Valve comprising tiltable piston member

Abstract

The invention relates to a valve (1), such as a shut-off valve. The valve (1) comprises a housing having a first port (3) and a second port (4). Further, the valve (1) comprises a valve stem (6) arranged inside said housing, and a first piston member (9) extending along a first longitudinal axis (Lp1) and coupled to the valve stem (6). The valve stem (6) is movable in rotation about its longitudinal axis (Lv) and the first piston part (9) is axially movable along the first longitudinal axis (Lp1). In order to provide a valve (1) which compensates for misalignment of the valve parts and ensures leak-free valve closing, the valve (1) additionally comprises a second piston part (10) which extends along a second longitudinal axis (Lp2) and which is axially coupled to the first piston part (9). The second piston part (10) is movable together with the first piston part (9) between an open position and a closed position. Further, the second piston part (10) can be tilted relative to the first piston part (9).

Description

[0001] The invention relates to a valve, such as a shut-off valve, comprising a housing having a first port and a second port, a valve stem, and a first piston part and a second piston part.

[0002] Valves, in particular shut-off valves, have been known for a long time and are generally used to shut off or control the flow of a fluid. However, demanding environments require continuous improvements to known valve systems. Such environments can occur in CO2 refrigeration systems, in which, for example, temperatures of 150°C and pressures of 140 bar are reached, so that a large torque of, for example, 70 Nm is required to provide a reliable valve closure.

[0003] Typically, each valve comprises several components which are manufactured separately and assembled. However, this means that, due to assembly and manufacturing, the final valve assembly will be within a tolerance range and misalignments between a valve closure element comprising a sealing element, which is to be seated on a valve seat in order to close the valve, and the valve seat can have to be compensated. Thus, a safe and reliable valve closure, preferably without leakage, can only be guaranteed if these tolerance differences are compensated, for example, by applying a large torque and pressing the valve closure element against the valve seat. When the valve closure element is pressed against the valve seat, the deformation of the sealing element ensures a tight seal in the case of misalignments.

[0004] However, the application of a large torque has several disadvantages, regardless of whether the valve is closed manually or automatically. For example, in the case of a valve system controlled by an electric motor, the motor must be able to apply a greater torque to the valve closure element, which is typically reflected in the cost and size of the electric motor.

[0005] It is therefore an object of the present invention to provide a valve which eliminates these disadvantages and guarantees a reliable valve closure and compensation of misalignments, even at significantly lower torques than comparable system valves.

[0006] This object is solved by a valve according to claim 1.

[0007] A valve (e.g., a gate valve) includes a housing having a first port and a second port. One port can be an inlet port, and the other port can be an outlet port. Thus, when the valve is in the open position, fluid can flow from the inlet port to the outlet port, for example, from the first port to the second port. A valve stem is disposed inside the housing. Further, a first piston component extending along a first longitudinal axis is coupled to the valve stem. The valve stem is rotatably movable about its longitudinal axis (i.e., the longitudinal axis of the valve stem). The valve stem can be axially constrained to the housing and therefore cannot move axially along its longitudinal axis. When the valve components are assembled, the longitudinal axis of the valve stem and the first longitudinal axis of the first piston component extend parallel but do not coincide. However, preferably, the longitudinal axis of the valve and the first longitudinal axis are aligned. Therefore, the valve stem can also rotate about the first longitudinal axis relative to the housing.

[0008] When the valve stem rotates, the first piston component moves axially along a first longitudinal axis and relative to the housing. This rotation can be caused, for example, manually or automatically by applying torque to the valve stem by a motor such as an electric motor. In this regard, the first piston component or other components connected to the first piston component can be threadedly engaged with the valve stem and rotatably constrained to the housing so as to move axially along the first longitudinal axis when the valve stem rotates. For example, a guide nut and a washer can be provided, wherein the guide nut, as part of the first piston component, is threadedly engaged with the valve stem, rotatably constrained to the housing, and configured to convert the rotational movement of the valve stem into axial movement of the first piston component along the first longitudinal axis by means of the washer, which has a protruding key guided in a keyway in the housing. The threaded engagement between the guide nut and the valve stem can be self-locking. Although the valve stem can be rotated automatically, for example by an electric motor, it can also be configured to be rotated manually, for example, if the electric motor fails.

