GB2549815A - Gate assembly - Google Patents

Abstract

A gate assembly for a blowout preventer having two gates (3 and 4) each comprising a through hole (5 and 6) such that, when the valve is open the holes align concentrically. Recesses (81) are provided in the gates and configured to receive the other, in a closed configuration. Side packer seals (90 and 91) are provided in seal grooves and energized by contact with each other in the closed configuration. Pressure on the side packer seals also energise the gate seal, which seals between the gates when closed and sits in a seal groove (99). The seals may be non-metallic or elastomeric.

Description

GATE ASSEMBLY

The present invention relates to a gate assembly for wellbore control devices, and more particularly to blow out preventers and related systems for closing a petroleum well also in the presence of tools or conduits, such as a drill string, in the wellbore.

BACKGROUND

In the oil and gas industry, production or exploration wells are provided with one or more cutting devices or well bore control devices, such as a blow out preventer or riser control device, for sealing the well bore in the event of an emergency in order to protect personnel and the environment. Conventional wellbore control devices have cutting rams mounted perpendicular to a vertical throughbore. The rams can be activated to sever a tubular disposed in the wellbore and seal the well bore. The cutting rams move through a horizontal plane and are often driven by in-line piston hydraulic actuators.

Documents which can be useful for understanding the background include US 2016/0108694, US 8,353,338, US 4,969,390, US 2632425, US 3050943, US 3242826, US 3918478, US 3941141, US 4188860, US 4290577, US 4305565, US 4519571, US 4601232, US 4840346, US 4969627, US 5025708, and US 5056418.

Such well bore control devices must withstand extreme conditions during use, which sets stringent requirement to their design. In order that the well can be closed and sealed in an emergency, the device must be able to cut anything present in the wellbore, which can be a drilling tubular, casing, or tools for well intervention. Moreover, effective sealing is required against what may be very high wellhead pressures. Since complicated handling and installation procedures will be carried out, it is further desirable that the device be compact.

The present invention has the objective to provide a wellbore control device which provides advantages over known solutions and techniques.

SUMMARY

In an embodiment, there is provided a gate assembly as outlined in the appended claim 1. In other embodiments, there is provided a gate assembly as outlined in any one of claims 26-45.

BRIEF DESCRIPTION OF THE DRAWINGS

Examplatory embodiments of the present invention will now be described with reference to the appended drawings, in which:

Figures 1-6 show different views of a device according to an embodiment. Figures 7-10 show various aspects of gates and a gate assembly.

Figure 11a shows details of an actuator unit.

Figure 11 b shows a locking apparatus.

Figures 12-14 show various aspects of an embodiment.

Figures 15-22 show further details of the device shown in Figs. 1-6.

DETAILED DESCRIPTION

Figures 1-6 show a device 100 according to an embodiment, suitable for use as e.g. a wellbore control device, cutting device or a blow-out preventer in a subsea or surface wellhead system. The device comprises a housing 1 having a throughbore 2. A first gate 4 and a second gate 3 are arranged in the housing and adapted to move transversely and in different (in this example opposite) directions in relation to the throughbore 2. The gates 3 and 4 have respective holes 5 and 6 (see Fig. 2). In the open position (Fig. 4), the holes 5 and 6 overlap and are aligned substantially co-axially with the throughbore 2 to permit passage through the throughbore, for example of a tubular holding drilling tools (e.g. a drill string) or a wireline carrying well intervention equipment. In the closed position (Fig. 6), the gates 3 and 4 are moved so that holes 5 and 6 do not overlap and the gates 3 and 4 split the throughbore into an upper portion and a completely separate lower portion, thus closing the throughbore.

Fig. 1 shows the device 100 in an operational configuration and Fig. 2 shows a partially disassembled view of the device 100. A first bonnet 103 and a second bonnet 104 are fixed to the housing 1. The bonnets 103 and 104 can be released from the housing 1 and moved away from the housing 1 along rails 105-108. This permits maintenance and repairs to be carried out, for example replacement of the gates 3 and 4. The bonnets 103 and 104 also comprise hydraulic actuators, as will be described in further detail below.

Rod locking apparatuses 201 and 202 are provided and configured to lock the gates 3 and 4 in the locked position, in a manner which will be described in further detail below.

