 12 while allowing the piston part 44 to slide relative to the housing.

[0073] The auxiliary valve support 34” is configured so that when the main valve member 16 is in its closed position, the auxiliary valve member 31” is situated in passage 24, specifically in the part of the first portion 24a of passage 24 enclosed by the tail portion 16c of the main valve member 16. The larger outside diameter of the auxiliary valve member 31” is only slightly smaller than the inside diameter of passage 23 in the tail portion 16c of the main valve member 16, so that there is no contact between the auxiliary valve member 31” and the main valve member 16, but the clearance between the two parts is so small that only very limited fluid flow can occur between them. As such, the auxiliary valve member 31” substantially blocks the passage. Petition 870250084509, dated 09 / 19 / 2025, page 32 / 65 22 / 32 24. This is the case over the entire range of motion of the choke part 40. In other words, while the main valve member 16 is in its closed position, passage 24 is blocked by the auxiliary valve member 31” when the choke is in its fully closed and fully open positions and all intermediate positions, and both the main valve member 16 and the auxiliary valve member 31” provide a barrier to significant fluid flow between the inlet volume 18a and the outlet volume 18b.

[0074] The auxiliary valve support 34” is configured, however, so that when the main valve member 16 moves to its open position, the auxiliary valve member 31” no longer blocks passage 24 and fluid flow between the inlet volume 18a and the outlet volume 18b is permitted. This can occur when the main valve member 16 has moved far enough towards the fully open position for the auxiliary valve member 31” to no longer be situated in passage 24. In this embodiment, however, passage 24 has a substantially constant cross-sectional area along most of the tail portion 16c of the main valve member 16 and increases, however (in this example generally linearly) in an enlarged end portion 24a at the end of the tail portion 16c of the main valve member 16.When the auxiliary valve member 31” is situated in the enlarged end portion, the clearance between the auxiliary valve member 31” and the inner surface of the main valve member 16 increases to allow significant fluid flow along passage 24. The size of this clearance increases. Petition 870250084509, dated 09 / 19 / 2025, page 33 / 65 23 / 32 as the main valve member 16 moves closer to its fully open position.

[0075] Valve 10” operates as follows.

[0076] When the pressure in the inlet volume 18a is low, the main spring 23 induces the main valve member 16 to its closed positions, as illustrated in Figure 6. In Figure 6, the choke part 40 is shown in its fully closed position. As such, fluid flow between the inlet volume 18a and the outlet volume 18b is blocked by both the main valve member 16 and the auxiliary valve member 31.”

[0077] When the choke portion 40 is opened and pressurized fluid is allowed to enter the inlet volume 18a through the inlet portion 28, the pressure in the inlet volume 18a increases, the force on the valve member 16 resulting from the contact between the fluid in the inlet volume 18a and the main valve member 16 increases until it is high enough to overcome the propulsion force of the main spring 23 and the force of the pressurized fluid in the outlet volume 18b acting on the head portion 16a of the main valve member 16. When this occurs, the main valve member 16 moves from its closed position to its open position. The auxiliary valve 31” moves along passage 24 in the opposite direction to the head portion 16a of the main valve member 16, but initially remains very close to the inner surface of the main valve member 16, thus effectively blocking passage 24. This configuration is illustrated in Figure 7.In this configuration, the fluid flow between inlet volume 18a and outlet volume 18b is... Petition 870250084509, dated 09 / 19 / 2025, page 34 / 65 24 / 32 blocked by the 30” auxiliary valve only, as this prevents significant fluid flow along passage 24.

[0078] As the pressure in the inlet volume 18a increases further, eventually the force from the fluid pressure in the inlet volume 18a on the working area of ​​the auxiliary valve 30 is sufficient to overcome the propulsive force of the main spring 23 to such an extent that the main valve member 16 moves substantially away towards its fully open position that the auxiliary valve member 31” is no longer blocking passage 24. This can occur because the auxiliary valve member 31” is no longer in passage 24. In this example, however, this occurs while the auxiliary valve member 31” is still in passage 24, but has entered the enlarged portion of passage 24.The diameter of passage 24 is, at this point, significantly larger than the outside diameter of the auxiliary valve member 31”, and as such there is a clearance large enough between the auxiliary valve member 31” and the inner surface of the main valve member 16, and the auxiliary valve 30” is open. The fluid can therefore flow from the inlet volume 18a into the outlet volume 18b through the clearance between the auxiliary valve member 31” and the main valve member 16 and passage 24. This configuration is illustrated in Figure 8.

