Valve for closing pipe

Abstract

The invention provides a valve (1) for closing a pipe (2), having: a central axis X; a body (10) having an inlet (12) and an outlet (14) defining an aperture (18); a plurality of closing portions (30) for closing the apertures (18); a valve mechanism (70), a plurality of closure portions (30) movable from a first closed position (8) to a second open position (9); a valve seat (20); a plurality of first fixed pivot mounts (41) on the body (10), and wherein each closure portion (30) is pivotally mounted within the first fixed pivot mount (41); a plurality of second non-fixed pivot mounts (42) connected to the valve mechanism (70), and wherein each closure portion (30) is pivotally mounted within the second non-fixed pivot mount (42); and wherein the valve mechanism (70), and thus each second non-fixed pivot mount (42), is movable in three dimensions.

Description

Technical Field

[0001] The present invention relates to valves. More particularly, the present invention relates to a valve for closing a pipe carrying a fluid. Background Art

[0002] Valves are used to seal tubes to stop the flow of fluid therein. The fluid can be a liquid or a gas. There are many challenges in designing valves. The valve must be able to operate to open and close at the high pressures and flow rates seen in the fluid flowing in the tube. The success of the valve design is measured by how well it stops flow when the valve is in the closed, sealing position and the pressure it can withstand, as well as the degree of obstruction or reduction in flow provided by the valve compared to the cross section of the flat tube when the valve is in the open position. The ideal valve would create a perfect seal at high pressure in both flow directions when in the closed position, and allow the fluid to flow through the open valve irrotationally in the same manner as the cross section of the flat tube.

[0003] The second challenge when designing a valve is to allow the valve to move between an open position and a closed position when a pressurized fluid is held by the valve in either direction or flows at high speed in a pipe. The fluid pressure on the valve seal or closure portion can create considerable friction between the sealing surface and the valve seat or between components of the valve mechanism, which must be overcome by the actuator. High friction and high forces must be overcome to allow the valve to function, thereby requiring greater forces to actuate the valve, thereby requiring a more powerful actuator. High forces and high friction also result in high wear.

[0004] Butterfly valves are a common design for flow control in pipes and other conduits that carry fluids. They consist of a disc or valve face that rotates on an axis in a pipe body that pivots at each end. By rotating the axis 90 degrees, the disc can be moved from being oriented perpendicular to the flow in the pipe (thus blocking it) to being parallel (thus allowing flow to pass relatively unimpeded). Butterfly valves are beneficial because of their quick and simple rotational operation, light weight, compact length, and simple operation.

[0005] However, because the disk remains in the center of the pipe flow, thereby partially blocking the pipe, the flow efficiency through the valve is not as high as that of a valve with full bore unobstructed flow (such as a ball valve) even when fully open. However, ball valves raise their own problems discussed below. Keeping the disk in the center of the flow when open also makes it susceptible to erosion from particulate matter in the flow. While the basic concept of a butterfly valve is simple, the details of how a tight seal is achieved between the rotating disk and the fixed seat in the valve body when closed are more complex. There are three different types of butterfly valves, all of which take different approaches to achieving this seal between the disk and the seat. These butterfly valves may be referred to as zero offset, double offset, and triple offset butterfly valves.

[0006] The zero offset butterfly valve as shown in FIG. 1 and disclosed in US1248926A has a valve seat S1, a closing disc / valve face VF1 mounted on an axis VSA1 centered in the middle of the valve seat S1, about which the valve disc VF1 rotates. This means that the force generated by the fluid pressure on the valve when closed acts directly through the axis centerline at its pressure center CP1.1, so that no resultant torque is generated on the axis. In this way, the zero offset valve is pressure balanced because there is no net force due to fluid pressure that prevents or helps the operation of the valve. However, in the sealing area at 1.01-1.04, significant forces and torques are caused due to friction / deformation forces between the sealing surfaces of the disc and the seat. In order for a disc with limited thickness to operate from a zero offset configuration, the disc must interfere / interact with the seat to provide a seal. Therefore, a zero offset valve must employ a deformable or soft (usually rubber) seat and / or disc sealing surface. Therefore, the seat and disc are subject to significant wear due to interaction in operation and require significant torque to operate, while the soft sealing material makes the valve unsuitable for fireproof applications.

[0007] The double offset butterfly valve shown in FIG. 2 and disclosed in GB302526A is also known as an eccentric, double eccentric or high performance butterfly valve. They are developed to overcome the defects of zero offset valves. In the double offset valve, the position of the vertical axis VSA2 is offset O1.1 behind the transverse plane C of the seat centerline DCL, and offset O2.1 to the side of the valve centerline VCL. The seat is conical. This means that when the shaft rotates, the disk moves out of the conical profile seat S2 in a cam-like motion, where there is potentially no friction interaction or wear between the disk and the seat. However, no interference can only be achieved when VSA2 is in the area Q specified by the dotted line portion, which is defined by the boundary lines 2.01 and 2.02, where the seat clearance angles SCA1.1 and SCA2.1 formed between 2.01, 2.02 and the conical seat profile must be greater than 90 degrees. This gap when opened allows the use of fireproof metal seals and extends component life. However, to achieve this, the shaft must be offset a considerable distance from the center of the tube (i.e. the location where the fluid pressure acts on the disc CP1.2). This means that the valve is no longer pressure balanced and, although friction is now minimized, the moment generated by the offset (moment arm) O2.1 between the shaft and the pressure center CP1.2 produces significant torque. In addition, when the valve face VF2 is opened to position VF2O, the structure connecting the disc to the offset shaft significantly impedes flow through the valve. Therefore, most double offset valves still involve interaction between the seat and the disc (usually a spring-loaded metal seal is used to facilitate this) because the torque and flow losses caused by the offset required to completely eliminate the seat / disc interaction are too great.

[0008] The triple offset butterfly valve shown in FIG. 3 and disclosed in US Pat. No. 3,275,289 A was invented to eliminate all friction seal interactions without excessive operating torque and overly restricted pipe flow. Like the double offset valve, this valve also offsets the shaft behind the disc O1.2 and to the side of the pipe centerline O2.2, but these offsets O1.2, O2.2 are reduced by angling the centerline of the conical profile of the seat relative to the center axis X of the pipe (the "third" offset). Although the triple offset valve successfully minimizes operating seat wear, thereby allowing the use of metal-to-metal seals, they are not pressure balanced and therefore still require significant torque to open. In addition, because there is no physical interaction between the disc and the seat, a force must be applied in operation to form a seal (these are so-called torque seat valves). Although fluid pressure can contribute to the sealing effectiveness of the valve when the flow is in a preferred orientation, its effectiveness is limited by the oblique angle formed by the face and the offset conical seat. Similarly, the seating force from the input torque is limited by the small contact angle (SCA - 90 degrees) between the seat and the disc, which is required to minimize shaft deflection and the resulting pressure torque. In addition, although reduced compared to the double offset valve, the VF3 still significantly restricts flow through the valve when the VF3O is open.

[0009] Alternative types of valves are known that do achieve unrestricted flow through the valve when open. Such valves include gate valves or ball valves. Gate valves can be pressure balanced (flat plate and parallel slide types), but these gate valves have significant friction and wear between the face and seat during operation. Wedge and expansion gate valves eliminate this friction but are no longer pressure balanced. In addition, the linear motion of the gate valve may inhibit rapid actuation while increasing the challenge of stem sealing. Ball valves combine a pressure balanced design with the desired quarter-turn (90 degree) actuation, but friction occurs between the valve face (ball) and the valve seat during operation. Summary of the invention

[0010] Thus, the present invention provides a valve that combines three desirable features that have not previously been achieved together in other valve designs:

[0011] 1. Non-frictional placement: Similar to an offset butterfly valve, it minimizes friction between the seat surface and the tube sealing surface of the valve disc, reducing the operating torque required to bring the sealing surfaces together and allowing the use of long-life, fire-resistant, metal-to-metal seals.