The first gate 4 and the second gate 3 define a shearing face between them, such that upon movement from the open position to the closed position, a tubular (or other equipment) located in the throughbore 2 will be sheared by the edges of holes 5 and 6. The shearing edges of holes 5 and 6 may be provided with a hardened surface compared to the rest of the gate body, e.g. by means of hardened cutting-edge inserts (shown as item 75 and 76 in Fig 12). For example, an MP35 material or equivalent may be suitable for this purpose.

In the closed position (Fig. 6), holes 5 and 6 are left in a position where each hole 5 or 6 remains in communication to the throughbore 2. This is achieved by arranging the end (“closed”) position of the gates 3 and 4 at a position where the sections of the gates 3 and 4 comprising the holes are not moved fully out of the throughbore 2 and thus not moved completely into the housing 1. Alternatively, the wellbore control device can be arranged so that only one of the holes 5 and 6 or part of one of the holes 5, 6 remain aligned with the throughbore 2, for example hole 6 in the upper gate 4, whereas hole 5 in the lower gate 3 is moved fully into the housing 1.

Figure 3 shows a top view of the device shown in Fig. 1.

Figure 4 shows a side cut view (section A-A as indicated in Fig. 3) of the device 100 in an open position.

Figures 5 and 6 show a top, partially cut view of the device 100. Figure 5 shows the gates 3 and 4 near the fully closed position and Figure 6 shows the gates 3 and 4 in the fully closed position.

Referring now to Fig. 4, a first piston rod 12a is operably connected to the first gate 4 and a second piston rod 12b is operably connected to the second gate 3. The first and second gates 3 and 4 are supported by the housing 1 and movable transverse to the throughbore 2 between an open position and a closed position. In the open position the holes 5 and 6 are aligned with the throughbore 2 and/or encompass the throughbore 2. In the closed position the gates 3 and 4 split an upper portion 2’ of the throughbore 2 completely from a lower portion 2” of the throughbore 2.

The rods 12a and 12b in this embodiment here are made up of individual segments connected together, however may equally well be formed in one piece as a single piece. A first actuator piston 312a, operating in a first actuator cylinder 313a, and a first piston rod 12a are operably connected to the first gate 4. The first actuator piston 312a has a first stroke length. A second actuator piston 312b, operating in a second actuator cylinder 313b, and a second piston rod 12b are operably connected to the second gate 3. The second actuator piston 312b has a second stroke length x. (See Fig. 4.) The first stroke length is, in this embodiment, identical to the second stroke length x, however in other embodiments this need not necessarily be the case. The first and second stroke lengths x are less than a diameter z of the throughbore 2.

The first piston rod 12b and the second piston rod 12b are arranged along a common axis 13.

In use, movement of the gates 3,4 from the open position to the closed position will thus shear (sever) an object such as a tubular located in the throughbore 2. Advantageously, permitting part of one or both of the first and second holes 5,6 to remain in alignment with the throughbore 2 in the closed position allows a part of the cut object, such as a tubular, to remain in the hole after cutting, thus it is not necessary to do a “double cut”, or to have a mechanism for lifting the cut object out of the hole, as would be required for the gate to move fully into the housing in the closed position. Such lifting of a drilling tubular may be extremely challenging, as a tubular may extend over several hundred meters from a topside facility and the total weight may be several hundred tons. A double cut would require cutting also the tubular between the gate 3 or 4 and the housing 1. A further advantage of this embodiment is that gates 3, 4, as opposed to conventional rams, are fully supported for loads around the throughbore 2. Once an object, such as a drill string, has been cut, or even during cutting, its full weight will rest on, and have to be carried by, the gates 3, 4. The same will be the case if the object is in compression or tension, which may equally create very high vertical loads on the cutting elements. By having gates 3, 4 which are supported by the housing 1, any bending of the gates due to forces from the cut object, or splitting/separation of the gates due to cutting loads acting at the shearing point between the gates, is avoided. Thus, in the case of e.g. a BOP system, the gates will be supported for vertical loads during the entire cutting and sealing position, both from above and below.

By providing the first and second gates 3, 4 with first and second holes 5, 6 which are aligned substantially co-axially with the throughbore 2 in the open position allows the device 100 to be designed with a through passage essentially without snag points. The holes 5, 6 can be designed essentially flush with the throughbore 2 walls.

In this embodiment, due to the use of gates with holes compared to conventional cutting rams, the tubular (e.g. drilling pipe) will be forced to the center of in the throughbore 2 upon cutting, thus there will be no risk of the cutting elements not being able to “catch” and engage the tubular. This can be a problem if e.g. the drilling pipe is forced to one side of the throughbore 2 by tension or weight forces.

