Key information

Title: Downhole tubular sleeve valve and use of such a sleeve valve
Application number: 20181085
Case type: National
Status: 04.11.2019 Patent meddelt (B1)
Filed: 16.08.2018
Effective date: 16.08.2018
Publicly available: 04.11.2019
Next annual fee due: 31.08.2027
Applicant: ADVANTAGE AS (NO)
Owner: T-WELL AS (NO)
Inventor: Kenneth Fuglestad (NO)
Agent: BRYN AARFLOT AS (NO)
Granted: 04.11.2019
Patent number: 344335
Expiry date: 16.08.2038

Abstract and drawing

Disclaimer: This text has been machine-scanned and may contain errors – please refer to "Publications" for legally binding content.

A downhole tubular sleeve valve 10 includes a rotary coaxial valve sleeve 14 with a plurality of circumferentially spaced sleeve flow paths 20 extending through the valve sleeve 14. The valve sleeve 14 is located inside a housing 12. A plurality of circumferentially spaced outer bores 24 extend through the housing 12 and can be aligned with the plurality of sleeve flow paths 20. A protruding ring 26 surround each of the circumferentially spaced outer bores 24 inside the housing and form a protruding sealing surface 52 conforming to a ported surface 18 in the sleeve 14. A chamber 28 exposed to the pressure outside the valve is formed between the housing 12 and the sleeve 14, whereby a piston formed by the sleeve is exposed to the pressure outside the valve. A tension element 29 biases a sealing surface on the sleeve towards each of the protruding ring surfaces 52. The sleeve valve 10 may be used to control fluid flow between a hydrocarbon reservoir and tubing in an oil well in the hydrocarbon reservoir, or to inject fluids into a formation surrounding a well.

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Date

Date	Doc. No.	Process	Case number	In/Out	Journal description	To/from
30.04.2021	02-01	Overdragelse av søknad/rettighet	2021/05646	UT	GH Forespørsel	BRYN AARFLOT AS
16.04.2021	01-02	Overdragelse av søknad/rettighet	2021/05646	INN	General Power of attorney - signed	BRYN AARFLOT AS
16.04.2021	01-01	Overdragelse av søknad/rettighet	2021/05646	INN	Generell henvendelse	BRYN AARFLOT AS
30.06.2020	10-01	Saksbehandling	20181085	UT	PT Varsel om betaling av første årsavgift (3317) (PT20181085)
05.11.2019	09-01	Saksbehandling	20181085	UT	PT Registreringsbrev Nasjonal Patent (15) (PT20181085)
23.08.2019	08-01	Saksbehandling	20181085	UT	PT Meddelelse om patent	BRYN AARFLOT AS
21.08.2019	07-06	Saksbehandling	20181085	INN	Hovedbrev	BRYN AARFLOT AS
21.08.2019	07-05	Saksbehandling	20181085	INN	Krav	BRYN AARFLOT AS
21.08.2019	07-04	Saksbehandling	20181085	INN	Beskrivelse med sporing	BRYN AARFLOT AS
21.08.2019	07-03	Saksbehandling	20181085	INN	Beskrivelse	BRYN AARFLOT AS
21.08.2019	07-02	Saksbehandling	20181085	INN	Patenttegninger	BRYN AARFLOT AS
21.08.2019	07-01	Saksbehandling	20181085	INN	Korrespondanse (Hovedbrev inn)	BRYN AARFLOT AS
26.06.2019	06-06	Saksbehandling	20181085	INN	fig. 7 amended	BRYN AARFLOT AS
26.06.2019	06-05	Saksbehandling	20181085	INN	fig. 3 amended	BRYN AARFLOT AS
26.06.2019	06-04	Saksbehandling	20181085	INN	figs. 1-2 amended	BRYN AARFLOT AS
26.06.2019	06-03	Saksbehandling	20181085	INN	Beskrivelse	BRYN AARFLOT AS
26.06.2019	06-02	Saksbehandling	20181085	INN	Hovedbrev	BRYN AARFLOT AS
26.06.2019	06-01	Saksbehandling	20181085	INN	Korrespondanse (Hovedbrev inn)	BRYN AARFLOT AS
07.02.2019	05-02	Saksbehandling	20181085	UT	PT_report 03:27:59
07.02.2019	05-01	Saksbehandling	20181085	UT	Realitet patent	BRYN AARFLOT AS
24.10.2018	04-03	Saksbehandling	20181085	INN	Erklæring Søkers rett til oppfinnelse	BRYN AARFLOT AS
24.10.2018	04-02	Saksbehandling	20181085	INN	Fullmakt	BRYN AARFLOT AS
24.10.2018	04-01	Saksbehandling	20181085	INN	Korrespondanse (Hovedbrev inn)	BRYN AARFLOT AS
20.08.2018	03-01	Saksbehandling	20181085	UT	Formalia 1	BRYN AARFLOT AS
20.08.2018	02-01	Saksbehandling	20181085	UT	Infobrev til oppfinner	BRYN AARFLOT AS
16.08.2018	01-03	Saksbehandling	20181085	INN	Beskrivelse	BRYN AARFLOT AS
16.08.2018	01-02	Saksbehandling	20181085	INN	figures	BRYN AARFLOT AS
16.08.2018	01-01	Saksbehandling	20181085	INN	Søknadsskjema Patent	BRYN AARFLOT AS

Description, claims and drawings

Disclaimer: This text has been machine-scanned and may contain errors – please refer to "Publications" for legally binding content.

Description

DOWNHOLE TUBULAR SLEEVE VALVE AND USE OF SUCH A SLEEVE VALVE

Field of the invention

The present invention relates to a rotary sleeve valve for use in controlling fluid flow between hydrocarbon reservoirs and oil or gas wells.