[0012] 2. Pressure balanced arrangement when closed: When the pressure differential across the valve is maximum (closed position), there is no fluid pressure contribution to the initial actuation force / torque.

[0013] 3. Provides a clear aperture when the valve is in the open position, allowing full bore flow without a valve disc or face remaining in the flow path. This provides an unobstructed full bore flow valve, similar to a ball valve or gate valve.

[0014] Aspects and / or embodiments seek to provide a valve for closing a pipe, the valve having: a central axis X; a body having an inlet and an outlet; a body wall defining an aperture extending between the inlet and the outlet; a plurality of closure parts for closing the aperture; a valve mechanism connectable to an actuator, the plurality of closure parts being movable by the valve mechanism from a first closed position when the valve is closed to a second open position when the valve is open, the body wall comprising a valve seat for receiving the plurality of closure parts, each closure part having a first end and a second end and an intermediate portion for sealing the aperture, the intermediate portion comprising a valve sealing surface for sealing to another closure part and a pipe sealing surface for sealing to the pipe. The valve may also include a plurality of first fixed pivot mounts on the body, and wherein the first end of each closure part is pivotally mounted in the first fixed pivot mount. The valve may also include a plurality of second non-fixed pivot mounts connected to the valve mechanism, and wherein the second end of each closure part is pivotally mounted in the second non-fixed pivot mount, and wherein the valve mechanism and therefore each second non-fixed pivot mount may be movable in three dimensions between the first closed position and the second open position.

[0015] Preferably, the valve mechanism is configured to move the plurality of second non-fixed pivot mounts along and circumferentially about axis X to move the closure portion radially, axially and circumferentially relative to axis X from a first closed position to a second open position.

[0016] Preferably, each first fixed pivot mount comprises a first pivot having a first axis of rotation α and a second pivot having a second axis of rotation β, and each second non-fixed pivot mount comprises a third pivot freely rotating about all three axes.

[0017] Preferably, each first fixed pivot mount comprises a third pivot freely rotating about all three axes, and each second non-fixed pivot mount comprises a first pivot having a first axis of rotation α and a second pivot having a second axis of rotation β.

[0018] Preferably, the valve seat comprises a circumferentially extending conical valve seat surface.The conical valve seat advantageously provides sealing and allows low friction or zero friction engagement of the valve seat surface with the pipe sealing surface of the closure portion.

[0019] Preferably, the valve comprises a transverse plane C perpendicular to said axis X and, for each closure part, a longitudinal plane A coinciding with the axis X and a first offset plane A' offset by a distance D1 from said longitudinal plane A, wherein the first axis α coincides with the first plane A'. The orientation of the axis α advantageously provides a low friction or zero friction engagement of the valve seat surface with the pipe sealing surface without interference, and a low friction or zero friction engagement of the corresponding valve sealing surfaces of the closure parts without interference.

[0020] Preferably, wherein each closed portion comprises a first pressure centre point P1 when the closed portions are viewed in said transverse plane C with the valve in the closed position; and wherein the first plane A' is located on said first pressure centre point P1.

[0021] When the first plane A' coincides with the pressure center P1 of the corresponding closed portion, the valve is advantageously in a pressure balanced state when in the closed position. Thus, the valve can be opened and closed with low force even when there is high pressure flow in the pipe.

[0022] Preferably, wherein, when in the closed position, each closing portion comprises a second pressure centre point P2 when viewed in the longitudinal plane A, and a third pressure centre point P3 when viewed in the lateral plane B; and wherein the pressure centre point P2 of each closing portion coincides with the respective axis α when viewed in its respective longitudinal plane A. Thereby, a pressure balance state is advantageously maintained when the valve is in the closed position.

[0023] Preferably, wherein, when in the closed position, each closure portion comprises a first pressure centre point P1 when viewed in the transverse plane C, a second pressure centre point P2 when viewed in the longitudinal plane A, and a third pressure centre point P3 when viewed in the lateral plane B, each pressure centre point P1, P2, P3 having an associated force and an associated moment M1, M2 and M3, respectively, exerted on the respective closure portion; and wherein, when viewed in the transverse plane C, each pressure centre point P1 is offset from the respective axis α, and when viewed in the respective longitudinal plane A, each pressure centre point P2 is offset from the respective axis α, such that the associated moments M1, M2 act in opposite directions such that they cancel, resulting in a zero combined moment. Advantageously, a pressure balance state is thereby maintained when the valve is in the closed position.

[0024] Preferably, wherein, when in the closed position, the third pivot axis of the respective closure part lies in longitudinal plane A. Longitudinal plane A is perpendicular to the second axis β, so the moment exerted by the force at the pressure centre point P3 has no effect and the valve is pressure balanced in the closed position.

[0025] Preferably, for each closing portion, the valve also comprises a lateral plane B coinciding with the axis X and perpendicular to the longitudinal plane A;

[0026] wherein, when the valve is in the closed position, the second axis β coincides with a second offset plane B' offset by a distance D2 from the lateral plane B. The orientation of each respective plane B, and hence each plane B' perpendicular to the respective plane A and hence the axis of rotation β of the second pivot, ensures that initial movement of the closure portion upon opening the valve is primarily or limited to rotation about the first pivot, thereby advantageously allowing low friction or frictionless engagement of each sealing surface without the aforementioned interference, while allowing the closure portion to rotate away from the aperture in the open position.

[0027] Preferably, for each closing portion, the valve further comprises a lateral plane B coinciding with the axis X and perpendicular to the longitudinal plane A, and each pipe sealing surface has a first end on the side of the longitudinal plane A having the pressure center of the corresponding closing portion 30 and a second end on the side of the longitudinal plane A opposite to the first end;

[0028] wherein a first axis of rotation α of the respective enclosed portion intersects a lateral plane B associated with said respective enclosed portion in a region R delimited by the first line F and the second line G;

[0029] a first line F extending along said lateral plane B, perpendicular to the surface of the seat sealing face at a point where the valve seat intersects said lateral plane B on a first side of the longitudinal plane A; and

[0030] The second line G extends along said lateral plane B, perpendicular to a line projected from the valve seat surface onto the lateral plane B at the point where the second end is located when in the closed position.

[0031] The location of the axis α advantageously provides the three benefits mentioned above.

[0032] Preferably, the valve seat has a first end close to the valve mechanism and a second end away from the valve mechanism, and the transverse plane C coincides with the second end of the valve seat; and

[0033] The second axis β intersects the longitudinal plane A of the respective closing part on the side of the plane C opposite to the valve mechanism. Advantageously it is ensured that there is no interference between the closing parts when the valve is open.

[0034] Preferably, wherein the third line H extends along the longitudinal plane A of the corresponding enclosed portion, perpendicular to the valve seat surface at the point where the valve seat intersects the longitudinal plane A; and

[0035] The second axis β intersects the longitudinal plane A in a region S defined by the transverse plane C and the third line H. Advantageously, no interference is provided between the closure portion and the valve seat surface when engaged.

[0036] Preferably, wherein the second non-fixed pivot mount is located radially outwardly of the seat from the axis X. Advantageously, the closure portion is caused to rotate away from the aperture when in the open position, thereby allowing full aperture flow.

[0037] Preferably, wherein the third pivot comprises a ball joint. This advantageously provides rotation on three axes in a compact arrangement.