As is most clearly seen from Fig. 4, the gates 3 and 4 are actuated by means of hydraulic actuators arranged in relation to the bonnets 103 and 104. The actuators comprise hydraulically driven piston-cylinder arrangements. The gates 3 and 4 are actuated by pistons 312a and 312b operable in cylinders 313a and 313b, respectively, and by pistons 314a and 314b operating within cylinders 315a and 315b, respectively. The cylinders 315a and 315b are arranged in tandem actuators 307a and 307b, each fixed to a respective bonnet 103 or 104.

Figure 11a show further details of the actuators and the tandem actuators. The bonnet 104 has a cylinder 313b arranged in the bonnet 104, with a respective piston 312b. A tandem actuator 307b is provided in conjunction with the bonnet 104. The tandem actuator 307b also has a cylinder 315b and respective piston 314b. The tandem actuator 307b is secured to the bonnet 104 by means of an attachment device, for example a latch ring and a locking ring, as can be seen in Fig. 11a. The locking apparatus 202 is attached in an equivalent manner to the tandem actuator 307b.

The second piston rod 12b extends out of the housing 1 and into the bonnet 104. The second piston rod 12b is connected to the piston 312b and extends further into the tandem actuator 307b. The tail end of the second piston rod 12b extends into the locking device 202, and the locking device 202 may be operated to engage the tail end and to prevent movement of the tail end when the device is in the closed position (see Fig. 4 and 6).

The piston 314b of the tandem actuator 307b is a floating piston 314b which is slidably arranged on the second piston rod 12b. The second piston rod 12b comprises a mechanical stop 422. The mechanical stop 422 may be a shoulder on the second piston rod 12b. When the back side (right hand side in Fig. 11 b) of the floating piston 314b is pressurized in cylinder 315b, the floating piston 314b will be urged towards the mechanical stop 422 and thus contribute to actuating the gate via the second piston rod 12b.

The floating piston 314b may have a shorter stroke length than the piston 312b. This improves the compactness of the overall unit. For example, when cutting an object located in the throughbore 2, such as a drill string, with the gates 3 and 4, the highest force requirements will be during the cutting process. After the cut has been done, the final movement of the gates may be merely to fully close the gates 3 and 4 and actuate the seals. This final movement requires much less actuation force.

By providing the floating piston 314b with a shorter stroke length than the piston 312b, the floating piston 314b may contribute actuation force for part of the stroke, while not consuming hydraulic fluid during the rest of the actuation stroke (for example during the final movement as noted above). This can be achieved by designing the cylinder 315b such that the floating piston 314b is stopped against an end stop 423 within the cylinder after a pre-determined stroke length for the floating piston 314b.

The cylinder 315b may be provided with a recess 424 being adapted for receiving the mechanical stop 422 during part of the stroke length of the actuator. This allows the end stop for the floating piston 314b to be the end 423 of the cylinder 315b, while the second piston rod 12b with the mechanical stop 422 may continue its motion over the final part of the actuation stroke as the floating piston 314b stops at the end 423 of the cylinder 315b, while the second piston rod 12b can continue its motion, sliding along within the floating piston 314b. Figure 5 shows the position during the stroke at which the floating piston 314b has reached the end stop 423, while Figure 6 illustrates how the piston 312b continues the actuation stroke to bring the gates into the fully closed position with the floating piston at its end stroke position. This allows the cylinder 315b to be designed with a length substantially equal to the stroke length of the floating piston 314b, thus allowing for a shorter and more compact tandem actuator 307b.

This moreover may provide advantages in relation to the operation of the device in certain embodiments. Since, in some embodiments, the sealing between the housing 1 and the gates 3 and 4 may be designed to be energized only upon nearly full or full closure of the valves (see below), it may be important to maintain a closing force from the actuators in order to keep the seals energized. By providing an actuator design according to some of the embodiments described above, it will be possible to maintain a closing force from piston 312b by keeping cylinder 313b pressurized, however while avoiding having to employ the full closing/shearing force of the device for this (relatively less demanding) purpose. This may improve system lifetime and energy usage.

The actuator arrangement on the opposite side, i.e. in relation to gate 4 and bonnet 103, is designed and operates equivalently.