[0079] This process is reversed if the pressure in the inlet volume 18a decreases.

[0080] It will be recognized that when the auxiliary valve 30” opens, the resulting drop in pressure in the inlet volume 18a may cause the main valve member 16 to move back towards the closed position. Petition 870250084509, dated 09 / 19 / 2025, page 35 / 65 25 / 32 As soon as the auxiliary valve member 31” blocks passage 24 again, the pressure in the inlet volume 18a will stabilize and the main valve member 16 will not move all the way back to its closed position. As such, the main valve member 16 will not strike and damage the valve seat 14.

[0081] Although not essential, in this embodiment, the auxiliary valve part 31” is tapered so that its cross-sectional area increases from a proximal end 31a” to a distal end 31b”, the proximal end 31a” being closer to the main valve member 16 than the distal end 31b”.

[0082] In the embodiment illustrated in figures 6-8, the auxiliary valve member 31” is teardrop-shaped. This is best illustrated in figure 9. Its proximal end 31a” is pointed, so that the cross-sectional area is minimal at the proximal end 31a”, increases towards the distal end 31b” and is maximal at an intermediate portion 31c” thereof. The cross-sectional area decreases again from the intermediate portion 31c” to the distal portion 31b”. It is the intermediate portion that interacts with the valve member 16 to block passage 24.

[0083] The molding of the auxiliary valve member 31” in this way can provide a more optimized fluid flow from the inlet volume 18a into passage 24, and can therefore reduce the fluid flow resistance of valve 10”. It can allow a fluid flow regime similar to a convergent plug nozzle. Petition 870250084509, dated 09 / 19 / 2025, page 36 / 65 26 / 32 divergent, thus providing a more stable throttled flow that is substantially independent of differential pressure fluctuations across the valve.

[0084] Advantageously, the area enclosed by the intermediate portion 31c” of the auxiliary valve member 31” is equal to the area enclosed by the contact line between the seal 46 and the piston part 44. In this embodiment, the cross-section of both the piston part 40 and the auxiliary valve member 31” is circular, and thus this means that the larger outside diameter of the auxiliary valve member 31 is equal to (or at least very similar to) the diameter of the contact line between the seal 46 and the piston part 44 (labeled OD in Figure 9). This means that the choke assembly (comprising the choke part 40, auxiliary valve support 34” and auxiliary valve member 31”) is pressure balanced when the choke part 40 is in its open position.In other words, the force acting on the choke portion 40 from pressurized fluid in the inlet volume 18a is counterbalanced by the force acting on the distal end 31b” of the auxiliary valve member 31”. This can help reduce the forces acting on the choke portion assembly as a result of fluid flow into the inlet volume 18a.

[0085] Similarly, the choke portion 40 and seat 42 are configured so that when the choke portion 40 is in its closed position, engaged with the seat 42, the area enclosed by the contact line between the seat 42 and the choke portion 40 is equal to or very similar to the area enclosed by the intermediate portion 31c” of Petition 870250084509, dated 09 / 19 / 2025, page 37 / 65 27 / 32 auxiliary valve member 31”, and also to the area enclosed by the contact line between the seal 46 and the piston part 44. The assembly of the choke part 31”, 34”, 40 is therefore pressure balanced when the choke part 40 is also in its closed position.

[0086] It should be recognized that the auxiliary valve member 31” does not need to be connected to the choke part 40. For example, the auxiliary valve support 34” can be fixed to the valve housing 12 to retain the auxiliary valve member 31” in the inlet volume 18a in such a position that when the main valve member 16 is in its closed position, the auxiliary valve member 31” is situated in passage 24 so that the auxiliary valve member 31” blocks passage 24. In other words, while the main valve member 16 is in its closed position, passage 24 is blocked by the auxiliary valve member 31”, and both the main valve member 16 and the auxiliary valve member 31” provide a barrier to fluid flow between the inlet volume 18a and the outlet volume 18b.