[0038] Preferably, wherein each first pivot is connected to its corresponding second pivot by a connecting rod;

[0039] The link is connected to the body or valve mechanism by a first pivot, and the link is connected to the corresponding closure portion by a second pivot.

[0040] Preferably, the first axis α and the second axis β intersect.

[0041] Preferably, wherein the connecting rod includes a first end and a second end separated by a length L; and the first pivot is located at the first end of the connecting rod and the second pivot is located at the second end of the connecting rod, so that the first axis α is offset from the second axis β by the length L. The connecting rod advantageously allows the first pivot and the second pivot to be offset to allow positioning inside the tapered seat surface. In particular, when the regions S and R do not overlap, the offset provided by the length L provides a low friction engagement or a frictionless engagement between the corresponding valve seat surface and the valve and pipe sealing surface.

[0042] Preferably, there are n closure portions, each of which includes one or more valve sealing surfaces, including a first valve sealing surface extending radially from the axis X toward the first fixed pivot mount and a second valve sealing surface extending radially from the axis X to the first valve sealing surface at an angle of 360 / n. The angle of the first valve sealing surface to the second valve sealing surface at the axis X allows the closure portion to be embedded in the valve seat and provide a seal.

[0043] Preferably, wherein one or more valve sealing surfaces are parallel to the axis X. Advantageously, in an embodiment with two enclosing parts, the valve sealing surfaces are allowed to come together without friction or interference.

[0044] Preferably, wherein the tube sealing surface is tapered to match the valve seat surface. The matching taper angles advantageously provide sealing.

[0045] Preferably, wherein a portion of each first valve sealing surface proximate to the valve seat extends away from the longitudinal plane A on a side of the longitudinal plane A opposite to the pressure center P. Preferably, wherein a portion of the second valve sealing surface proximate to the valve seat extends away from the longitudinal plane A on the same side of the longitudinal plane A as the pressure center P. The complementary arrangement of the first and second valve sealing surfaces extending away from either side of their respective planes A advantageously provides a clear aperture and no interference between the closure portion and the valve seat when the closure portion is in the open position.

[0046] Preferably, the valve seat surface is divided into one or more flat valve seat portions.

[0047] Preferably, the valve seat surface makes an angle ε of less than 90 degrees with the axis X. This allows low or no friction between the sealing surfaces when the valve is closed and opened.

[0048] Preferably, wherein the one or more valve sealing surfaces are offset in a first direction along the axis X and connected to the tube sealing surface via an intermediate sealing surface to form a continuous seal around the closure portion.

[0049] Preferably, wherein the valve sealing surface includes a chamfered lower edge for providing clearance between the plurality of closure portions when moving from a first closed position to a second open position. The chamfered lower edge and the corresponding offset position of the seal provide clearance for movement of the closure portions while maintaining the valve sealing surface meeting with no interference and low friction or no friction.

[0050] Preferably, wherein the valve mechanism comprises a control ring comprising a plurality of second non-fixed pivot mounts for connecting the plurality of closure portions to the control ring. The control ring advantageously maintains the relative positions of the second non-fixed pivot mounts and comprises a central aperture that does not interfere with the central aperture of the valve.

[0051] Preferably, the body comprises a control ring guide for limiting the movement of the control ring to translation along the axis X and rotation about the axis X.

[0052] Preferably, wherein the control ring comprises engagement means for engaging the actuator.

[0053] Preferably, the body wall is continuous with no apertures other than the inlet and outlet.

[0054] Preferably, the valve further comprises one or more actuators for moving the control ring.

[0055] The continuous body wall advantageously eliminates possible failure points of the seal.

[0056] Preferably, wherein one or more actuators include a magnetic coupling. The magnetic coupling enables drive from the actuator to pass through the continuous body wall to drive the valve mechanism.

[0057] Preferably, wherein the inlet and outlet comprise flanged, threaded or welded pipe connections. Alternatively, any stable, fluid tight connection may be used. The pipe connections provide a sealed connection between the inlet and outlet of the valve and the pipe to which it is fitted. BRIEF DESCRIPTION OF THE DRAWINGS

[0058] Embodiments will now be described, by way of example only, and with reference to the accompanying drawings having the same reference numerals, in which:

[0059] Figure 1a A prior art zero offset butterfly valve is shown, particularly in cross-section, with details showing the required interference between the valve face / disc and the seat; wherein the dashed lines show the face / disc in an open position;

[0060] Figure 1b yes Figure 1a A front view of a valve;

[0061] Figure 2a A cross-sectional view of a prior art double offset butterfly valve is shown, wherein the dashed area shows a suitable position for the axis line to avoid contact between the valve face / disc and the valve seat when open; wherein the dashed line shows the face / disc in the open position;

[0062] Figure 2b Shows Figure 2a A front view of a valve;

[0063] Figure 3a A cross-sectional view of a prior art triple offset butterfly valve is shown, wherein the dashed area shows a suitable position for the axis line to avoid contact between the valve face / disc and the valve seat when open; the dashed line shows the valve face / disc in the open position;

[0064] Figure 3b Shows Figure 3a A front view of a valve;

[0065] Figure 4a and Figure 4b A valve according to the invention is shown in a closed position; Figure 4a A representation of the key mechanisms forming the disclosed embodiments is shown, with the body removed to provide a clear view; Figure 4b Shows Figure 4a A valve further comprising a quarter portion of a valve body having a flanged pipe connection as an example of how the valve may be engaged with a coupling piping system; a magnetic coupling and an actuator (segment);

[0066] Figure 5a and Figure 5b Shown in open position Figure 4a and Figure 4b valve; Figure 5b Shows Figure 5a A valve further comprising a quarter portion of a valve body having a flanged pipe connection as an example of how the valve may be engaged with a coupling piping system; a magnetic coupling and an actuator (segment);

[0067] Figure 6a and Figure 6b A schematic conceptual diagram of a pressure balancing valve according to the present invention is shown;

[0068] Figure 7a and Figure 7b A schematic conceptual diagram of a pressure balancing valve by dividing the valve face / disc into multiple closed sections is shown;

[0069] Figure 8a and Figure 8b A schematic conceptual diagram of a pressure balancing valve according to the present invention is shown;

[0070] FIG. 9 shows the closed position of the present invention. Figure 4a and Figure 4b The valve, Figure 9a A pictorial view is shown in; Figure 9b A rear view is shown in FIG. Fig.9c A top cross-sectional view is shown in FIG. Figure 9d A pictorial view is shown in; Fig.9e A front view is shown in FIG. Figure 9f A side cross-sectional view is shown in FIG.

[0071] Figure 10 shows Figure 4a and Figure 4b of the invention with the control ring rotated 3% towards the open position and including details showing the clearances between the faces and between the faces and the seat when open, Fig.10a A rear view is shown in FIG. Fig.10b A pictorial view is shown in; Fig.10c A top cross-sectional view is shown in FIG.