Figures 7-10 show further details of the gates 3 and 4 and associated components, according to one embodiment. Fig. 7 shows a gate assembly for use in a device as described above, the gate assembly comprising a first gate 4 and a second gate 3. The first gate 4 has a front part 4’ and a rear part 4”, and the second gate 3 has a front part 3’ and a rear part 3”. The first hole 6 is arranged in the front part 4’ of the first gate 4, and the second hole 5 is arranged in the front part 3’ of the second gate 3. The front parts 3’ and 4’ protrudes from the rear parts 3” and 4” forwardly as seen in the direction of travel when the respective gate 3 or 4 moves from the open position to the closed position.

The second gate 3 has a recess 81 configured to receive the front part 4’ of the first gate 4, and the first gate 4 has a recess configured to receive the front part 3’ of the second gate 3. The recess 81 is adapted to receive the entire front part 4’ of the first gate 4, or part of the front part 4’ of the first gate 4, when the gate assembly is in the closed position, as illustrated in Fig. 8. The recess of the first gate 4 is designed equivalently as the recess 81 of the second gate 3. Providing a recess in each of the gates 3 and 4 enables a very compact design of the gate assembly, and thus allowing a more compact overall device.

The recess 81 comprises a first side wall 83 and a second side wall 84. The first and second side walls 83 and 84 are configured to guide a first side wall 4a and a second side wall 4b of the front part 4’ of the first gate 4 during the movement of the gate assembly from the open position to the closed position. The recess of the first valve may have equivalent side walls to guide side walls of the front part 3’ of the second gate 3. This assists the gate assembly in achieving a clean cut and to perform well also in difficult operating conditions, for example if the device has to cut a tool joint, since each of the gates 3 and 4 will have additional support during the movement from the other gate.

The recess 81 may further comprise a rear wall 85, where the rear wall 85 is configured to abut a front wall 4c of the front part 4’ of the first gate 4. The rear wall 85 follows a curved path in an imaginary plane perpendicular to an imaginary axis extending longitudinally through the hole 5, 6, i.e. an axis extending along the throughbore 2. The recess of the first gate 4 may have an equivalent a rear wall configured to abut a front wall 3c of the front part 3’ of the second gate 3. The rear wall of the first gate 4 may also follow a curved path, equivalently as for the second gate 3. This allows a compact gate assembly, while maintaining a high structural strength of the front parts 3’ and 4’ (particularly around the hole 5 and 6) and of the rear parts 3” and 4”. The curved path may have a semi-circular shape.

The front wall 3c of the second gate 3 and the front wall 4c of the first gate 4 equivalently follow a curved path in the imaginary plane perpendicular to an imaginary axis extending through the hole. This path may also be semicircular.

As can be seen in Figs 7-9, the second gate 3 comprises a seal 90 and the first gate 4 comprises a seal 91. The seal 90 is provided in a seal groove on the second gate 3 and the seal 91 is provided in a seal groove on the first gate 4. The seal groove extends in a continuous manner from a front end 3d of the back part 3” of the second gate 3, across a top side 3f of the second gate 3, and to the front end 3e on the other side of the second gate 3. The seal 91 is arranged equivalently on the first gate 4. The seals 90 and 91 are arranged to provide a substantially fluid-tight seal between the housing 1 and the first and second gates when the gates 3 and 4 are in the closed position.

The seals are preferably non-metallic, for example elastomeric or polymeric seals. The seals 90 and 91 each comprise side packer seals 90a, 90b, 91a and 91b. The seals 90 and 91 are energized by means of the side packer seals upon the first and second gates reaching the closed position. In that position, the side packer seals 90a and 91a come together and the side packer seals 90b and 91b come together. The side packer seals thus seal against each other and energize all seals. A seal groove 99 (see Figs 9b-d) is provided on at least one of the gates 3 or 4 (in this embodiment, on the first gate 4), the seal groove 99 having a gate seal (not shown in the figures but arranged in the seal groove 99) configured to seal between the gates 3 and 4 when the gates 3 and 4 are in the closed position. The seal groove 99 extends towards the sides of the first gate 4 such that the gate seal is in communication with the side packer seals 90a, 90b, 91a and 91 b. The seal groove 99 is preferably on the underside of the upper gate (in this embodiment, first gate 4), to engage with an upwards-facing surface of the lower gate (in this embodiment, second gate 3). This avoids a cut item, such as a pipe end 21a (see Fig. 13) whose weight is carried by the lower gate (in this embodiment, second gate 3) to damage the gate seal.