[0087] The auxiliary valve support 34” would be positioned, however, so that when the main valve member 16 is near its fully open position, the auxiliary valve member 31” no longer blocks passage 24, and fluid flow between the inlet volume 18a and the outlet volume 18b is permitted. This can occur when the main valve member 16 has moved far enough towards its fully open position for the auxiliary valve member 31” to no longer be situated in passage 24, or it can occur in the same way as described. Petition 870250084509, dated 09 / 19 / 2025, page 38 / 65 28 / 32 in relation to the embodiment illustrated in figures 6 - 8 when the auxiliary valve member 31” enters the enlarged part of the tail portion 16c and the clearance between the auxiliary valve member 31” and the main valve member 16 increases.

[0088] In this embodiment, the auxiliary valve support 34” is configured to support the auxiliary valve member 31” in the inlet volume 18a such that its longitudinal geometric axis generally coincides with the geometric axis A. It is also configured so that it does not form a barrier to fluid flow along the inlet volume 18a. It may comprise, for example, a plurality of radii extending radially inward from the valve housing 12 to the auxiliary valve member 31”.

[0089] This 10” valve type may be fitted with a 40 choke section, but this is not required.

[0090] This type of 10” valve operates as follows:

[0091] When the pressure in inlet volume 18a is low, the main spring 23 induces the main valve member 16 to its closed position. As such, fluid flow between inlet volume 18a and outlet volume 18b is blocked by both the main valve member 16 and the auxiliary valve member 31.

[0092] When pressurized fluid is allowed to enter inlet volume 18a through inlet portion 28, the pressure in inlet volume 18a increases, the force on valve member 16 resulting from the contact between the fluid in inlet volume 18a and the main valve member. Petition 870250084509, dated 09 / 19 / 2025, page 39 / 65 29 / 32 increases until it is high enough to overcome the propulsion force of the main spring 23 and the force of the pressurized fluid in the outlet volume 18b acting on the head portion 16a of the main valve member 16. When this occurs, the main valve member 16 moves from its closed position to its open position. The auxiliary valve 31” moves along passage 24 in the opposite direction to the head portion 16a of the main valve member 16, but initially remains in its closed position in which it prevents significant fluid flow along passage 24.

[0093] As the pressure in the inlet volume 18a increases further, eventually the force from the fluid pressure in the inlet volume 18a on the working area of ​​the auxiliary valve 30 is sufficient to overcome the propensity force of the main spring 23 to such an extent that the main valve member 16 moves substantially away towards its fully open position that the auxiliary valve member 31” is no longer blocking the passage 24. Fluid can therefore flow from the inlet volume 18a into the outlet volume 18b through the gap between the auxiliary valve member 31” and the main valve member 16 and along the passage 24.

[0094] This process is reversed if the pressure in the inlet volume 18a decreases.

[0095] It will be recognized that in all the embodiments disclosed, when the pressure rises in the inlet volume 18a, there is significant movement of the main valve member 16 in the opposite direction to the valve seat 14 before the auxiliary valve 30, 30” opens to allow flow. Petition 870250084509, dated 09 / 19 / 2025, page 40 / 65 30 / 32 of fluid from inlet volume 18a to outlet volume 18b.

[0096] In the embodiments illustrated in figures 1-5, when the auxiliary valve 30 opens, the resulting drop in pressure in the inlet volume 18a may allow the auxiliary spring 36 to push the auxiliary valve member 31 back to the closed position. As such, there may be vibration of the auxiliary valve 30. However, since the auxiliary valve 30 does not provide the main barrier to fluid flow between the inlet volume and the outlet volume, any resulting damage is not so critical, as it will not result in fluid leakage between the inlet volume 18a and the outlet volume 18b.

[0097] In the embodiments illustrated in figures 6 - 8, while the pressure drop in the inlet volume 18a that occurs when fluid flow from inlet volume 18a to outlet volume 18b begins may cause the main valve member 16 to move back towards its closed position, as soon as the auxiliary valve member 31” blocks the passage 24 again, the pressure in inlet volume 18a will stabilize and the main valve member 16 will not move all the way back to its closed position. As such, the main valve member 16 will not strike and damage the valve seat 14.