[0009] Furthermore, the valve includes a second piston component extending along its longitudinal axis, i.e., along a second longitudinal axis. The second piston component is axially coupled to the first piston component and is therefore movable together with the first piston component between the valve's open and closed positions. This means that when the valve stem rotates to move the first piston component axially, the second piston component is also translated and configured to close one port of the valve to prevent fluid from flowing from one port to the other. Therefore, when the first piston component moves from the closed position to the open position in the valve closing direction, the second piston component also moves axially, wherein in the closed position, the second piston component is located on the valve seat to close the valve. Accordingly, the second piston component may include a seal that is located on the valve seat when the second piston component is in the closed position.

[0010] Furthermore, the second piston assembly can be tilted relative to the first piston assembly. This means that the second piston assembly can deflect relative to the first piston assembly in a tilting direction. Therefore, when the valve is in the open position, the second longitudinal axis can be aligned with the first longitudinal axis, and when the valve is in the closed position, the second longitudinal axis can be tilted relative to the first longitudinal axis. The second longitudinal axis can be further aligned with the longitudinal axis of the valve stem, for example, when the valve is in the open position. However, when the valve is in the closed position, the second piston assembly can be tilted relative to the first piston assembly, and therefore, in the closed state, the second longitudinal axis can be tilted relative to both the first longitudinal axis and the longitudinal axis of the valve stem.

[0011] In other words, and considering that the plane of the second piston component has a normal vector defining the plane's normal direction, wherein the normal vector extends parallel to the second longitudinal axis, tilting the second piston component relative to the first piston component causes the plane to be skewed relative to the first longitudinal axis, i.e., forming an angle not equal to 0° between the normal vector and the first longitudinal axis. Therefore, the terms "to tilt," "can tilt," or "tilt" can define the deflection of one axis (here, the second longitudinal axis) relative to another axis (here, the first longitudinal axis), wherein the two axes (if not tilted) are parallel or aligned with each other, and wherein the tilt of the axis (here, the second longitudinal axis) is related to the deflection of the corresponding component (here, the second piston component). The tilting of the second piston component allows for tolerances and misalignments in the compensating valve due to manufacturing. Therefore, the force required to securely close one port is significantly reduced.

[0012] According to one aspect, the second piston component may be tiltable relative to the first piston component at a tilt angle defined between the first longitudinal axis and the second longitudinal axis. The tilt angle between the first and second longitudinal axes may be at least 0.2°. However, in some embodiments, a tilt angle of at least 0.5° may be preferred. Typically, however, a tilt angle greater than 1° is not required to produce the desired technical effect. However, the value 5° should be understood less as a limiting upper limit and more as an instruction from a person skilled in the art. Furthermore, the tilt angle may also be between 0.2° and 5°. Choosing a very large tilt angle may cause the second piston component to impinge on the housing when the fluid flow can deflect the second piston component, which may lead to undesirable effects and potentially damage. Meanwhile, choosing too small a tilt angle may not adequately compensate for manufacturing tolerances and misalignments.

[0013] According to another aspect of the invention, the first piston component and the second piston component may be partially arranged inside each other. Thus, a portion of a plug section having a first outer diameter in one of the first and second piston components is arranged within a socket section of the other. Therefore, either the first or second piston component may include the plug section. The other component then includes the socket section. Thus, the first piston component may be partially arranged within the second piston component, or vice versa. The plug section and the socket section define overlapping portions of the respective piston components. Further, the socket section may include a second inner diameter larger than the first diameter to receive the plug section of the respective piston component. Furthermore, a gap formed by lateral distance may exist between the plug section and the socket section. Providing a gap between the plug section and the socket section allows the second piston component to tilt. However, other types of connections between the two piston components are also possible. For example, a joint may be used to allow the second piston component to tilt relative to the first piston component. However, using a plug-socket connection allows for simple, uncomplicated, and low-wear assembly.