The gate seal is energized by means of the side packer seals 90a, 90b, 91a and 91b upon the first and second gates reaching the closed position: The second gate 3 comprises second side packer seals 90a and 90b and the first gate 4 comprises first side packer seals 91a and 91b, the first and second side packer seals being configured to come into contact in the closed position such as to engage each other and be pressed together, thereby energizing the seals 90 and 91 by compression. Due to the seals’ elastic properties, the side packer seals coming together will thus energize all seals. Since the seal groove 99 is in communication with the side packer seals, this will include energizing the gate seal.

The side packer seals provide a substantially fluid-tight seal between the gates 3, 4 and the housing 1, to prevent flow of fluid between the gates 3, 4 and the housing 1. The gate seal provides a substantially fluid-tight seal between the two gates 3, 4, when the gates 3, 4 are in the closed position. As a result, when the gates 3, 4 are in the closed position, fluid flow along the throughbore 2 is substantially prevented.

Providing an elastomeric seal which is energised upon closing provides the advantage that the seals are protected in the seal groove prior to engagement, thus will not be damaged by external objects. This is particularly important for the gate seal, where e.g. the cut pipe end may have sharp edges which could destroy the seal. A further advantage can be realised by providing the seal groove for the gate seal in a curved shape. This further reduces the risk that external object present in the throughbore 2 enters the seal groove and damages the seal.

Providing non-metallic seals, such as elastomeric or polymeric seals, gives improved sealing in the closed position. A particular challenge in, for example, BOPs, is that the shearing faces and surfaces are damaged during cutting. This may particularly be the case where the full weight of a drill string acts on a surface, and slides across it during closing. This may render conventional metal-to-metal seals ineffective, i.e. the device may not be able to seal the wellbore completely off in a critical situation. Non-metallic seals are significantly more tolerant to such damaged and uneven surfaces, providing more effective sealing.

Energizing of the seals only upon closing further permits the seals to be positioned in seal grooves, wherein they are protected against any object being cut in the wellbore. Upon full, or near full, closure of the device, the seals can be energized, and thus engage the relevant face to be sealed against, e.g. a housing surface or a surface on the other gate.

Forming a seal groove on a gate in a semi-circular shape prevents any cut objects from extending into the seal groove. In particular, when cutting a tubular, the cut end will be deformed into an oval, and in particular cases, a nearly flat shape. Sliding such a cut end across a surface with a seal groove may lead to it being pushed into the seal groove and thus damaging the seal. By providing a semi-circular seal groove the cut end finds support on other parts of the gate surface at any point when sliding across a seal groove.

Figure 11 illustrates further details of the rod locking apparatuses 201 and 202. (Apparatus 201 is shown, however apparatus 202 operates equivalently.) Each rod locking apparatus 201 and 202 comprises a main housing 210 having a first tubular passage 222 and a second tubular passage 223. The housing 210 is provided with a mounting attachment to attach the locking apparatus to the bonnets 103 and 104 or to the tandem actuator as illustrated in Figures 5, 6 and 1 la and described above. A wedge piston 212 is slidably provided in the housing 210. The wedge piston 212 has a front side with a wedge surface 211 which engages a back end surface 12a’ of the first piston rod 12a. The wedge piston 212 is movable between a closed position in which it substantially blocks the second tubular passage 223 and an open position in which the second tubular passage 223 is open.

In this example, the wedge piston 212 has a transverse bore forming a through passage 217 which extends from the front side to the rear side of the wedge piston 212 generally parallel to the second tubular passage 223 and, when the wedge piston 221 is in the open position, is aligned with the second tubular passage 223 so that the rod 12a may extend through the through passage 217 as shown in Figure 11b. (See also Fig. 4.) When the wedge piston 212 is in the closed position, the through passage 217 is not aligned with the second tubular passage 223, as illustrated in Figure 6.

The wedge piston 212 incorporates a series of ridges, or teeth, that mesh with grooves in a serrated locking surface arranged on the back end surface 12a’ or in the main housing 210. The design of the serrations may be according to one of the alternatives described in US 4,969,390 or any other suitable design. This may include splines, grooves, ridges, or teeth, or a combination thereof, suitable for producing a mating motion and a friction-based locking effect between the wedge piston 212 and the serrated locking surface.

Figures 12-14 illustrate further details of one embodiment. In this embodiment, the second gate 3 and the first gate 4 are shaped such that its respective hole 5 and 6 is frustoconical or has a frustoconical portion 30 and 31. The diameter of the hole 5 and 6 is larger towards the side of the gate 3 and 4 facing the housing 1 and smaller towards the side of the gate 3 and 4 adjacent to the other gate.