[0072] FIG. 11 shows the control ring in a position where it is rotated 50% toward the open position. Figure 4a and Figure 4b The valve of the present invention, Fig.11a A rear view is shown in FIG. Fig.11b A pictorial view is shown in;

[0073] FIG. 12 shows a schematic diagram of an embodiment of a valve according to the present invention, showing possible positions of the first pivot and the second pivot and the third pivot; and

[0074] FIG. 13 shows an alternative embodiment of a valve according to the invention having eight closing portions, wherein the axes α and β intersect; Fig.13a A cross-sectional side view is shown in FIG. Fig.13b A front view is shown in FIG. Fig.13c A pictorial view is shown in; Fig.13d A pictorial view of a position between the closed position and the open position is shown in ; a pictorial view of the open position is shown in 13e. DETAILED DESCRIPTION

[0075] refer to Figure 4a and Figure 4b (together with FIG. 4 ), a preferred embodiment of the present invention will now be described. Figure 4a A valve 1 for closing a pipe is shown, which has a central axis X. The valve comprises a plurality of closing portions 30, a valve mechanism 70, a body 10 comprising a body wall 16, a valve seat 20, an inlet 12 and an outlet 14. The body wall 16, the inlet 12 and the outlet 14 are arranged at Figure 4a 2, so that the closure portion 30, the valve seat 20 and the valve mechanism 70 are visible. Figure 4a In addition to the features shown, Figure 4b An inlet 12 and an outlet 14 are shown, each having a bore and a bore center, the bore center including a portion of an aperture 18 extending through a valve seat 20 between the inlet 12 and the outlet 14. A central axis X joins the bore centers of the inlet 12 and the outlet 14. The body wall 16 including the valve seat 20 defines a portion of the aperture 18 extending from the inlet 12 to the outlet 14 of the valve 1. Preferably, the aperture 18 is the only aperture at the valve seat 20. The valve 1 is in the closed position 8, wherein the plurality of closing portions 30 close the aperture 18 at the valve seat 20. Figure 4b Shows that Figure 4a A quarter section view of the complete valve in the same position with the addition of the body wall 16, the inlet 12, the outlet 14 and the valve mechanism 70. The closure portion 30 and the valve mechanism are movable from a closed position 8 in which they block flow through the valve 1 to an open position 9 in which the closure portion 30 is away from the aperture 18 and thereby away from the flow stream passing downwardly along said aperture 18. Figure 4a and Figure 4b Both include arrows labeled MO which illustrate the movement of components when the valve moves from a closed position 8 to an open position 9 .

[0076] Figure 4a An embodiment of a valve 1 is shown having two closing portions 30, a valve seat 20 of a body 10 and a portion of a valve mechanism 70. Each closing portion 30 has a first end 31 and a second end 32 and a middle portion 33. When the valve 1 is in the closed position 8, the middle portion 33 of the closing portion 30 closes or seals the aperture 18 defined by the valve seat 20 of the body 10.

[0077] The valve 1 includes a plurality of first fixed pivot mountings 41 on the body 10. Each closure portion 30 is pivotally mounted to the valve body 10 at its respective first end 31 by a first fixed pivot mounting 41 ( Figure 4a Each first fixed pivot mount 41 is fixed in that it is attached to the body 10 of the valve 1, which can be considered fixed, and therefore at least a portion of the fixed pivot mount 41 is constrained so that it cannot translate in any direction relative to the body 10 when the valve 1 is actuated so that the valve 1 and thus the closure portion 30 moves from the first closed position 8 to the second open position 9 or from the second open position 9 to the closed position 8.

[0078] The valve 1 comprises a plurality of second non-fixed pivot mounts 42 connected to the valve mechanism 70. Each second end 32 of the closure portion 30 is pivotally mounted to the valve mechanism 70 at a second non-fixed pivot mount 42. Each second non-fixed pivot mount 42 is non-fixed in that each second non-fixed pivot mount 42 and thus the second end 32 of the closure portion 30 and the portion of the valve mechanism 70 to which the closure portion 30 is connected by the second non-fixed pivot mount 42 can translate in three dimensions along a path controlled by the valve mechanism 70 between a first closed position 8 and a second open position 9. Figure 4a As can be seen in the figure, the valve mechanism 70 includes a control ring 72, and a plurality of second non-fixed pivot mounts 42 pivotally connect the second end 32 of each closure portion 30 to the control ring 72. In a preferred embodiment, the control ring 72 includes a plurality of second non-fixed pivot mounts 42. In this embodiment, all second ends 32 of the closure portion 30 are coupled to the control ring 72 and constrained to move together. The control ring 72 is constrained by the control ring guide 76 to move axially along the axis X and rotate about the axis X, thereby causing the second non-fixed pivots 42 to move axially along the axis X and rotate circumferentially about the axis X. This causes the closure portion 30 to move radially, axially and circumferentially about the axis X from the first closed position 8 to the second open position 9. Therefore, the valve mechanism 70 and therefore each second non-fixed pivot mount 42 can move in three dimensions between the first closed position 8 and the second open position 9.

[0079] The valve mechanism 70 may be connected to an actuator 80 via an engagement device 74 so as to move the valve mechanism 70 and thereby the closure portion 30 from the closed position 8 to the open position 9. The engagement device 74 may be included as part of the control ring 72, and the actuator 80 may be used to rotate the control ring 72 to open or close the valve 1. The valve may include the actuator 80. The actuator 80 may include one or more electric, hydraulic, pneumatic or other suitable actuators 80. In a preferred embodiment, the engagement device 74 and / or the actuator 80 include a magnetic coupling 82. If the magnetic coupling 82 is present, the body wall may be continuous without apertures except for the inlet 12 or the outlet 14, thereby reducing the number of seals compared to the prior art.

[0080] Each first fixed pivot mount 41 includes a first pivot 51 having a first rotation axis α and a second pivot 52 having a second rotation axis β. Each first pivot 51 and the second pivot 52 are coupled by a link 60. The link has a first end 61 and a second end 62 separated by a length L. The first end 61 of the link 60 is connected to the body 10 via the first pivot 51 of the first fixed pivot mount 41, and the second end 62 of the link 60 is attached to the first end 31 of the closure portion 30 via the second pivot 52, whereby the first rotation axis α and the second rotation axis β are separated by a length L. When in the closed position, each link 60 can axially, radially or circumferentially offset the first pivot 51 from the second pivot 52 of the corresponding first fixed pivot mount 41.

[0081] Each second pivot mount 42 includes a third pivot 53 that is free to rotate in all three axes. Figure 4a In the preferred embodiment, the third pivot 53 is a ball joint, but other suitable joints may be used.

[0082] Figure 4b The same embodiment of the valve 1 of the invention is shown, with the addition of further parts of the body 10. An inlet 12 and an outlet 14 can be seen. Each of the inlet and outlet comprises a flanged pipe connection 15. Figure 4b Also included are the electric motor actuator 80 , magnetic coupling 82 , control ring guide 74 , and engagement device 76 , which are depicted with one quarter removed.

[0083] Figure 5a and Figure 5b (together as FIG. 5) respectively show Figure 4a and Figure 4b Identical components, wherein the valve 1 and thus the closure part 30 and the valve member 70 are in the open position 9 . Figure 5a and Figure 5b Both include an arrow labeled MC which illustrates the movement of components when the valve moves from an open position 9 to a closed position 8 .

[0084] Figure 5a An intermediate portion 33 of the closure portions 30 is shown, including a tube sealing surface 40 for sealing each closure portion 30 to the valve seat 20 . Figure 5b The middle portion 33 of the closure portion 30 is shown, including a first valve sealing surface 38 for sealing each closure portion 30 to another closure portion 30. The valve sealing surface 38 of each closure portion 30 is vertical and parallel to the axis X to allow sealing with the valve sealing surface 38 of another closure portion 30. The valve seat 20 is also shown as including a radially extending conical valve seat surface 22. The tube sealing surface 40 of each closure portion 30 is conical to match the conical valve seat surface 22 to provide a seal. In a preferred embodiment, the valve seat surface 22 is at an angle ε less than 90 degrees with the X axis, and in another embodiment, the valve seat surface 22 is at an angle less than 88 degrees with the X axis.