Background to the invention

Sleeve valves are typically used in hydrocarbon (oil or gas) wells to control the fluid flow from a hydrocarbon reservoir into the tubing being used for the extraction of the hydrocarbon from that reservoir. This is desirable because a hydrocarbon well typically intersects several producing zones in the reservoir, each of which may have a different flow performance or a different composition in terms of the proportions of e.g. oil, gas, and/or water that are present. In addition, it is likely that during the lifetime of a well, the various production zones will change in production character, for example, the flow may change from being predominantly oil-based, to being predominantly water- or gas-based. This change of fluid type, especially from oil to gas or water has a detrimental effect on the overall productivity of the well. Therefore, an operator of the well will generally wish to optimise the productivity of the well throughout its lifetime, by either closing or choking one or more of the various production zones in the wellbore.

Similarly, in the case of injection wells, sleeve valves may be used to control the rate of injection of fluids into the reservoir.

A typical valve used to control flow from or into a hydrocarbon reservoir comprises a coaxial inner sleeve and an outer tubular housing, each of which is provided with throughthickness ports that can be brought into or out of alignment with each other by sliding the inner sleeve relative to the housing in an axial direction. One disadvantage of these types of valves is that sliding the sleeve relative to the housing in an axial direction results in a change in internal volume of the valve. This may cause solids such as sand or scale to build up in the interior region of the valve, thus preventing smooth movement valve components relative to each other.

By contrast, rotary valves comprise a housing and a coaxial valve sleeve that may be rotated in the housing to bring their respective ports into or out of alignment. The interior volume of these valves does not change during use and so the problem of solids building up inside the valve during use is reduced.

Many valves rely on elastomeric gaskets to provide seals around the ports when the valve is in the closed position. However, such gaskets are easily damaged and it has been found that after these valves have been in the closed position for some time, it is often impossible to obtain sealing again when the valve is opened and then closed once more.

To avoid the problems that arise in connection with flexible gaskets, valves having metal-to-metal seals have been developed. However, such valves are typically complex in structure in order to provide the required sealing performance, and comprise many components that have to be engineered to a high level of precision.

WO2010123588 discloses a fracture valve tool. The fracture valve tool includes a mandrel with a through passage. The mandrel has at least a first mandrel port extending from an exterior surface to an interior surface. A rotating sleeve with at least one sleeve port is rotatably positioned on the mandrel. The rotating sleeve rotates between a first position out of alignment with the at least one mandrel port and a second position where the at least one sleeve port is at least partially aligned with the mandrel port.

US2006284134 discloses variable radial flow rate control valve including a body forming a bore along the longitudinal axis thereof for transporting a fluid through the body. A fixed choke member is fixedly positioned about the bore. The fixed choke member form a fixed aperture. A rotational choke member is rotationally positioned about the bore. The rotational choke member forms a rotational aperture radially corresponding to the fixed aperture. A fluid passage is formed radially between the bore and the exterior of the body. The corresponding apertures overlap. The rotational choke member is rotatably, but not axially moveable in relation to the fixed choke member between variable radial flow rate positions.

It is desirable to provide a rotary sleeve valve for use in hydrocarbon wells that meets one or more of the following criteria:

i. it can withstand substantial differential pressure between the interior region of the valve and the region exterior to the valve, when the valve is in the closed position, without leakage occurring;

ii. it does not rely on the use of elastomeric gaskets to provide the intermittent sealing that is required to allow the valve to change between the open and closed positions; iii. it provides reliable sealing in the closed position both when the pressure of the fluid outside the valve is greater than the pressure of the fluid inside the valve and when the pressure of the fluid inside the valve is greater than the pressure of the fluid outside the valve.

Summary of the invention

At its most general, the present invention may provide a sleeve valve that is configured such that the sealing performance of the valve in the closed position is assisted by the pressure of a fluid from the interior or exterior regions of the valve. This is achieved by providing a valve that is configured such that the interface at which the one or more ports of the inner and housings of the valve are configured to meet is oriented at 90º to 30º relative to the longitudinal axis of the valve. Fluid pressure is used to urge the valve sleeve against the housing at an interface, to provide a pressure seal when the valve is in a closed position.

Therefore, in a first aspect, the present invention provides a sleeve valve controlling fluid flow between a hydrocarbon reservoir and tubing in an oil and gas well in the hydrocarbon reservoir. The sleeve valve comprise a housing and a valve sleeve coaxially located inside the housing. The valve sleeve has a ported annular end portion defining a sleeve annular ported surface oriented at an angle of 90º-30º in relation to the longitudinal axis / the axial centre line of the sleeve valve. A plurality of circumferentially spaced sleeve flow paths extend between a plurality of valve sleeve outer ports in the sleeve annular ported surface and a plurality of valve sleeve inner ports in an axial bore of the valve sleeve. A plurality of circumferentially spaced outer bores extend between a plurality of housing inner ports in a housing inner ported surface and a plurality of housing outer ports in a housing outer surface. The plurality of valve sleeve outer ports can be aligned with the plurality of housing inner ports. A protruding ring surround each of the plurality of housing inner ports, form protruding ring surfaces conforming to the sleeve annular ported surface of the annular end portion of the valve sleeve in the housing. A sleeve first cylindrical portion and a first sealing radius ri and a sleeve step to a sleeve outer cylindrical portion and a second increased sealing radius ro on the valve sleeve forms a ring shaped piston. A housing inner cylindrical portion with the first radius and a housing annular step to a housing increased radius cylindrical portion in the housing forms a ring shaped inner wall. A chamber is confined by the sleeve outer cylindrical portion, the sleeve step, the sleeve first cylindrical portion, the housing inner cylindrical portion, the housing annular step and the housing increased diameter cylindrical portion. At least one aperture extend through the housing and into the chamber. A tension element biases the sleeve annular ported surface towards the protruding ring surfaces.

An annular area defined between the second increased sealing radius ro and the first sealing radius ri may be smaller than a total area ap*n defined by an outer diameter of the protruding rings projected in a direction perpendicular to the longitudinal axis of the sleeve times the number n of protruding rings and greater than a total area ai*n defined by an inner diameter of the protruding rings projected in a direction perpendicular to the longitudinal axis of the sleeve times the number n of protruding rings.

The housing annular ported surface may include one or more protruding portions each forming a contact surface configured to conform to the sleeve annular ported surface of the first annular portion. Each protruding portion may be provided by a protruding ring extending around the one or more outer ports.