Optionally, the housing 1 is shaped such that the throughbore 2 has frustoconical portions 32 and 33. As can be seen in Figs 12 and 14, the housing 1 is shaped such that the throughbore 2 has two frustoconical portions 32 and 33 which are arranged such that the gates 3 and 4 are directly adjacent to and supported between the two frustoconical portions 32 and 33 of the throughbore 2.

The frustoconical portions 32 and 33 of the throughbore 2 has a larger diameter end and a smaller diameter end, and is arranged with the larger diameter end directly adjacent one of the two gates 3 and 4 and the smaller diameter end spaced from the gates 3 and 4.

Figure 12 shows this in a magnified view. In this preferred embodiment, a part of one or both holes 5 and 6 has a frusto-conical portion 30, 31, whereby the diameter of the holes 5 and/or 6 is larger towards the side facing the housing 1 compared to that facing the other gate. The frusto-conical portions 30 and 31 provide the additional advantage that more space is available for the end of the cut object, e.g. pipe ends 21a and 21b (see Fig. 13) in the hole 5 or 6 when the wellbore device is in the closed position.

Further, the throughbore 2 can be provided with frusto-conical portions 32 and/or 33 at a point interfacing the gates 3 and 4. The frusto-conical portions 32 and/or 33, on their own or in combination with the frusto-conical portions 30 and 31, provide the same advantages as those described above, i.e. allowing more space for the cut object in the holes 5 and 6 after closure of the device. Frusto-conical portions 30, 31, 32 and 33 thus provide particular advantages if there is a need to cut large-diameter objects, e.g. a casing tubular, as there will be less tendency for the cut pipe end to be deformed when present in the hole 5 or 6 during closing of the gates 3 and 4.

Fig. 13 illustrates in a schematic manner two cut ends 21a and 21b of a tubular which was present in the throughbore 2 prior to closing and has been sheared by gates 3 and 4. The cut ends of the tubular 21a and 21b are left in holes 5 and 6 when the wellbore control device is in the closed position. This eliminates the need for pipe ends 21a and 21b to be lifted, removed or subject to a “double cut”, i.e. shearing between the upper edge of hole 5 / lower edge of hole 6 and the housing 1, which would have been necessary if the gates 3 and 4 were to be driven fully into the housing 1.

This configuration may also allow the device to shear a large-diameter tubular object, such as a casing string. In this case, the pipe ends 21a and 21b will be deformed, but as in the case above, remain partly in the holes 5 and 6.

Figure 14 illustrates the area 70 interconnecting the hole 5 of gate 3 and the throughbore 2 in the closed position. (A similar area will exist for the lower gate 4.) With a circular hole 5 this area 70 will have the shape of a circle intersection, or vesica piscis. The area 70 will have a circumferential length 71. In a preferred embodiment, the frusto-conical portions 30 and 32 are arranged with an appropriate conical angle (i.e. the angle between the frusto-conical portions 30 and 32 to the vertical) such at the circumference length 71 is larger than the circumference of the largest tubular object to be sheared by the device.

As noted above, when cutting a tubular, the cut end will be deformed, generally into an oval-like shape. Arranging frusto-conical portions 30 and 32 with a conical angle large enough to give such a circumferential length 71 in a vesica piscis shaped area allows the cut end to remain in the hole 5 without the need for a double cut or further deformation of the tubular.

For example, in conventional wellbore systems the throughbore 2 may have a diameter of 18 3/4”. For cutting of object larger than 6 5/8” OD, the frusto-conical portions can form an increased circumferential length 71 which can allow for cutting and sideways storage of objects up to 14” OD. The objects will be deformed to the circumference and the available shape and space. Thus, the wellbore control device according to the invention is, unlike conventional systems, able to cut and seal with various sized tubular present in the throughbore.

Advantageously, providing conical portions in the gates and/or in the throughbore therefore allows more space for the cut object to remain in the hole after closing. Particularly, if cutting a large-diameter tubular, such as casing, the cut end may be heavily deformed, usually into an oval shape. Providing conical portions allows such a deformed end to remain in the hole without affecting the closing function of the device.

By providing frusto-conical portions of the same dimensions in both the gates and the throughbore, a substantially flush through passage can be achieved through the device, thus avoiding any snag points in the open position.