[0085] In order to move between the closed position 8 shown in FIG. 4 and the open position shown in FIG. 5 , the valve mechanism 70 has caused the control ring 72 to translate along the axis X and rotate about the axis X in the direction of the arrow MO in FIG. 4 . The plurality of closure portions 30 have been moved by the valve mechanism 70 from a first closed position 8 when the valve is closed to a second open position 9 when the valve is open. Thus, the closure portions 30 extending across the aperture 18 in the closed position 8 are moved radially and axially relative to the axis X and circumferentially about the axis X from the first closed position 8 to the second open position 9 in which the first end 31 and the second end 32 of each closure portion 30 are axially disposed along the same side of the aperture 18. In the preferred embodiment shown, the rotation of the control ring of the valve mechanism is greater than 170 degrees, and in alternative embodiments may be between 60 and 180 degrees. Thus, the aperture 18 is free of obstruction, thereby allowing the fluid to flow freely through the valve 1 in the open position 9.

[0086] It should be understood that although the embodiment shown in Figures 4 and 5 includes two closure portions 30, any number of closure portions 30 may be used in the present invention. The connecting rod 60 is shown to have a length L between the first end 61 and the second end 62, however in alternative embodiments, the length L may be reduced or approach zero, and the first axis of rotation α and the second axis of rotation β may intersect. In alternative embodiments, the first fixed pivot mounting 41 may include a third pivot 53, and the second non-fixed pivot mounting 42 may include a first pivot 51, a second pivot 52 and a connecting rod 60 having the same function. A flanged pipe connector 15 is shown, but the skilled person will understand that a flanged, threaded, welded or other suitable pipe connector 15 may be used. Although the terms inlet 12 and outlet 14 are used to indicate the points at which fluid enters and leaves the valve 1, it should be understood that the valve is bidirectional and the terms inlet 12 and outlet 14 are interchangeable depending on the direction of fluid flow. In some embodiments, in addition to the apertures 18, there may be bypass apertures in the body 10 for allowing a controlled amount of flow around the seat 20 when the valve 1 is in the closed position 8. In the preferred embodiment shown in Figures 4 and 5 with two closure portions 30, at least a portion of the valve sealing surface 38 of each closure portion is parallel to the axis X when in the closed position 8. In alternative embodiments with more than two closure portions, the valve sealing surfaces 38 may be at an angle to the axis X, since the valve sealing surfaces will move axially in opposite directions when the valve is opened. Although the preferred embodiment has a conical valve seat 20 with a single conical valve sealing surface 22, any contoured valve seat may be used, such as a hexagonal or octagonal shape instead of a circle.

[0087] refer to Figure 6a and Figure 6b (together with FIG. 6 ), a schematic diagram of the invention will now be described to illustrate the orientation and location of the features of the valve 1 . Figure 6a A cross-sectional view is shown that passes through the valve seat 20 and the middle portion 33 of the pair of closing portions 30 , which is perpendicular to the valve sealing surface 40 of the closing portion 30 at the center axis X. Figure 6b The diagram shows a view along the axis X from the side of the valve seat 20 opposite to the valve mechanism 70. Figure 6a The arrangement of components.

[0088] For each closing portion 30, the valve 1 comprises a longitudinal plane A and a lateral plane B. Each longitudinal plane A coincides with the axis X and the longitudinal planes A may be equally spaced radially around the axis X. Each lateral plane B coincides with the axis X and is perpendicular to the longitudinal plane A of the corresponding closing portion 30. Therefore, the planes B may also be equally spaced around the axis X. The longitudinal planes A and the lateral planes B of the two closing portions 30 may be equally spaced radially around the axis X. Figure 6bThe opposite end is seen in FIG. 2 , however, the two planes A coincide and the two planes B coincide, because there are two closed portions 30, so the two planes A and the two planes B are 180 degrees from each other. The valve also has a transverse plane C perpendicular to the axis X. The valve seat 20 has a first side 26 close to the valve mechanism 70 and a second side 28 away from the valve mechanism 70. The transverse plane C can be located on the second side 28 of the valve seat. Figure 6a The cross section is taken at plane B.

[0089] FIG6 shows possible positions of the axis α. The axis α of the first pivot 51 associated with a particular closing portion 30 coincides with a first offset plane A' offset from plane A by a distance D1. Also shown is a pressure center point P1 at the center of the pressure exerted by the fluid in the tube on each closing portion 30 when viewed in a transverse plane C. The pressure center P1 may be located at the centroid of the area presented to the fluid in the transverse plane C by the closing portion 30 when in the closed position 8. Figure 6a In the embodiment, the valve seat is located on the transverse plane C.

[0090] The distance D1 can be used to control whether the valve is forced to open by the pressure of the fluid flowing in the pipe, forced to close by the pressure of the fluid in the pipe, or whether the valve is pressure balanced. In the preferred arrangement shown in Figure 6, the distance D1 is equal to the distance from the longitudinal plane A to the pressure center, so the pressure center coincides with the first offset plane A' and coincides with the axis α. Therefore, there is no lever arm and there is no moment applied to the closed part 30 by the pressure of the fluid. If the distance D1 is greater than or less than the distance between the pressure center point P1 and the plane A, the force from the pressure center P1 will no longer act through the axis α, and the closed part 30 will act as a lever arm, and the fluid will apply a moment around the axis α. If the distance D1 is greater than the distance between the plane A and the pressure center P1, the valve will be forced to close, and if the distance D1 is less than the distance between the plane A and the pressure center P1, the valve will be forced to open by the pressure of the fluid.

[0091] Figure 6b A tube sealing surface 40 is shown for each closing portion 30 , which has a first end 40 a on the side of the longitudinal plane A having the pressure center of the respective sealing surface and a second end 40 b on the side of the longitudinal plane A opposite the first end 40 a .

[0092] Figure 6aAn area R on the lateral plane B is shown. The axis of rotation α of the respective closing part 30 preferably intersects the lateral plane B associated with said respective closing part in the area R. The area R is bounded by a first line F and a second line G. The first line F extends along the lateral plane B, perpendicular to the surface of the seat sealing surface 22 at the point where the valve seat surface 22 intersects the lateral plane B on the first side of the longitudinal plane A. The first side of the longitudinal plane A is the side with the pressure center of the respective closing part 30. The second line G extends along the lateral plane B, perpendicular to the line projected from the valve seat surface 22 onto the lateral plane B at the point where the furthest extent of the second end 40b is located in the closed position 8. With the axis α intersecting the lateral plane B in the area R, the tube sealing surface 40 does not interfere with the valve sealing surface 22 when moving from the closed position 8 or to the closed position.

[0093] As can be seen from the schematic diagram of Figure 6, Figure 6a The lower edges 44 of the valve sealing surfaces 38 observed coincide with each other. The lower edge 44 of the valve sealing surface 38 is the edge on the side opposite to the valve mechanism 70. Therefore, if the closure parts were to rotate in the direction shown around the axis α (as they do when the valve 1 is actuated), the valve sealing surfaces 38 would interfere. This would require the valve 1 to become blocked and / or require a deformable sealing surface, resulting in high wear and inefficient sealing. Figure 7a and Figure 7b (together with FIG. 7 ) shows a pictorial view of the features included in the schematic diagram of FIG. 6 , according to the present invention, which enables the valve to be moved from the closed position 8 to the open position 9 without scratching or interfering with the various valve sealing surfaces 38 and allows the valve 1 to be opened without the tube sealing surface 40 interfering with the valve seat surface 22. Therefore, the lower edge 44 of the valve sealing surface is chamfered to prevent interference. This requires that the valve sealing surface 38 is offset in a first direction along the axis X. The first direction is toward the valve mechanism 70. In order to maintain the seal, the middle portion 33 of each closure portion 30 also includes an intermediate sealing surface 37 extending between the tube sealing surface 40 and the valve sealing surface 38 to provide a continuous sealing surface 37, 38, 39, 40 around the periphery of the closure portion 30, thereby allowing multiple closure portions 30 to create a seal within the valve seat 20 when in the closed position 8.