The valve sleeve is rotatable relative to the housing to align the inner and outer ports and to provide fluid communication between the region outside the valve and the bore defined by the valve sleeve.

The sleeve valve includes one or more chambers located between the valve sleeve and the housing. Each of the one or more chambers is bound in the longitudinal direction of the valve by two walls that each extend outwardly from the longitudinal axis of the valve. The chamber or chambers also include an inner wall that is provided by the valve sleeve and an outer wall that is provided by the housing, the inner wall being disposed between the first annular portion and the outer wall, and the chamber being in fluid communication with the region outside the valve.

The valve may further include two seals or sealing rings to isolate the chamber or each chamber from the valve bore. The seals are located at opposite ends of the chamber in a longitudinal direction of the valve. Each seal is located between the inner and outer sleeves, and is provided by a ring surrounding the longitudinal axis of the valve. The area enclosed by the seal adjacent to the first annular portion is greater than the area enclosed by the seal distal from the first annular portion.

Each of the one or more contact surfaces has a respective outer perimeter and the sum of the areas contained within the respective outer perimeters, when projected onto a notional plane perpendicular to the longitudinal axis of the valve, is at least as great as the difference between the areas defined by the two sealing rings, when projected onto the notional plane.

The sum of the areas of the inner walls of the one or more chambers, when projected onto the notional plane, is at least as great as the sum of the areas of the internal openings of the one or more outer ports, when projected onto the notional plane.

The valve has a single floating component (that is, the valve sleeve). This simplifies construction and maintenance of the valve.

The valve is configured to allow the valve sleeve to be rotated relative to the housing between the following three positions:

a) one or more inner ports are in full alignment with one or more outer ports: this is the open configuration of the valve, which allows fluid to flow between the bore of the valve and the region exterior to the valve;

b) one or more inner ports are in partial alignment with one or more outer ports, to regulate the extent of flow through the valve;

c) the one or more inner ports are fully out of alignment with the one or more outer ports, such that there is no fluid communication between them. The one or more outer ports are sealed by the sleeve annular ported surface of the first annular portion.

The valve is configured to improve sealing when the one or more inner ports are fully out of alignment with the one or more outer ports.

In this case, two main scenarios typically occur:

i. the pressure of the hydrocarbon fluid outside the valve (that is, the pressure of the hydrocarbon reservoir) is greater than the fluid pressure in the bore of the valve; or ii. the pressure of the fluid in the bore of the valve is greater than pressure of the hydrocarbon fluid in the reservoir external to the valve: this typically occurs during the case of injection of fluids into the hydrocarbon reservoir.

In scenario (i), the pressure of the fluid in the chamber urges the inner and outer walls of the chamber apart, in an axial direction of the valve, thus urging the sleeve annular ported surface 18 of the first annular portion against the interior surface of the second annular portion. However, the one or more outer ports are also filled with hydrocarbon fluid having the same pressure as the fluid in the chamber (since both the chamber and the one or more outer ports are in fluid communication with the hydrocarbon reservoir). The pressure of the fluid in the one or more outer ports tends to urge the valve sleeve away from the outer ports, thus counteracting the action of the fluid in the chamber. This tends to undermine good sealing of the one or more outer ports.

In order to help ensure that the action of the fluid in the one or more outer ports does not overcome the action of the fluid in the chamber, the sum of the areas of the inner walls of the one or more chambers, when projected onto the notional plane, is at least as great as the sum of the areas of the internal openings of the one or more outer ports, when projected onto the notional plane. This helps to ensure that the forces acting on the valve sleeve due to the fluid in the chamber and the fluid in the one or more outer ports are at least in balance, and preferably favour a net force urging the valve sleeve against the one or more outer ports.

In scenario (ii), the force acting on the valve sleeve is primarily due to the pressure of the fluid in the bore of the valve. This fluid penetrates as far as the two seals that isolate the chamber from the bore of the valve. The pressure of the fluid that penetrates as far as the two seals acting on the area enclosed by the two seals urges the valve sleeve away from the one or more outer ports. The fluid pressure that penetrates as far as the outside of the protruding ring extending around the one or more outer ports tends to urge the valve sleeve towards the one or more outer ports. The sum of the areas of the outside of the protruding ring extending around the one or more outer ports, when projected onto a notional plane, is at least as great as the area between the two seals that isolate the chamber from the bore of the valve.

Typically, a tension element is provided in the chamber. The tension element is configured to urge the valve sleeve towards the second annular portion. This helps to ensure that when the valve is installed, the valve sleeve is in the required axial position relative to the housing, that is, the valve sleeve is in contact with the outer ports. Preferably, the force from the tension element should be relatively low, that is, sufficient to bring the valve sleeve into contact with the outer ports, but not so great that it inhibits rotation of the valve sleeve relative to the housing.

Preferably, the sleeve annular ported surface of the first annular portion and the surface of the one or more protruding rings surrounding the one or more ports in the housing each correspond to the surfaces of a truncated cone. These surfaces thus conform to each other. Typically, the cone has an internal angle α greater than 30° relative to the longitudinal axis of the valve. Typically, the cone has an internal angle of less than 60° relative to the longitudinal axis of the valve. The angle should not be so steep that it produces a wedging and sticking effect.

The present invention thus relate to a downhole tubular sleeve valve, with an inner central valve bore. The downhole tubular sleeve valve comprises a housing and a rotary coaxial valve sleeve located inside the housing. The valve sleeve has a ported annular end portion with an angle α between 90º and 30º to an axial centreline of the sleeve valve. The ported annular end portion defines a sleeve annular ported surface forming a flat ring portion when the angle α is 90º and a frustoconical portion when the angle α is 30º. A plurality of circumferentially spaced bores extend between a plurality of valve sleeve outer ports in the ported annular end portion, and a plurality of valve sleeve inner ports in an axial bore of the valve sleeve. A housing inner annular portion interior surface has a ring shape conforming to the valve sleeve annular ported surface of the annular end portion.