[0098] 10, 10', 10” valves are advantageously supplied for use in controlling the flow of an injection fluid from an annular well space into a wellbore conduit of a hydrocarbon well. The injection fluid may be a gas and the valve a pneumatic lift valve. In this case, the Petition 870250084509, dated 09 / 19 / 2025, page 41 / 65 31 / 32 Inlet volume 18a of valve 10, 10', 10” is fluidly connected to the wellbore annular space and outlet volume 18b of valve 10, 10', 10” is fluidly connected to the wellbore conduit. The wellbore conduit typically comprises the main passage of a production piping section.

[0099] Such a fluid injection system is illustrated in Figure 10. This shows a production pipeline 90 extending from a wellhead 93 located on a land surface 94. The wellhead 93 may alternatively be situated on a subsea surface, or a platform deck. A well casing 95 extends towards an underground reservoir (not shown). The production pipeline 90 comprises a pipe 91 having at least one side-socketed mandrel 92a-c. Each side-socketed mandrel 92a-c has an opening that allows fluid communication between the interior 97 of the production pipeline 90 and an annular space 96 between the well casing 95 and the production pipeline 90. At least one tool, in this embodiment, a valve 10, 10', 10” according to the invention, is disposed in each respective side-socketed mandrel 92a-c.

[00100] Such a side-pocket mandrel 92 is illustrated in Figure 11. The side-pocket mandrel 92 can be installed on the tube 91 of the production tubing 90 in a wellbore by means of end connectors 104 and 105. The side-pocket mandrel 92 has a main passage 102 which, when installed, is aligned with the main passage of the production tubing 90. This allows production fluids to pass through the side-pocket mandrel 92 and allows access to the interior of the pocket mandrel. Petition 870250084509, dated 09 / 19 / 2025, page 42 / 65 32 / 32 lateral 92 through the interior of the production pipeline 90.

[00101] The side pocket mandrel 92 also has a side offset pocket hole 107, the main passage 102 and the side offset pocket hole 107 being separated by an inner wall 109; An entry opening 106 (or alternatively, several entry openings) is provided on the outer surface of the side pocket mandrel 92 to connect the annular space 96 with the side pocket hole 107.

[00102] The valve 10, 10', 10” (illustrated schematically in figure 11) is disposed in the side pocket hole (107), inlet volume 18a of the valve 10, 10', 10, being in fluid communication with the outside of the side pocket mandrel (92) through the inlet opening or openings 106 and the outlet volume 18b of the valve 18 being in communication with the main passage 102 through an outlet hole 108 provided in the inner wall 109.

[00103] The invention is not limited by the embodiments described above; reference should be made to the appended claims. Petition 870250084509, dated 09 / 19 / 2025, p. 43 / 65

Claims

1 / 5 CLAIMS 1. A valve comprising a housing having an exterior and enclosing an interior space, the housing being provided with an inlet orifice and an outlet orifice, both of which provide a conduit between the exterior and interior space of the housing, the valve further comprising a main valve seat and a main valve member situated in the interior space of the valve housing, the main valve member being movable relative to the valve housing between a closed position in which it engages with the main valve seat and blocks the flow of fluid between the inlet orifice and the outlet orifice and an open position in which it is not engaged with the main valve seat and the inlet orifice is fluidly connected to the outlet orifice through the interior space,The main valve member having a passage that extends through the main valve member and provides a conduit for fluid flow between the inlet orifice and the outlet orifice when the main valve member is in the open position, the valve being characterized in that it further comprises an auxiliary valve member that is movable relative to the main valve member between a closed position in which the auxiliary valve member blocks the passage thereby restricting fluid flow along the passage and an open position in which substantially unrestricted fluid flow along the passage is permitted.

2. Valve, according to claim 1, characterized in that the main valve member further comprises an auxiliary valve seat with Petition 870250084509, dated 09 / 19 / 2025, page 44 / 65 2 / 5 which the auxiliary valve member engages when in the closed position to block fluid flow along the passage, the auxiliary valve seat being integral with or fixed to the main valve member.