[0094] Thus, each enclosed portion 30 is constrained not only to move about a single axis or translate in a single plane as in the prior art, but also to rotate at one end about a first axis α and a second axis β lying in planes A' and B' that are perpendicular to each other. Although the first axis α and the second axis β do not have to be perpendicular to each other. The other end of the enclosed portion is constrained to rotate about all three axes, for example at a spherical ball joint.

[0095] Figure 8aA schematic diagram of the valve seat 20 and the two enclosing portions 30 is shown, viewed from the side of the valve 1 remote from the valve mechanism 70. The plane of the cross-sectional view of FIG. 8B is also shown; this plane is the plane A of each enclosing portion 30. A plane B of the enclosing portion is also shown, the two planes being viewed as opposite ends. Plane B' is offset from each of the respective planes B of the two enclosing portions 30 by a distance D2. The distance D2 is greater than or equal to the radius r of the valve seat surface 22 from the axis X. Preferably, the radius r is obtained at the second end 28 or the narrower end of the valve seat 20.

[0096] Figure 8b Shows Figure 8a 8 and a schematic cross-sectional view of the components shown in FIG. 8 and the position of the transverse plane C on the second side 28 of the valve seat 20 away from the valve mechanism 70. Preferably, the axis β associated with each closure portion 30 intersects the corresponding longitudinal plane A on the side of the transverse plane C away from the valve mechanism 70. The axis β may intersect the longitudinal plane A at a distance D3 from the transverse plane C, wherein D3 is greater than zero. The line H extends perpendicularly to the valve seat surface 22 away from the central axis X, thereby defining an area S on the plane A, where it is preferred that the corresponding axis β intersects the longitudinal plane A of the corresponding closure portion 30. For clarity in FIG. 8, the axis β associated with each closure portion 30 intersects the corresponding longitudinal plane A. Figure 8a The enclosed portion 30 shown on the right side is the same as that in Figure 8b The bottom portion is shown associated with a second axis β.

[0097] As can be seen in the above-mentioned Figures 4 and 5 to 8, all of which show the valve 1 and thus the closure portion 30 in the first closed position 8. The first valve sealing surface 38 of each closure portion 30 is shown to extend radially from the axis X. The embodiment shown in these figures has two closure portions 30, however, in the present invention, any number of closure portions 30 is possible. Figures 12 and 13 show embodiments of the present invention with 8 and 3 closure portions, respectively. For the embodiment of the present invention with n closure portions, the second valve sealing surface 39 will extend from the axis X to the first valve sealing surface 38 at an angle of 360 / n degrees. In the preferred embodiment of Figure 4, the first valve sealing surface 38 of each closure portion 30 extends along its respective longitudinal plane A towards the respective first fixed pivot mounting 41, however, it should be understood that in alternative embodiments, the first valve sealing surface may only extend substantially towards the first fixed pivot mounting and not coincide with the longitudinal plane A. Preferably, the closure portion 30 has valve sealing surfaces 38, 39 that are equally spaced around the central axis X. The valve sealing surfaces 38, 39 must also be engaged to provide a seal when in the closed position 8.

[0098] 4 and 5 to 8 also show an embodiment in which a portion of the first valve sealing surface 38 close to the valve seat 20 of each closure portion 30 extends away from the longitudinal plane A on the opposite side of the pressure center P1 of the corresponding closure portion 30. Correspondingly, in order to allow multiple closure portions 30 to be inlaid, each closure portion 30 includes a portion of the second valve sealing surface 39 close to the valve seat 20, which extends away from the corresponding longitudinal plane A on the same side of the longitudinal plane A as the pressure center P of the closure portion 30.

[0099] When in the open position 9, the valve 1 provides an unobstructed aperture 18 extending through the valve 1. To allow this, there is an aperture clearance cutout 46 on the middle portion 33 of each closure portion, which can be Figure 7b See on.

[0100] The movement of the present invention between the first closed position 8 and the second position 9 will now be described with reference to FIGS. 9 to 11. These figures show the valve seat 20, the closure portion 30 and the valve mechanism 70 as they move stepwise from the first closed position 8 to the second open position 9. To move from the closed position 8 to the open position 9, the second end 32 of the closure portion 30 is translated circumferentially 180 degrees around the central axis X under the control of the valve mechanism 70. The second end 32 is pivotally mounted to the control ring 72 of the valve mechanism 70 at the second non-fixed pivot mount 42. The control ring 72 is a component in the valve mechanism 70 that rotates around the axis X and translates the second end 32 circumferentially around the axis X.

[0101] Figure 9a to Figure 9f The valve 1 is shown in the closed position 8. It can be seen that the closing portion 30 extends across the aperture 18 and that the middle portion 33 of the closing portion 30 closes the aperture 18 at the valve seat 20. Fig.9c A cross-sectional view taken at lateral plane B is shown, showing the profile of the middle portion 33 of the closing part. The arrow marked MO shows the initial direction of movement of the closing part 10 when the valve 1 starts to open.

[0102] Figure 9a The positions of planes A and A' in 3 dimensions are shown. Figure 9d The positions of planes B, b' and C in 3 dimensions are shown. Fig.9e and a cross-section taken at plane A Figure 9f Planar B and B' opposite ends are shown.

[0103] While the above arrangement provides the desired movement in operation and a degree of pressure balance, FIG9 illustrates an additional constraint that may be applied to ensure that the valve 1 maintains pressure balance in the first closed position 8. The 3D geometry of the closed portion means that in addition to the forces applied at each first pressure center point P1 and the resultant lever arm generated at about the first axis α, an additional component of force must be considered. Thus, there are pressure centers and resultant forces in the remaining two directions. When the valve 1 is in the first closed position 8, the pressure center is in the first closed position 8. Figure 9f When the valve is viewed from the direction of plane A shown in FIG. Fig.9c When the valve is viewed in the direction of plane B shown, there is a third pressure center point P3. When in the closed position 8, the fluid pressure in the tube 2 generates a force acting on the closed part. Due to the 3d profile of the closed part, this force acts on each closed part at the pressure centers P1, P2 and P3 in three orthogonal directions in the viewing direction defining the pressure centers P1, P2 and P3. The force has a composite lever arm and composite moments M1, M2 and M3 from the forces at P1, P2 and P3, respectively. The moment of M1 from the pressure center P1 is balanced by the aforementioned axis α located on the first offset plane A'. When each pressure center P2 is consistent with the axis α when viewed in plane A, a pressure balance state can be maintained about M2, and when each third pivot 53 is located on the corresponding longitudinal plane A of the closed part 30, the moment from M3 is balanced. Preferably, the third pivots 53 of the opposite closed parts are aligned with a single plane passing through the axis X, wherein the plane is perpendicular to the corresponding axis β of the opposite closed part, such as the lateral plane A. Alternatively, some combination of deviations from this ideal plane causes the resultant moments to cancel, for example if P2 is moved closer to the valve seat 20 of the respective closure portion, P1 may be moved closer to the longitudinal plane A so that their contributions to the torque about the axis α remain equal and opposite.

[0104] Fig.10a 10e shows the valve 1 with the valve mechanism 70 rotated 3% towards the open position. As viewed in FIGS. 10 and 11 , the valve mechanism 70 rotates counterclockwise via the control ring 72, however, it should be noted that the present invention will work with features of the valve 1 arranged to move in the opposite direction. The initial rotation at the first pivot 51 and the second pivot 52 is almost entirely around the first axis α at the first pivot 51 as the second non-fixed pivot mount 42 translates circumferentially about an axis X that is parallel or nearly parallel to the second axis β.