A plurality of circumferentially spaced bores extend between a plurality of housing inner ports in the housing annular inner surface, and a plurality of housing outer ports in an outer cylindrical surface of the housing. The plurality of valve sleeve outer ports can be aligned with the plurality of housing inner ports. A raised or protruding ring surround each of the plurality of housing inner ports, forms protruding ring surfaces. The valve sleeve furthermore includes a sleeve first cylindrical portion and a first sealing radius ri and a sleeve step to a sleeve outer cylindrical portion and a second increased sealing radius ro on the valve sleeve, whereby the step forms a ring shaped piston.

A housing reduced cylindrical portion has the first diameter and a housing annular step to a housing increased diameter cylindrical portion whereby the housing inner annular step forms a ring shaped inner wall. A chamber is confined by the sleeve outer cylindrical portion, the sleeve step, the sleeve first cylindrical portion, the housing inner cylindrical portion, the housing annular step and the housing increased diameter cylindrical portion. At least one pressure port or aperture extends through the housing and into the chamber. A tension element biases the sleeve annular ported surface towards the protruding ring surfaces.

An area defined by the sleeve step may be smaller than a total area ap*n defined by an outer diameter of the protruding rings projected in a direction perpendicular to the longitudinal axis of the sleeve times the number n of protruding rings and greater than a total area ai*n defined by an inner diameter of the protruding rings projected in a direction perpendicular to the longitudinal axis of the sleeve times the number n of protruding rings.

The sleeve annular ported surface and the protruding ring surfaces may be oriented at an angle α of between 30° and 60° relative to the longitudinal axis of the valve.

The sleeve annular ported surface and the protruding ring surfaces may be oriented at an angle α of 45° relative to the longitudinal axis of the valve.

The tension element may be selected from a group including of leaf springs, helical springs, disc springs, elastomeric material, and/or a combination thereof.

A number of circumferentially spaced bores in the valve sleeve may be is higher than the number of circumferentially spaced bores in the housing, and a diameter of a bore of the number of circumferentially spaced bores in the valve sleeve may be different from a diameter of an adjacent bore of the circumferentially spaced bores in the valve sleeve.

The sleeve valve may further include at least a first sealing ring inserted between the sleeve first cylindrical portion and the housing inner cylindrical portion and a second sealing ring may be inserted between the sleeve outer cylindrical portion and the housing increased diameter cylindrical portion.

The housing may include a threaded pin connection at a first end and a threaded box connection at a second end.

A central housing bore and an inner sleeve valve bore may have a uniform diameter. The housing may be assembled of a first coaxial housing portion and a second housing portion, and the housing inner annular step may be formed in the first coaxial housing portion and the housing annular portion inner surface may be formed in the second housing portion.

The protruding rings may be made as inserts inserted into the housing and, the inserts may be made of a material different from the material of the housing.

The sleeve valve may be used for controlling fluid flow between a hydrocarbon reservoir and tubing in an oil well in the hydrocarbon reservoir.

The downhole tubular sleeve valve defined above may be used for injecting fluids into a formation surrounding a well.

Detailed description

The invention will now be described by way of example with reference to the following figs. in which:

Fig.1 is a perspective view of an embodiment of a sleeve valve according a first aspect of the invention, a longitudinal section of the valve being cut away to show through-thickness features of the valve;

Fig.2 shows the valve of fig.1 in an alternative configuration;

Fig.3 is a cross-sectional view of a portion of the valve of fig.2;

Fig.4 shows the valve of fig.1 in an embodiment with variable flow area;

Fig.5 shows the valve of fig.1 in an embodiment with recesses in the sleeve for actuation with a tool in the valve bore;

Fig.6 shows the valve of fig.1 in an embodiment with an actuator in the housing for rotating the sleeve; and

Fig.7 is a schematic cross section to further highlight details of the invention.

Referring to figs.1-3, a sleeve valve 10 comprises a housing 12 forming an outer sleeve, and a valve sleeve 14. The valve sleeve and housing are coaxial and the valve sleeve is located within the housing 12. The housing 12 is formed as two coaxial housing parts 12a, 12b. Housing part 12a is partly accommodated within housing part 12b and the two parts are bonded together at the region of overlap. The valve has a bore 16. A central housing bore and the valve sleeve axial bore 16 have a uniform diameter.

Sleeve valve 10 has a threaded pin connection 13a at one end and a threaded box connection 13b at the other end. The treaded pin connection and the threaded box connection are configured for connection to the remainder of the oil well production string.

The valve sleeve 14 has a sleeve annular ported surface 18. The sleeve annular ported surface 18 may be considered as convex, conical, tapered or frustoconical as long as the sleeve annular ported surface 18 not is angled 90º in relation to a central axis through the downhole tubular sleeve valve. The sleeve annular ported surface 18 extends at an oblique angle α to the longitudinal axis of the valve and corresponds to the surface of a truncated cone. A plurality of circumferentially spaced sleeve flow paths 20 is provided in the convex sleeve annular ported surface 18, each of the circumferentially spaced sleeve flow paths 20 extend through the thickness of the valve sleeve 14, so as to provide fluid communication between the convex sleeve annular ported surface 18 and the valve sleeve axial bore 16. In the figs.1, 2, 5 and 6 are the circumferentially spaced sleeve flow paths 20 inside shown as a single bore with a circular cross section and a bore diameter. In fig.4 are the circumferentially spaced sleeve flow paths 20 shown as multiple bores arranged within a circle with a diameter corresponding to the bore diameter.

The housing 12 has an interior surface forming the housing annular ported surface 22. The housing annular ported surface 22 may be considered as concave, conical, tapered or frustoconical as long as the sleeve annular ported surface 18 not is angled 90º in relation to a central axis through the downhole tubular sleeve valve. The interior surface may extend at an oblique angle to the longitudinal axis of the valve and corresponds to the surface of a truncated cone. This interior surface is configured to accommodate the convex sleeve annular ported surface 18 of the valve sleeve. A plurality of outer bores 24 are provided from the concave housing annular ported surface 22, each outer bore 24 extending through the housing 12 to provide fluid communication between the concave housing annular ported surface 22 and the region external to the valve.