[0014] According to another aspect, the first piston component may be partially arranged inside the second piston component. The first outer diameter of the plug section and the second inner diameter of the socket section may differ from each other in the range of 0.2 mm to 0.6 mm. Considering the cylindrical plug section inserted into the cylindrical socket section, if the cylindrical sections are arranged relatively centrally relative to each other, this will result in a circumferential gap between the corresponding inner and outer walls of the two sections being between 0.1 mm and 0.3 mm. Preferably, the first diameter of the plug section and the second diameter of the socket section differ from each other by 0.4 mm. Obviously, when one section is laterally displaced relative to the other section, one side may have no gap, but the gap on the other side increases. According to the invention, the first outer diameter should be understood as the maximum diameter of the plug section. Therefore, when the plug section includes a recess, the first outer diameter decreases in the region of the recess. Therefore, the diameter in the region of the recess is not included in the first outer diameter. In contrast, and according to the invention, the second inner diameter should be understood as the minimum diameter of the socket section. Therefore, when the socket section includes a recess, the second inner diameter increases in the region of the recess. Thus, the diameter in the recess region is not included in the second inner diameter. In summary, this means that when the first outer diameter of the plug section can be 15.6 mm at some points in the overlapping region, and 15 mm and 14 mm at other points in the overlapping region, the first outer diameter should be understood as 15.6 mm. Conversely, when the second inner diameter of the socket section can be 16 mm at some points in the overlapping region, and 17.6 mm and 18 mm at other points in the overlapping region, the second inner diameter should be understood as 16 mm. Here, the socket section and the plug section are interposed between each other by 20 mm and 22 mm along the second longitudinal axis; that is, there is an overlap region of 20 mm to 22 mm between the plug section and the socket section, measured along the second longitudinal axis.

[0015] In one example, the first outer diameter of the plug section may be 11.5 mm at some points in the overlapping area, and 11 mm and 10.5 mm at other points in the overlapping area, where the first outer diameter should be understood as 11.5 mm. The second inner diameter of the socket section can then be between 11.7 mm and 12.1 mm.

[0016] In one embodiment, the second piston component can be axially connected to the first piston component via a bearing arranged between the socket section and the plug section. Therefore, the bearing can be arranged in the overlapping area of ​​the socket section and the plug section. The bearing can be a rolling bearing, preferably a ball bearing. However, any other bearing configured to axially connect the second piston component to the first piston component can be used. The ball bearing can include thirteen balls. The balls of the ball bearing can be made of stainless steel, while the first and second piston components are made of low-carbon steel. The bearing can be arranged in corresponding recesses formed on the first and second diameters. The bearing allows relative rotational movement between the first and second piston components. However, due to the bearing, the second piston component may not be able to move axially relative to the first piston component. In this respect, "no axial movement" can also be understood as allowing only limited axial movement, where the limited axial movement does not allow the first and second piston components to be disengaged. Simultaneously, the bearing allows tilting between the second and first piston components. Using a ball bearing can be advantageous because the second piston component can roll relative to the first piston component on the surface of the rolling element to tilt. Furthermore, ball bearings require less maintenance due to the advantage of their placement between the socket section and the plug section.

[0017] According to one embodiment, a first seal may be disposed between the receptacle section and the plug section. Therefore, the seal can be arranged in the overlapping area of ​​the receptacle section and the plug section. The first seal can help prevent rotation between the second piston component and the first piston component due to friction. The first seal can seal the gap formed by lateral distance. This means that no fluid can reach the other side of the seal from within the gap or through the seal. In one embodiment, the first seal can be arranged further away from the valve stem than the bearing. In other words, the bearing can be closer to the valve stem than the first seal. Considering a valve including a balancing pressure chamber as described below, the first seal can allow fluid and pressure to be fully transmitted to the balancing pressure chamber, respectively.

[0018] In one embodiment, the first seal may include a first sealing element and a second sealing element, the first sealing element including an O-ring, the second sealing element partially surrounding the first sealing element. Further, the first sealing element may abut against the second sealing element. The O-ring may be an internal sealing element surrounding a plug section about a first longitudinal axis, wherein the second sealing element may be an external sealing element partially surrounding both the internal sealing element and the plug section about the first longitudinal axis. Therefore, "partially" does not mean that the second sealing element does not completely surround the plug section, but rather that it does not completely surround the first sealing element. The second sealing element may have a substantially semi-circular cross-section, the curved profile of which abuts against the socket section. Using two different elements to provide the first seal allows each corresponding element to use a different material. Additionally, the corresponding seal allows the second piston component to tilt relative to the first piston component without reducing the sealing effect of the first seal. Further, the O-ring may press the second sealing element against the socket section. Especially when the valve is used at high pressures and temperatures of 140 bar and 150°C, this gap will be too large to be reliably sealed by the O-ring alone. The pressure differential on a closed valve can exceed 90 bar.

[0019] According to another embodiment, the valve may include a tapered portion at the end of the second piston component opposite to the first piston component. The tapered portion may include a central apex surrounded by a flow-guiding surface of a concave shape that gradually converges towards the apex. The tapered portion may be screwed onto the second piston component. The specific shape of the tapered portion can improve fluid flow, where the force exerted by the fluid flow on the piston component is smaller.