Figures 15-19 show further details of the embodiments described above.

When used in this specification and claims, the terms "comprises" and "comprising" and variations thereof mean that the specified features, steps or integers are included. The terms are not to be interpreted to exclude the presence of other features, steps or components.

The features disclosed in the foregoing description, or the following claims, or the accompanying drawings, expressed in their specific forms or in terms of a means for performing the disclosed function, or a method or process for attaining the disclosed result, as appropriate, may, separately, or in any combination of such features, be utilised for realising the invention in diverse forms thereof.

The present invention is not limited to the embodiments described herein. Reference should be had to the appended claims.

Claims (20)

1. A gate assembly having a first gate (4) and a second gate (3), the first gate (4) having a front part (4’) and a rear part (4”), the second gate (3) having a front part (3’) and a rear part (3”), a first hole (6) arranged in the front part (4’) of the first gate (4), a second hole (5) arranged in the front part (3’) of the second gate (3), the first gate (4) having a recess configured to receive the front part (3’) of the second gate (3), and the second gate (3) having a recess (81) configured to receive the front part (4’) of the first gate (4).

2. A gate assembly, wherein the recess (81) comprises a first side wall (83) and a second side wall (84), the first and second side walls (83,84) being configured to guide a first side wall (4a) and a second side wall (4b) of the front part (4’) of the first gate (4).

3. A gate assembly, wherein the recess of the first gate (4) comprises a first side wall and a second side wall, the first and second side walls being configured to guide a first side wall (3a) and a second side wall (3b) of the front part (3’) of the second gate (3).

4. A gate assembly, wherein the recess (81) comprises a rear wall (85), the rear wall (85) configured to abut a front wall (4c) of the front part (4’) of the first gate (4).

5. A gate assembly, wherein the recess of the first gate (4) comprises a rear wall, the rear wall configured to abut a front wall (3c) of the front part (3’) of the second gate (3).

6. A gate assembly, wherein the rear wall (85) follows a curved path in an imaginary plane perpendicular to an imaginary axis extending longitudinally through the hole (5,6).

7. A gate assembly, wherein the rear wall of the first gate (4) follows a curved path in an imaginary plane perpendicular to an imaginary axis extending longitudinally through the hole (5,6).

8. A gate assembly, wherein the rear wall (85) and/or the rear wall of the first gate (4) follows a semi-circular shape.

9. A gate assembly, wherein the front wall (3c) of the second gate (3) follows a curved path in the imaginary plane perpendicular to an imaginary axis extending through the hole, and/or the front wall (4c) of the first gate (4) follows a curved path in the imaginary plane perpendicular to an imaginary axis extending through the hole.

10. A gate assembly, wherein the front wall (3c) of the second gate (3) and/or the front wall (4c) of the first gate (4) follows a semi-circular shape in the imaginary plane perpendicular to an imaginary axis extending through the hole.

11 .A gate assembly, wherein the first gate (4) comprises a first seal (91) and the second gate (3) comprises a second seal (90).

12. A gate assembly, wherein the first seal (91) is provided in a seal groove on the first gate (4) and the second seal (90) is provided in a seal groove on the second gate (3).

13. A gate assembly, wherein the seal groove extends to a front end surface (3d,3e) of the back part (3”,4”) of the gate (3,4).

14. A gate assembly, wherein the seals (90,91) are arranged to provide a substantially fluid-tight seal between the housing (1) and the first and second gates (3,4).

15. A gate assembly according to the preceding claim, the seals arranged to provide a substantially fluid-tight seal between the first and second gates (3,4) when the gates (3,4) are in the closed position.

16. A gate assembly wherein the seals are non-metallic.

17. A gate assembly wherein the seals are elastomeric.

18. A gate assembly wherein the first gate (4) comprises first side packer seals (91a, 91b) and the second gate (3) comprises second side packer seals (90a,90b), the first and second side packer seals configured to be in contact in the closed position such as to energize the seals (90,91).

19. A gate assembly according to any preceding claim wherein a seal groove (99) is provided on at least one of the gates (3,4), the seal groove having a gate seal configured to seal between the gates (3,4) when the gates (3,4) are in the closed position.

20. A gate assembly according to the previous claim, wherein the gate seal is energized by means of the side packer seals (90a, 90b, 91 a,91 b) upon the first and second gates (3,4) reaching the closed position.

21 .A gate assembly wherein the seal groove (99) has a semi-circular shape.