Each outer bore 24 is provided with a protruding ring 26 with a concave surface 52 that is located on the housing annular ported surface 22 and extends around the perimeter of the outer bore 24. The concave surface 52 on the protruding ring 26 is forming a metal to metal seal against the convex sleeve annular ported surface 18.

An annular chamber 28 is provided between housing 12 and valve sleeve 14. The annular chamber is coaxial with the valve and is located between two gaskets formed as a first sealing ring 32 and a second sealing ring 34 respectively sealing against the first sealing surface 42 and the second sealing surface 44. That is, annular chamber 28 is bounded between the sealing surfaces 42 and 44..

A tension element 29 is positioned within annular chamber 28 and is coaxial with sleeve valve 10. The tension element 29 urges the convex sleeve annular ported surface 18 of valve sleeve 14 towards concave surface 52 on the protruding ring 26 bounding the outer bore 24.

Apertures 30 provide fluid communication between the annular chamber 28 and the region external to the valve.

Annular elastomeric gaskets or sealing rings 32, 34 are coaxial with the valve and the annular chamber 28, and are provided on opposite axial sides of annular chamber 28.

Gasket/sealing ring 32 is located within an annular recess provided on the radially inwardlyfacing surface of housing 12 sealing against the first sealing surface 42, while gasket 34 is located within an annular recess provided on the radially outwardly-facing surface of valve sleeve 14 sealing against sealing surface 44. The sealing surface 44 corresponds to the outer diameter of annular chamber 28, while the sealing surface 44 corresponds to the inner diameter of the chamber.

In use may valve sleeve 14 be rotated relative to housing 12 in order to bring the sleeve inner bores outer ports 21 and housing inner ports 23 into full alignment, thereby connecting sleeve bores/the circumferentially spaced sleeve flow paths 20 and housing bores/outer bores 24. This is the open configuration of the valve, shown in figs.1 and 7, which allows fluid to flow from the region exterior to the valve (e.g. the hydrocarbon reservoir) into the bore of the valve, from which it may flow through further connected tubing in order to be extracted from the hydrocarbon well.

Alternatively, the circumferentially spaced sleeve flow paths/inner bores 20 and outer bores 24 may be only partially aligned to regulate the extent of flow through the valve.

In a further alternative, the circumferentially spaced sleeve flow paths or inner bores 20 and outer bores 24 and the respective ports may be brought fully out of alignment, such that there is no fluid communication between them. In this case, the valve is in its closed position, shown in figs.2 and 3. The outer bores 24 are in contact with the convex annular ported surface 18 of the valve sleeve 14, through the contact between surface 52 on the protruding ring 26 and the convex annular ported surface 18 forming a metal to metal seal. Tension element 29 urges annular ported surface 18 against surface 52 on the protruding ring 26, thus providing an initial surface pressure and hence seal for the outer bores 24.

Additionally, fluid from the hydrocarbon reservoir is present within annular chamber 28 due to aperture 30, which provides fluid communication between the chamber and the region external to the valve. The pressure of the fluid (corresponding to the pressure within the hydrocarbon reservoir at the location of the valve) acts on the area enclosed by the two sealing rings 32 and 34 respectively sealing against sealing surfaces 42 and 44, thus urging the convex annular ported surface 18 of valve sleeve 14 towards surface 52 on the protruding ring 26 bounding the outer bores 24, so as to increase the effectiveness of the metal to metal sealing mechanism for the outer bores 24.

Gaskets/sealing rings 32, 34 respectively sealing against surfaces 42, 44 prevent leakage between the valve sleeve 14 and housing 12.

Referring to fig.3, fluid from the hydrocarbon reservoir is also present in outer bores 24, and presses against convex annular ported surface 18, thus urging valve sleeve 14 in direction A and tending to undermine good metal to metal sealing between the convex annular ported surface 18 and the concave surface 52. The surface area enclosed by the two sealing rings 32 and 34 sealing against sealing surfaces 42 and 44 respectively (fig.7), is greater than a perpendicularly projected total cross-sectional area of the internal openings of the protruding rings 26 surrounding each of the one or more outer ports. This perpendicularly projected total cross-sectional area is projected onto a notional plane 40 perpendicular to the longitudinal axis of sleeve valve 10. The surface area enclosed by the two sealing rings 32 and 34 (Fig.7) sealing against sealing surfaces 42 and 44 forms a step 45 defining a ring shaped piston. This contributes to ensure that the force generated on the area enclosed by the two sealing rings 32 and 34 (fig.1) in direction B (that is, towards outer bores 24) is greater than the force generated in direction A (that is, away from outer ports) by the fluid present in outer bores 24.

In certain cases, typically in the case of injection of fluids into the oil well, the pressure inside the valve sleeve axial bore 16 is significantly greater than the pressure within the hydrocarbon reservoir. Referring to fig.3, internal fluid penetrates between convex annular ported surface 18 and concave housing annular ported surface 22, as far as gasket/sealing ring 34 and between valve sleeve 14 and the first housing part 12a of the housing where the internal fluid pressure generating force on the area enclosed by the two gaskets/sealing rings 32 and 34 respectively sealing against sealing surfaces 42 and 44. The internal fluid pressure tends to act to separate convex annular ported surface 18 from surface 52, thus urging the valve sleeve in direction A.

In order to prevent valve sleeve 14 to be urged in direction A, the following is necessary:

the area enclosed by the two sealing rings 32 and 34 respectively sealing against sealing surfaces 42 and 44 should be less than or equal to the total area covered by the outer diameter 50 of the protruding rings 26, when this is projected onto the notional plane 40 perpendicular to the longitudinal axis of sleeve valve 10.