[0020] Furthermore, the valve may additionally include a second seal configured to seal the first port relative to the second port when the valve is in the closed position. The second seal may be at least partially arranged, for example, clamped between the second piston assembly and the tapered portion. Thus, when the tapered portion is screwed onto the second piston assembly, the second seal can be held in place without requiring additional securing devices. In the closed position of the valve, the second seal may press against the orifice of one of the ports. Accordingly, when the second piston assembly moves to the closed position, i.e., when fluid flow from the first port to the second port is blocked, the second seal may be located on the valve seat.

[0021] In one embodiment, the second seal may comprise polyetheretherketone (PEEK) and / or the first seal may comprise polytetrafluoroethylene (PTFE). For example, the first sealing element of the first seal may be made of an elastic material (such as rubber), wherein the second sealing element may be made of PTFE. As a result, an O-ring made of rubber can apply force to the second sealing element, wherein the second sealing element presses against the receptacle section of the second piston component. Using PTFE for the second sealing element allows for less deformation under high pressure. Simultaneously, the O-ring made of rubber helps to seal the gap. Further, using PEEK for the second seal can provide a seal comprising high strength, high stiffness, and heat resistance. In one embodiment, the second seal may also comprise two sealing elements, for example, an O-ring made of rubber that can apply force to a further sealing element made of PEEK.

[0022] In one embodiment, when the second piston component is tilted relative to the first longitudinal axis, the second piston component can move partially in the tilting direction. Each direction perpendicular to the first longitudinal axis can be a tilting direction. During tilting, the second piston component moves not only laterally in the tilting direction but also partially in a direction parallel to the first longitudinal axis, such as towards the valve stem. However, especially when the socket section and plug section are cylindrical in shape, the tilting direction can be any direction perpendicular to the first longitudinal axis. Therefore, considering the plug section of the first piston component (which can be cylindrical and thus have a circular cross-section), the tilting of the second piston component allows for partial movement of the second piston component in a direction laterally to the first longitudinal axis, and wherein this lateral direction can be any direction relative to the cross-sectional area; that is, each of the 360° directions relative to the circular cross-sectional area would be a possible tilting direction. This degree of freedom allows for extremely efficient compensation for tolerance and misalignment differences.

[0023] In another embodiment, the valve may include a balancing pressure chamber and an internal passage. When the valve is in the closed position, the internal passage may be configured to fluidly connect a first port to the balancing pressure chamber. Thus, when the valve is in the closed position and a second seal seals the first port relative to the second port, fluid, for example, pressed against a tapered portion, can enter the internal passage to flow into the balancing pressure chamber. The balancing pressure chamber may be sealed relative to the port, for example, by a piston seal, which is part of a first piston assembly, abutting against the housing independently of the position of the first piston assembly. Further, the balancing pressure chamber is configured such that fluid entering the balancing pressure chamber can apply a force (i.e., in the valve closing direction) to a portion of the piston assembly. Due to this force pointing in the valve closing direction, the fluids acting, for example, on the tapered portion and applying a force in the valve opening direction can be balanced, i.e., substantially the same in magnitude but opposite in direction. The more similar the forces caused by the fluid pressure applied to the pressure surfaces, the more similar the surfaces on which the pressure acts. Ideally, the pressure surfaces are identical in size and orientation, such that the forces caused by the fluid pressure acting on these surfaces and pointing in the valve opening or valve closing direction are perfectly balanced. Therefore, a smaller force is required to hold the valve in the closed position. In this regard, the valve may include a balancing chamber, wherein the balancing pressure chamber may include a first pressure surface at least partially facing the valve opening direction, wherein the second piston component may include a second pressure surface at least partially facing the valve closing direction, and wherein the first and second pressure surfaces may be configured such that when the valve is in the closed position, the magnitudes of a first force acting on the first pressure surface and the second force acting on the second pressure surface may be substantially the same but opposite in direction. Considering the first port as the inlet port, this balancing may be referred to as inlet balancing or balance on the first port side.

[0024] However, the valve can also provide output balance or equilibrium on the second port side, i.e., balance relative to the fluid that has passed the second piston assembly and is about to leave the second port. In this regard, the valve may include a third pressure surface at least partially facing the valve opening direction, and the first piston assembly may include a fourth pressure surface at least partially facing the valve closing direction, wherein the third and fourth pressure surfaces can be configured such that when the valve is in the closed position, the magnitudes of the third force acting on the third pressure surface and the fourth force acting on the fourth pressure surface can be substantially the same but opposite in direction. Assuming both the first port equilibrium and the second port equilibrium are applied, ideally, all forces caused by the fluid are balanced against each other, such that the valve remains in the proper position even without continuous application of force along the valve closing direction or the locking mechanism. However, the valve may additionally or alternatively include a locking mechanism that locks the valve in the desired position, preventing the valve from changing position without unlocking the locking mechanism.