[0105] Fig.10cDetailed views are included that demonstrate the clearance challenges addressed by the present invention and, in particular, the benefits of having an initial rotation only or primarily about the first pivot axis 51. In the first detailed view showing the first valve sealing surface 38, the valve sealing surface 38 is biased in a first direction along the axis X to a level or above the first pivot axis 51 to produce a zero interference and zero or low friction condition when the valve 1 begins to open. The second detailed view includes the valve seat 20 and the tube sealing surface 40. This view shows the initial movement of the tube sealing surface 40 relative to the tapered valve seat surface 22, which is the product of the intersection of the axis α with the lateral plane B in the region R as described above. Since the initial movement of the valve is essentially a rotation about the first axis α, the position of each axis α relative to the pressure center of the corresponding closure portion can be used to produce a pressure equilibrium condition when the valve is closed. The arrow labeled MO shows the initial movement direction of the closure portion 30 when the valve 1 begins to open.

[0106] As the valve mechanism 70, and in particular the control ring 72, is further rotated so that the second non-fixed pivot mount 42 and the second end of the closure portion 30 connected thereto are translated circumferentially about the axis X, the amount of rotation of each closure portion 30 about the corresponding first axis α decreases and the amount of rotation of each closure portion 30 about the second axis β increases until the mechanism is approximately 50% open.

[0107] Fig.11a and Fig.11b The valve 1 is shown with the valve mechanism 70 rotated 50% toward the open position. Again, as in FIGS. 9 and 10 , the control ring 72 of the valve mechanism 70 is further rotated, thereby causing the second non-stationary pivot mounting 42 and the second end of the closure portion 30 connected thereto to translate circumferentially about the axis X. At this point, since the translation of the second non-stationary pivot mounting 52 is parallel or nearly parallel to the second axis of rotation β of the second pivot 52, the rotation of the closure portion 30 is entirely or almost entirely about the second pivot 52 of the closure portion 30. The rotation about the second pivot 52 causes the closure portion 30 to move out of the aperture 18. Starting from approximately this point in the movement of the valve 1 from the closed position 8 to the open position 9, the rotation direction of the closure portion 30 about its respective first pivot 51 changes direction when the respective second end 32 stops moving away from the longitudinal plane A and begins to return toward the plane A.

[0108] Fig.12a to Fig.12dA schematic diagram of an embodiment with three enclosures 30 is shown. The schematic diagram shows a first end 31 of each enclosure 30 connected to a first fixed pivot mount 41 and a second end 32 of each enclosure connected to a second non-fixed pivot mount 42. The fixed pivot mount 41 is represented by a fixed symbol, which includes a triangle on top of a horizontal line with three diagonal lines from the bottom, indicating that the first fixed pivot mount 41 is not free to translate. The non-fixed pivot mount 42 is free to translate.

[0109] Fig.12a and Figure 12b An embodiment of a valve 1 is shown in a first closed position 8 and a second open position 9, respectively. One enclosed portion 30 in each image shows two axes at a first fixed pivot mount 41, indicating that the first pivot mount 41 is constrained to two axes (two rotational degrees of freedom), and at a second non-fixed pivot mount 42, the enclosed portion 30 shows a ball indicating three rotational degrees of freedom. Thus, in this arrangement, the two axes remain fixed and the ball is free to translate.

[0110] Fig.12c and Fig.12d A further embodiment of the valve 1 is shown also in a first closed position 8 and a second open position 9, respectively. One closed portion 30 in each figure shows a ball, indicating that the first pivot mount 41 is free to rotate about three rotational degrees of freedom, and two axes are shown at the second pivot mount 42, indicating that the second non-fixed pivot mount 42 is constrained to two axes (two rotational degrees of freedom). Thus, in this arrangement, the ball remains fixed and the two axes are free to translate.

[0111] It should be understood that although the schematic diagram is shown as having three enclosure portions 30, the features of the illustrative embodiments may be used with any number of enclosure portions.

[0112] Now refer to Fig.13a to Fig.13e An alternative embodiment of the valve 1 of the present invention is described. The valve 1 of Figure 13 comprises eight closing portions 30. The axes α and β are positioned as disclosed above with respect to Figures 4 to 8 and as Fig.13a 6. The seat 20 intersects as shown, and the first pivot 51 and the second pivot 52 are connected by a connecting rod 60. The seat 20 includes an outer sealing conical sealing surface 23. The outer sealing surface makes an angle ε less than 90 degrees with the axis X. The seat also includes a conical sealing surface 23 divided into a plurality of radially extending flat seat portions 24 to produce a polygonal conical seat. Preferably, the number of radially extending flat seat portions 24 is the same as the number of closure portions 30 in the valve 1.

[0113] In FIG. 17 b , the positions of the two planes A and the two planes B of the two shaded enclosed portions are shown with a corresponding offset plane A′.

[0114] It should be understood that the tapered valve seat surface 22 may also include a plurality of radially extending flat valve seat portions 24 .

[0115] Any system features as described herein may also be provided as method features, and vice versa.As used herein, means-plus-function features may be expressed alternatively in terms of their corresponding structures.

[0116] Any feature in one aspect or embodiment may be applied to other aspects in any appropriate combination. In particular, method aspects may be applied to system aspects, and vice versa. In addition, any, some and / or all features in one aspect or embodiment may be applied to any, some and / or all features in any other aspect or embodiment in any appropriate combination.

[0117] It should also be understood that specific combinations of the various features described and defined in any aspect may be implemented and / or provided and / or used independently.

Claims

1. A valve (1) for closing a pipe (2), the valve (1) comprising: Central axis X; a body (10) having an inlet (12) and an outlet (14); a body wall (16) defining an aperture (18) extending between the inlet (12) and the outlet (14); A plurality of closing portions (30) for closing the apertures (18); a valve mechanism (70) connectable to an actuator (80), The plurality of closing portions (30) can be moved by the valve mechanism (70) from a first closed position (8) when the valve is closed to a second open position (9) when the valve is open, The body wall (16) includes a valve seat (20) for receiving the plurality of closure portions (30), Each closure part (30) has a first end (31) and a second end (32) and a middle part (33) for sealing the aperture (18), the middle part (36) including a valve sealing surface (38) for sealing to another closure part (30) and a tube sealing surface (40) for sealing to the tube (2); A plurality of first fixed pivot mounting members (41) on the body (10), and wherein: The first end (31) of each closure portion (30) is pivotally mounted within one of the plurality of first fixed pivot mounts (41); a plurality of second non-fixed pivot mounts (42) connected to the valve mechanism (70), and wherein the second end (32) of each closure portion (30) is pivotally mounted within one of the plurality of second non-fixed pivot mounts (42); Wherein the valve mechanism (70) and therefore each second non-fixed pivot mounting (42) is movable in three dimensions between the first closed position (8) and the second open position (9).

2. The valve (1) according to claim 1, wherein: The valve mechanism (70) is configured to move the plurality of second non-fixed pivot mounts (42) along and circumferentially about the axis X to move the closure portion (30) radially, axially and circumferentially relative to the axis X from the first closed position (8) to the second open position (9).

3. A valve according to claim 1 or 2, each first fixed pivot mounting member (41) includes a first pivot (51) having a first rotation axis α and a second pivot (52) having a second rotation axis β, and each second non-fixed pivot mounting member (42) includes a third pivot (53) that is free to rotate around all three axes.

4. A valve (1) according to claim 1 or 2, each first fixed pivot mounting (41) includes a third pivot (53) that is free to rotate around all three axes, and each second non-fixed pivot mounting (42) includes a first pivot (51) having a first rotation axis α and a second pivot (51) having a second rotation axis β.