Fig.4 primarily corresponds to the 1, 2, 5 and 6 apart from showing an embodiment that can provide varying flow rate. The each of the circumferentially spaced bores is divided into set of multiple bores providing a variable flow area. The variable flow area is achieved by forming the each of the circumferentially spaced sleeve flow paths 20 on fig.1 as multiple bores 11 formed of a number of individual bores in a pattern allowing a variation of the number of bores that is covered by the housing inner ports 23, thus providing variable flow area upon rotation of the inner sleeve in relation to the housing. The housing is rotated in increments to ensure that each of the multiple bores 11 is either completely covered and thus not allow flow, or is completely open and thus allow flow. The Intermediate positions should be avoided to prevent erosion of the sealing surfaces. By forming each circumferentially spaced sleeve flow path as a pattern of as multiple bores 11 formed as a number of individual smaller bores inside a diameter of each circumferentially spaced sleeve flow path, can the all the individual small bores be covered by the housing inner ports 23.

Intermediate positions should also be avoided in the embodiments without ports / bores with multiple bores 11 of the same reason, and the increments in the rotation of the sleeve in these embodiments should thus be greater. The invention may thus include a mechanism that prevents location of the inner sleeve in intermediate positions.

Fig.5 primarily corresponds to the 1, 2, 4 and 6, apart from showing housing latch recesses 31 and sleeve latch recesses 51. An actuating tool may be inserted into the valve and latches on the tool may be moved into the latch recesses in the housing and in the sleeve. The sleeve latch recesses 51 provides a gripping surface for the tool. The latching between both the tool and the housing and the tool and the sleeve provides excellent control of the positioning of the sleeve in relation to the housing and thus the positioning of the ports in the sleeve and the ports in the housing. The tool gripping into the latch recesses may be a dedicated actuation tool with a fixed portion and a rotating portion and actuated latching members for selectively gripping or leasing the housing and the sleeve.

Fig.6 primarily corresponds to the 1, 2, 4 and 5, apart from showing a rotation / valve actuator 35 for rotating the sleeve in increments in relation to the housing. The valve actuator 35 is typically an electric actuator. The valve actuator 35 may also be hydraulic.

The increments are typically sufficient to move the sleeve in a distance in a circumferential direction somewhat in excess of one diameter of a diameter of the outer ports of the sleeve.

The embodiments with both the multiple bores and the single bores may be actuated by an actuator or a tool.

Fig.7 is a schematic cross section of a sleeve valve of the invention and as shown in figs.1-3, enclosed to further highlight the invention. A first housing part 12a is secured to a second housing part 12b with a screw connection. The housing parts are tubular/cylindrical and have a cylindrical outer surface 33. The screw connection between the first and second housing part 12a, 12b allows the valve sleeve 14 to be installed before the housing 12 is assembled. The first housing part 12a also defines the housing annular step 27 and the housing inner cylindrical portion 47. The second housing part 12b defines a housing outer cylindrical portion 48, an aperture 30 allowing pressure into the annular chamber 28, and a sleeve annular ported surface 18 of a ported annular end portion 17. The housing annular ported surface (22 in fig.3) is shown with an inclination a of 45º to a centre line C.L.. This angle is of less importance as long as the surface of the protruding rings 26 seals against the valve sleeve 14.

The diameter of the housing inner cylindrical portion 47, corresponds to the diameter of the sleeve first cylindrical portion 41, and the diameter of the sleeve outer cylindrical portion 43, corresponds to diameter of the housing outer cylindrical portion 48. The sleeve first cylindrical portion 41 has a reduced diameter compared to the sleeve outer cylindrical portion 43. A height of the step 45 on the valve sleeve 14 and a height of the housing annular step 27 corresponds with the difference between the inner and outer portions. These diameters are more or less equal and have tolerances to allow the valve sleeve 14 to rotate and slide lengthwise somewhat in the housing 12, i.e. to prevent the valve sleeve 14 to be fixed to the housing 12.

The first and a second sealing ring 32 and 34 allow the valve sleeve 14 to rotate and shift slightly in the longitudinal direction in the housing 12 while keeping a fluid tight seal between the inner bore of the valve and the housing outer ports 25. A pressure outside the valve will enter the aperture 30 and act on the annular surface formed by step 45, and press the valve sleeve 14 to the right on the fig. The sealing rings 32 and 34 define the area of step 45 when sealing rings are used. This area can be expressed as πro2- πri2 where ro is the sealing radius of the sleeve outer cylindrical portion 43 and ri is the sealing radius of the sleeve first cylindrical portion 41. This assumes that the sealing rings 32 and 34 are located in recesses in the housing. If the sealing rings 32 and 34 are located in recesses in the sleeve as shown in fig.1, then the inner sealing radius ri and the outer sealing radius ro are the radiuses of the corresponding inner diameters of the housing, and the area of step 45 changes slightly. The pressure outside the valve will also act on an area corresponding to an area of each of the housing inner ports 23 times the number of ports in the housing 12 resulting in a force with a component in the opposite direction along the C.L when the valve is in a closed position. This area equals the area n * ai where n is the number of ports 23 and ai is the projected area of each port. This area should be less than the area of the step 45 (as defined by the sealing rings 32, 34) explained above. The area of the step 45 can be considered as the area the pressure in the annular chamber 28 between the first and second sealing ring 32 and 34, contacting the sealing surfaces 42, 44 shown on fig.1.

Each protruding ring 26 has an inner diameter defined by the housing inner ports 23 and a protruding ring outer diameter 50. The width of these raised or protruding rings 26 correspond to the difference between the above-mentioned diameters. The forces acting on the valve sleeve 14 to the right is distributed between the protruding rings 26, and must exceed the forces exerted by the external pressure projected in a direction parallel to the C.L. acting on the area of the housing inner ports 23 times the number of ports on the valve sleeve 14.

A circumferential distance between inner bores outer ports 21 must exceed a width of the protruding rings 26 outer diameters 50 to allow sufficient surface area on the annular ported surface 18 to produce a proper seal between the protruding rings 26 and the annular ported surface. The protruding rings 26 have a slightly curved front surface adapted to the curvature of the annular ported surface. In the event the angle a is 90º, then this surface is flat, and the above mentioned front surface is flat. The annular ported surface 18 is located on the ported annular end portion 17.