[0025] In one aspect, the internal passage may include an opening at least partially facing the valve closing direction. The opening can be considered as a plane including a normal vector that at least partially points towards the valve closing direction; or in other words, the normal vector of the opening plane includes a component parallel to the valve closing direction. Additionally, in one embodiment, the opening may also face a first port. Further, the internal passage may be at least partially disposed within the first piston member, the second piston member, and the tapered portion (if present). Thus, the internal passage provides a fluid passage through the aforementioned components of the valve from the first port side and leads to a region at least partially located above the first and second piston members. This ensures that fluid can flow into the region of the valve where a first force can be applied to a first pressure surface. In one embodiment, the internal passage may also be at least partially disposed within the valve stem.

[0026] In one embodiment, the second piston component may include an annular channel disposed in a plane perpendicular to the second longitudinal axis at its end opposite to the first piston component. Thus, the annular channel can be arranged such that it surrounds the second longitudinal axis. Further, a tapered portion may be disposed at the end of the second piston component opposite to the first piston component. The annular channel may open toward the valve closing direction such that a portion of the internal channel of the tapered portion is always fluidly connected to the remainder of the internal channel via the annular channel, regardless of the rotational position of the tapered portion relative to the second longitudinal axis. Therefore, it is not important how far or how tightly the tapered portion is screwed onto the first piston component, or how the tapered portion is brought into the second piston component during assembly to ensure that the internal channel fluidly connects the first port to the balancing pressure chamber, when the tapered portion is, for example, screwed onto the second piston component. Therefore, providing an annular channel simplifies valve assembly and allows fluid to be delivered to the balancing pressure chamber independently of the rotational position of the tapered portion.

[0027] According to another approach, the valve may include an electric motor. Therefore, the valve can be automatically driven by the electric motor, which applies torque to the valve stem. The electric motor may be a DC electric motor. The electric motor can be configured to apply a maximum torque of less than 30 Nm to the valve stem. Preferably, the electric motor applies a torque of less than 20 Nm. The electric motor can apply a torque between 8 Nm and 12 Nm. The use of such a small electric motor has been successfully tested in configurations where approximately 70 Nm of torque was previously required to securely close the valve, i.e., to prevent leakage, due to misalignment. The electric motor may be equipped with a control unit that allows, for example, remote access to the valve control via a network. The valve may also be equipped with other components, such as sensors, data storage devices, and / or transmitting and receiving units, to send data to and receive data from the remote control unit.

[0028] Finally, it should be noted that, based on the combination of features, the present invention also provides a valve that can be driven by an electric motor, the valve including a tiltable piston component, and wherein the valve is balanced.

[0029] Additional features, advantages, and possible applications of the invention will derive from the following description of exemplary embodiments and the accompanying drawings. All features described and / or illustrated herein, individually or in any desired combination, form the subject matter of the invention, regardless of how they are combined in the claims or in their retrospective reference to the preceding claims.

[0030] Preferred embodiments of the invention will now be described with reference to the accompanying drawings, in which:

[0031] Figure 1 A cross-sectional view of the valve according to the invention in the open position is shown;

[0032] Figure 2 It shows Figure 2 Detailed view of section A in the diagram;

[0033] Figure 3 It shows that according to Figure 1 A cross-sectional view of the valve in the closed position;

[0034] Figure 4 It shows that according to Figure 1 A cross-sectional view of the valve, wherein the second piston assembly is inclined relative to the first piston assembly;

[0035] Figure 5 It shows Figure 4 Detailed view of section B in the diagram;

[0036] Figure 6 It shows Figure 4 Detailed view of section C in the diagram;

[0037] Figure 7 It shows along Figure 4 A cross-sectional view of line DD in the diagram; and

[0038] Figure 8 It shows Figure 4 Detailed view of section E in the diagram.

[0039] exist Figure 1 The image depicts a valve 1 according to the invention in the open position. The valve 1 includes a housing 2 having a first port 3 and a second port 4, wherein the first port 3 includes a valve seat 3a. Further, the first port 3 may define a fluid inlet, and the second port 4 may define a fluid outlet. In the open position, fluid can flow into the first port 3 and out through the second port 4. The housing 2 includes a top part 2a and a lower part 2b. The top part 2a may also be referred to as a valve cover. The top part 2a can substantially house the actuation device of the valve 1, wherein the lower part 2b may include ports 3 and 4.