5. Valve (1) according to any one of the preceding claims, wherein: The valve seat (20) includes a circumferentially extending conical valve seat surface (22).

6. A valve (1) according to any one of claims 3 to 5, comprising a transverse plane C perpendicular to the axis X, and for each closing portion (30) also comprising a longitudinal plane A coinciding with the axis X and a first offset plane A' offset from the longitudinal plane A by a distance D1, wherein The first axis α coincides with the first plane A'.

7. The valve (1) according to claim 6, wherein: Each closed portion (30) comprises a first pressure centre point P1 when the closed portions (30) are viewed in the transverse plane C when the valve (1) is in the closed position (8); and The first plane A' is located on the first pressure center point P1.

8. The valve (1) according to claim 7, wherein: When in the closed position (8), each closure portion (30) comprises a second pressure centre point P2 when viewed in the longitudinal plane A and a third pressure centre point P3 when viewed in the lateral plane B; and wherein the pressure center point P2 of each closed portion (30) coincides with the corresponding axis α when viewed in its corresponding longitudinal plane A; So as to maintain a pressure balanced state when the valve 1 is in the closed position 8 .

9. The valve (1) according to claim 6, wherein: When in the closed position (8), each closed part (30) includes a first pressure center point P1 when viewed in the transverse plane C, a second pressure center point P2 when viewed in the longitudinal plane A, and a third pressure center point P3 when viewed in the lateral plane B, each pressure center point P1, P2, P3 having an associated force and an associated moment M1, M2 and M3 applied to the corresponding closed part (30); and wherein, when viewed in the transverse plane C, each pressure center point P1 is offset from the corresponding axis α, and when viewed in the corresponding longitudinal plane A, each pressure center point P2 is offset from the corresponding axis α, so that the associated moments act in opposite directions so that they cancel each other out, resulting in a zero combined moment.

10. A valve according to any one of claims 3 to 9, wherein: The third pivot axis (53) of the respective closure portion (30) is located on the longitudinal plane A when in the closed position 8.

11. Valve (1) according to any one of claims 6 to 10, comprising, for each closing portion (30), a lateral plane B coinciding with the axis X and perpendicular to the longitudinal plane A; in, When the valve is in the closed position (8), the second axis β coincides with a second offset plane B′ offset from the lateral plane B by a distance D2.

12. Valve (1) according to claims 6 to 11, comprising, for each closing portion (30), a lateral plane B coinciding with the axis X and perpendicular to the longitudinal plane A, and each pipe sealing surface (40) having a first end (40a) on the side of the longitudinal plane A having the pressure center of the corresponding closing portion (30) and a second end (40b) on the side of the longitudinal plane A opposite to the first end (40a); in, said first axis of rotation α of the respective closed portion (30) intersects a lateral plane B associated with said respective closed portion (30) in a region R delimited by a first line F and a second line G; The first line F extends along the lateral plane B and is perpendicular to the surface of the seat sealing surface (22) at the point where the valve seat intersects the lateral plane B on the first side of the longitudinal plane A; as well as The second line G extends along the lateral plane B and is perpendicular to a line projected from the valve seat surface (22) onto the lateral plane B at a point where the second end (40b) is located when in the closed position (8).

13. The valve (1) according to claims 6 to 12, wherein: The valve seat (20) has a first end (26) close to the valve mechanism (70) and a second end (28) away from the valve mechanism (70), and the transverse plane C coincides with the second end (28) of the valve seat (20); and The second axis β intersects said longitudinal plane A of the corresponding closing portion (30) on the side of the plane C opposite to said valve mechanism (70).

14. The valve (1) according to claims 6 to 13, wherein: A third line H extends along the longitudinal plane A of the corresponding closed portion (30), perpendicular to the valve seat surface (22) at the point where the valve seat (20) intersects the longitudinal plane A; and The second axis β intersects the longitudinal plane A in a zone S delimited by the transverse plane C and the third line H.

15. Valve (1) according to claims 6 to 14, wherein: The second non-fixed pivot mount 42 is positioned radially outside the seat ( 20 ) from the axis X.

16. The valve (1) according to any one of claims 3 to 15, wherein: The third pivot (53) comprises a spherical joint.

17. The valve (1) according to claims 3 to 16, wherein: Each first pivot (51) is connected to its corresponding second pivot (52) via a connecting rod (60); The connecting rod (60) is connected to the main body (10) or the valve mechanism (70) through the first pivot (51), and the connecting rod (60) is connected to the corresponding closing part (30) through the second pivot (52).

18. Valve (1) according to claims 3 to 17, wherein: The first axis α and the second axis β intersect.

19. The valve (1) according to claim 17 or 18, wherein: The connecting rod (60) includes a first end (61) and a second end (62) separated by a length L; and The first pivot (51) is located at the first end (61) of the connecting rod and the second pivot (52) is located at the second end (62) of the connecting rod (60) such that the first axis α is offset from the second axis β by the length L.

20. Valve (1) according to any one of the preceding claims, wherein: There are n closure portions (30), each of which includes one or more valve sealing surfaces (38), including a first valve sealing surface (38) extending radially from the axis X toward the first fixed pivot mount (41) and a second valve sealing surface (39) extending radially from the axis X at an angle of 360 / n to the first valve sealing surface (38).

21. Valve (1) according to any one of the preceding claims, wherein: The one or more valve sealing surfaces (38, 39) are parallel to the axis X.

22. Valve (1) according to any one of the preceding claims, wherein: The tube sealing surface (40) is tapered to match the valve seat surface (22).

23. Valve (1) according to any one of the preceding claims, wherein: A portion of each first valve sealing surface (38) close to the valve seat (20) extends away from the longitudinal plane A on a side of the longitudinal plane A opposite to the pressure center P.

24. Valve (1) according to any one of the preceding claims, wherein: A portion of the second valve sealing surface (39) close to the valve seat (20) extends away from the longitudinal plane A on the same side of the longitudinal plane A as the pressure center P.

25. The valve (1) according to any one of claims 5 to 24, wherein: The valve seat surface (22) is divided into one or more flat valve seat portions (24).

26. The valve (1) according to any one of claims 5 to 25, wherein: The valve seat surface (22) forms an angle ε with the axis X that is less than 90 degrees.

27. Valve (1) according to any one of the preceding claims, wherein: The one or more valve sealing surfaces (38, 39) are offset in a first direction along the axis X and connected to the tube sealing surface (40) via an intermediate sealing surface (37) to form a continuous seal around the closure portion (30).

28. Valve (1) according to any one of the preceding claims, wherein: The valve sealing surface (38) includes a chamfered lower edge (44) for gaps between the plurality of closure portions (30) when moving from the first closed position (8) to the second open position (9).

29. Valve (1) according to any one of the preceding claims, wherein: The valve mechanism (70) includes a control ring (72) including the plurality of second non-fixed pivot mounts (42) for connecting the plurality of closure portions (30) to the control ring (72).

30. The valve (1) according to claim 29, wherein: The body (10) includes a control ring guide (74) for limiting the movement of the control ring (72) to translation along axis X and rotation about axis X.

31. A valve (1) according to claim 29 or 30, wherein: The control ring (72) includes engagement means (76) for engaging an actuator (80).

32. Valve (1) according to any one of the preceding claims, wherein: The body wall (16) is continuous and has no apertures except for the inlet (12) and the outlet (14).

33. Valve (1) according to claim 31 or 32, further comprising one or more actuators (80) for moving the control ring (72).

34. Valve (1) according to claim 33, wherein The one or more actuators (80) include a magnetic coupling (82).

35. Valve (1) according to any one of the preceding claims, wherein: The inlet (12) and the outlet (14) comprise flanged, threaded or welded pipe connections (15).

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