In other words, each of the one or more contact surfaces correlated with the one or more of the housing inner ports 23 has a respective outer perimeter/diameter 50 and the sum of the areas of the housing inner ports 23 contained within the respective outer perimeters, when projected onto a notional plane perpendicular to the C.L. is at least as great as the difference between the area of the step 45 enclosed by the first and second sealing rings 32, 34, when projected onto the notional plane. The sum of the areas of the inner walls of the one or more chambers, when projected onto the notional plane, is at least as great as the sum of the areas of the internal openings of the one or more outer ports, when projected onto the notional plane. “ai” is shown on fig.3.

The protruding rings 26 may be integrated in the housing or may be inserted into the housing as protruding ring inserts. Protruding ring inserts may include non-metallic materials, ceramics, sintered materials, elastomeric materials, composite materials, metallic materials etc.

Claims

CLAIMS

1. A downhole tubular sleeve valve (10) with an inner central valve bore comprising: a housing (12) and a rotary coaxial valve sleeve (14) located inside the housing (12), wherein the valve sleeve (14) has a ported annular end portion (17) defining a sleeve annular ported surface (18) with an angle α between 90º and 30º to an axial centreline C.L of the sleeve valve (10);

a plurality of circumferentially spaced sleeve flow paths (20) extending between a plurality of valve sleeve inner bores outer ports (21) in the sleeve annular ported surface (18) and a plurality of valve sleeve inner ports (19) in an axial bore (16) of the valve sleeve (14);

a plurality of circumferentially spaced outer bores (24) extending between a plurality of housing inner ports (23) in a housing annular ported surface (22) and a plurality of housing outer ports (25) in a housing (12) outer surface (33), whereby the plurality of valve sleeve inner bores outer ports (21) can be aligned with the plurality of housing inner ports (23);

a protruding ring (26) surrounding each of the plurality of housing inner ports (23), forming protruding ring surfaces (52) conforming to the sleeve annular ported surface (18) of the ported annular end portion (17) of the valve sleeve (14), in the housing (12);

a sleeve first cylindrical portion (41) and a first sealing radius ri and a sleeve step (45) to a sleeve outer cylindrical portion (43) and a second increased sealing radius ro on the valve sleeve (14), whereby the step (45) forms a ring shaped piston;

a housing inner cylindrical portion (47) with the first radius and a housing annular step (27) to a housing increased radius cylindrical portion (48) in the housing, whereby the housing annular step (27) forms a ring shaped inner wall;

an annular chamber (28) confined by the sleeve outer cylindrical portion (43), the sleeve step (45), the sleeve first cylindrical portion (41), the housing inner cylindrical portion (47), the housing annular step (27) and the housing increased diameter cylindrical portion (48);

at least one aperture (30) through the housing (12) and into the annular chamber (28); and

a tension element (29) biasing the sleeve annular ported surface (18) towards the protruding ring surfaces (52).

2. The sleeve valve (10) according to claim 1, wherein an annular area defined between the second increased sealing radius ro and the first sealing radius ri is smaller than a total area ap*n defined by an outer diameter (50) of the protruding rings (26) projected in a direction perpendicular to the longitudinal axis of the sleeve times the number n of protruding rings (26) and greater than a total area ai*n defined by an inner diameter of the protruding rings (26) projected in a direction perpendicular to the longitudinal axis of the sleeve times the number n of protruding rings (26).

3. The sleeve valve (10) according to claim 1, wherein the sleeve annular ported surface (18) and the protruding ring surfaces (52) are oriented at an angle α between 30° and 60° relative to the longitudinal axis of the valve.

4. The sleeve valve (10) according to claim 1, wherein the sleeve annular ported surface (18) and the protruding ring surfaces (52) are oriented at an angle α of 45° relative to the longitudinal axis of the valve.

5. The sleeve valve (10) according to claim 1, wherein the tension element (29) is selected from a group including of leaf springs, helical springs, disc springs, elastomeric material, and/or a combination thereof.

6. The sleeve valve (10) according to any of the preceding claims, wherein each circumferentially spaced sleeve flow paths (20) in the valve sleeve (14) is divided into a pattern of multiple bores (11).

7. The sleeve valve (10) according to any of the preceding claims, further comprising at least a first sealing ring (32) defining the first sealing radius ri, inserted between the sleeve first cylindrical portion (41) and the housing inner cylindrical portion (47) and a second sealing ring (34) defining the second increased sealing radius ro, inserted between the sleeve outer cylindrical portion (43) and the housing outer cylindrical portion (48).

8. The sleeve valve (10) according to any of the preceding claims wherein the housing (12) includes a threaded pin connection (13a) at a first end and a threaded box connection (13b) at a second end.

9. The sleeve valve (10) according to any of the preceding claims wherein a central housing bore (15) and a valve sleeve axial bore (16) have a uniform diameter.

10. The sleeve valve (10) according to any of the preceding claims wherein the housing (12) is assembled of a first coaxial housing part (12a) and a second housing part (12b), and wherein the housing inner annular step (27) is formed in the first coaxial housing part (12a) and the housing annular ported surface (22) is formed in the second housing part (12b).

11. The sleeve valve (10) according to any of the preceding claims wherein the protruding rings (26) are made as inserts inserted into the housing (12) and, wherein the inserts are made of a material different from the material of the housing.

12. Use of a sleeve valve (10) according to any one of the preceding claims for controlling fluid flow between a hydrocarbon reservoir and tubing in an oil well in the hydrocarbon reservoir.

13. Use of a downhole tubular sleeve valve (10) according to claim 1, for injecting fluids into a formation surrounding a well.