3. A valve, according to any of the preceding claims, characterized in that an auxiliary valve member is provided in the passage.

4. A valve, according to any of the preceding claims, characterized in that it further comprises a main resilient propulsion element that acts on the main valve member to induce the main valve member to the closed position.

5. Valve according to claim 4, characterized in that the main resilient protrusion element extends between the housing and the main valve member.

6. A valve, according to any of the preceding claims, characterized in that it further comprises an auxiliary protrusion element that induces the auxiliary valve member to the closed position.

7. Valve according to claims 4 and 6, characterized in that the auxiliary propulsion element is configured to provide a greater propulsion force than the main resilient propulsion element.

8. A valve, according to any of the preceding claims, characterized in that the main valve member is linearly movable between the open and closed positions.

9. Valve, according to claim 8, characterized in that the main valve member Petition 870250084509, dated 09 / 19 / 2025, page 45 / 65 3 / 5 has a longitudinal geometric axis and generally moves parallel to the longitudinal geometric axis between the open and closed positions.

10. Valve according to claim 9, characterized in that the passage, or at least part of the passage, extends from a first end of the main valve member generally parallel to the longitudinal geometric axis.

11. A valve, according to any of the preceding claims, characterized in that the main valve member divides the interior space of the housing into an inlet volume and an outlet volume, the inlet volume comprising the portion of the interior volume of the housing with which the inlet orifice is connected when the main valve member is in its closed position, and the outlet volume comprising the portion of the interior volume of the housing with which the outlet orifice is connected when the main valve member is in its closed position.

12. A valve, according to any of the preceding claims, characterized in that it further comprises a throttling portion that is movable between a fully open position in which the cross-sectional area available for fluid flow through the inlet orifice is maximized and a variety of active positions in which the throttling portion restricts fluid flow through the inlet orifice.

13. Valve, according to claim 12, characterized in that the throttling part is movable to a fully closed position in which the throttling part blocks the inlet orifice and therefore substantially prevents fluid flow between the exterior of the valve housing and the interior volume of the housing through the inlet orifice.

14. Valve, according to claims 12 or 13, characterized in that the housing comprises an inlet volume comprising the portion of the interior volume of the housing with which the inlet orifice is connected when the main valve member is in its closed position and the throttling part is situated in the inlet volume.

15. Valve, according to any one of claims 12 to 14, characterized in that the auxiliary valve member is connected to the choke portion in such a way that the auxiliary valve member moves relative to the valve housing with the choke portion.

16. Valve according to claim 15, characterized in that the choke portion and the auxiliary valve member are configured such that the auxiliary valve member moves in the opposite direction to the main valve member when the choke portion moves towards its fully open position.

17. A valve, according to any of the preceding claims, characterized in that the auxiliary valve member is tapered in such a way that its cross-sectional area increases from a proximal end thereof towards a distal end, the proximal end being closer to the main valve member than the distal end.

18. Fluid injection system for use in a hydrocarbon well, characterized in that it comprises a valve according to any one of claims 1 - 17.

19. Fluid injection system characterized in that it comprises a valve according to any one of claims 1-17, and a tube having a side wall enclosing a main passage and a side passage extending through the side wall to the main passage, the valve being mounted on the tube so that the outlet volume of the valve is in fluid communication with the side passage.

20. Fluid injection system for a hydrocarbon well, characterized in that it comprises a valve according to any one of claims 1-17, a tubular and a mandrel with a side pocket having a main passage that is aligned with a main passage of the tubular and a laterally displaced side pocket hole, the main hole and the laterally displaced side pocket hole being separated by an inner wall, in which the valve is disposed in the side pocket hole, the valve inlet orifice being in fluid communication with the exterior of the mandrel with side pocket through an inlet opening and the valve outlet orifice being in communication with the main passage through an outlet conduit.

21. Fluid injection system according to claim 20, characterized in that the outlet conduit is provided in the inner wall. Petition 870250084509, dated 09 / 19 / 2025, pp. 48 / 65

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