PATENTKRAV

1. En rørformet nedihulls hylseventil (10) med en indre, sentral, ventilboring omfattende:

et hus (12) og en koaksial roterbar ventilhylse (14) plassert i huset (12), idet ventilhylsen (14) har et portet ringformet endeparti (17) som definerer en ringformet, portet, hylseoverflate (18) med en vinkel α på mellom 90 og 30 º i forhold til en aksiell senterlinje CL av hylseventilen (10);

et antall hylsestrømningsveier (20) anbrakt med innbyrdes avstand langs en omkrets og som strekker seg mellom ytre porter (21) på ventilhylsens indre boringer i hylsens ringformede, portede, hylseoverflate (18) og et antall ventilhylse indre porter (19) i en aksial boring (16) av ventilhylsen (14);

et antall ytre boringer (24) anbrakt med innbyrdes avstand langs en omkrets, og som strekker seg mellom et antall, indre porter (23) i huset, i en ringformet, portet, overflate (22) på huset og et antall, ytre porter (25) i huset, i en ytre overflate (33) av huset (12), hvorved antallet ytre porter (21) på ventilhylsens indre boringer kan innrettes i med antallet indre porter (23) i huset;

en forhøyet ring (26) som omgir hver av antallet innvendige porter (23) på huset, og som danner forhøyede ringflater (52) som samsvarer med den ringformede, portede, hylseoverflaten (18) av det portede, ringformede, endepartiet (17) av ventilhylsen (14), i huset (12);

et første sylindrisk hylseparti (41) og en første tetningsradius ri og et hylstrinn (45) til et ytre sylindrisk parti (43) på hylsen og en andre økt tetningsradius ro på ventilhylsen (14), hvorved trinnet (45) danner et ringformet stempel; et indre, sylindrisk husparti (47) med den første radiusen og et i huset ringformet trinn (27) opp til et sylindrisk parti (48) av huset med økt radius, hvorved husets ringformede trinn (27) danner en ringformet innervegg;

et ringformet kammer (28) avgrenset av hylsens ytre sylindriske del (43), hylstrinnet (45), hylsens første sylindriske del (41), husets indre sylindriske del (47), husets ringformede trinn (27) og husets sylindrisk del (48) med økt diameter;

minst en åpning (30) gjennom huset (12) og inn i det ringformede kammeret (28); og

et spenningselement (29) som forspenner den ringformede, portede, hylseoverflaten (18) mot de forhøyede ringflatene (52).

2. Hylseventil (10) ifølge krav 1, hvori et ringformet område definert mellom den andre økte tetningsradius ro og den første tetningsradius ri er mindre enn et totalareal ap * n definert av en ytre diameter (50) av de forhøyede ringer (26) projisert i en retning vinkelrett på lengdeaksen av hylsen ganger antall n av de forhøyede ringer (26) og større enn et totalt areal ai * n definert av en indre diameter av de forhøyede ringer (26) projisert i en retning vinkelrett på hylsens lengdeakse ganger antallet n av forhøyede ringer (26).

3. Hylseventil (10) ifølge krav 1, hvori den ringformede, portede hylseoverflaten (18) og de forhøyede ringflatene (52) er orientert i en vinkel α mellom 30 ° og 60 ° i forhold til ventilens lengdeakse.

4. Hylseventil (10) ifølge krav 1, hvori den ringformede, portede hylseoverflaten (18) og de forhøyede ringflatene (52) er orientert i en vinkel α på 45 ° i forhold til ventilens lengdeakse.

5. Hylseventil (10) ifølge krav 1, hvori spenningselementet (29) er valgt fra en gruppe som inkluderer bladfjærer, spiralfjærer, skivefjærer, elastomerisk materiale og / eller en kombinasjon av disse.

6. Hylseventil (10) ifølge et av de foregående krav, hvor hver hylsestrømningsvei (20) anbrakt med innbyrdes avstand langs en omkrets i ventilhylsen (14) er delt inn i et mønster av flere boringer (11).

7. Hylseventil (10) ifølge et av de foregående krav, videre omfattende minst en første tetningsring (32) som definerer den første tetningsradius ri, innsatt mellom hylsens første sylindriske del (41) og husets indre sylindriske del (47) og en andre tetningsring (34) som definerer den andre økte tetningsradius ro, innsatt mellom hylsens ytre sylindriske del (43) og husets ytre sylindriske del (48).

8. Hylseventil (10) ifølge et av de foregående krav, hvori huset (12) innbefatter en gjenget tappforbindelse (13a) i en første ende og en gjenget muffeforbindelse (13b) i en andre ende.

9. Hylseventil (10) ifølge et av de foregående krav, hvori en sentral husboring (15) og en aksial boring (16) i ventilhylsen har jevn diameter.

10. Hylseventil (10) ifølge et av de foregående krav, hvori huset (12) er satt sammen av en første koaksial husdel (12a) og en andre husdel (12b), og hvor husets indre ringformede trinn (27) er dannet i den første koaksiale husdel (12a) og den ringformede, portede overflate (22) på huset er dannet i den andre husdel (12b).

11. Hylseventil (10) ifølge et av de foregående krav, hvori de forhøyede ringer (26) er laget som innsatser satt inn i huset (12), og hvor innsatsene er laget av et annet materiale enn husets materiale.

12. Anvendelse av en hylseventil (10) ifølge et av de foregående krav for å styre fluidstrømning mellom et hydrokarbonreservoar og rør i en oljebrønn i hydrokarbonreservoaret.

13. Anvendelse av en rørformet hylseventil (10) i borehull ifølge krav 1, for å injisere væsker i en formasjon som omgir en brønn.

Drawings

Priority

No priority

Patent classes

IPC classes

E21B 34/14

E21B 43/12

E21B 34/00

F16K 3/02

CPC classes

E21B 34/14

E21B 43/12

E21B 2034/007

F16K 3/0236

Citations

WO 2010/123588 A2 (A2)

US 2006/0284134 A1 (A1)

Applicants, owners and inventors

Owners

T-WELL AS

c/o Robert Greene, Gangflåtveien 3

4018 STAVANGER

NO (STAVANGER Municipality, Rogaland county)

Org. number: 918072608

Inventors

Kenneth Fuglestad

Steinalderveien 28

4340 BRYNE

NO (TIME Municipality, Rogaland county)

Agent

BRYN AARFLOT AS

Stortingsgata 8

0161 OSLO

NO (OSLO Municipality, Oslo county)

Org. number: 979993269

Reference: 130891/JH

Status history

Payment history

Oppositions and appeals

No oppositions or appeals

Administrative limitation

No administrative limitation

Liens and licences

No liens or licenses registered

Gazette entries

No Gazette entries found

Only events from 2024.03.04 and onwards are shown.

Downhole tubular sleeve valve and use of such a sleeve valve