[0040] The top part 2a and the lower part 2b of the valve 1 housing 2 are screwed together by bolts 5. During the assembly of the valve components, these bolts 5 and other manufacturing tolerances of the valve components typically (i.e., not employing the inventive concept) lead to tolerances and misalignments, thereby weakening the valve's performance when moved to a position such as... Figure 3 The depicted closed position is the ability to prevent fluid flow between the first port 3 and the second port 4. Therefore, the object of the present invention is to overcome these tolerances and misalignments and to improve the valve.

[0041] In this respect, valve 1 includes an actuating device, such as valve stem 6, disposed within housing 2. Here, valve stem 6 is functionally coupled to electric motor 7. Electric motor 7 may be a DC electric motor. Further, electric motor 7 may be configured to apply a torque of less than 30 Nm to valve stem 6, thereby causing valve stem 6 to move about its longitudinal axis L. V Rotation. The electric motor 7 can be remotely controlled. However, instead of using the electric motor 7, the valve 1 can be manually operated, for example, by a person using a handwheel.

[0042] Furthermore, the guide nut 8, as part of the first piston component 9, is threaded to the valve stem 6, rotatably constrained to the housing 2, and configured to convert the rotational movement of the valve stem 6 into the first piston component 9 along the first longitudinal axis L. p1 The axial movement. Here, the first longitudinal axis L p1 With respect to the longitudinal axis L of valve stem 6 v Alignment. The threaded engagement between the guide nut 8 and the valve stem 6 can be self-locking.

[0043] exist Figure 1In at least some areas, the first piston component 9 is arranged above the second piston component 10 because the first piston component 9 includes a plug section 11 that inserts into a socket section 12 of the second piston component 10. The plug section 11 and the socket section 12 (i.e., the first piston component 9 and the second piston component 10) are axially connected by a bearing 13. Here, the bearing 13 is provided as a ball bearing with balls made of stainless steel. The bearing 13 allows the second piston component 10 to rotate relative to the first piston component 9.

[0044] Figure 2 It shows Figure 1 A more detailed view of section A. Section A clearly depicts the ball bearings arranged in the recesses of the plug section 11 and the socket section 12. The rolling elements of the bearing 13 are accessible via flat-head screws 14, which, for example, simplifies the assembly of the valve 1.

[0045] Furthermore, Figure 2 The outer diameter D of the plug section 11 of the first piston component 9 is shown. o The inner diameter D of the socket section 12 of the second piston component 10 is smaller than that of the second piston component 10. i Therefore, a gap 18 is formed between the plug section 11 and the socket section 12.

[0046] Furthermore, a first seal 15 is disposed in a recess of the plug section 11 of the first piston component 9. The first seal 15 is formed by two sealing elements (i.e., a first sealing element 16 and a second sealing element 17). The first sealing element 16 is formed by an O-ring, which is surrounded by the second sealing element 17 having a substantially semi-circular cross-sectional profile. The first sealing element 16 is at least partially disposed within the second sealing element 17. The O-ring presses the second sealing element 17 against the socket section 12 and is thus configured to seal the gap 18 formed by the lateral gap between the plug section 11 and the socket section 12. Figure 6 The gap 18 can be seen better in the middle. Due to the inclination, a gap angle β is formed between the outer wall of the plug section 11 and the inner wall of the socket section 12.

[0047] The contact and friction between the first seal 15 and the socket section 12 make it more difficult for the second piston component 10 to rotate relative to the first piston component 9. That is, rotation is theoretically possible, but only by applying a very large force.

[0048] The gap 18 between the first piston component 9 and the second piston component 10 allows the second piston component 10 to be tiltable relative to the first piston component 9. However, in Figure 1 In the valve position shown, the second piston component 10 is not tilted, such that the second longitudinal axis L of the second piston component 10 is... p2The first longitudinal axis L relative to the first piston component 9 p1 No deflection. However, the second piston component 10 can be perpendicular to the first longitudinal axis L. p1 Inclined in any direction, where the dashed arrow indicates a direction perpendicular to the first longitudinal axis L. p1 Possible tilt direction T d .

[0049] Additionally, the end of the second piston component 10 pointing towards the first port 3 includes a tapered portion 19, which is screwed onto the pin 20 of the second piston component 10. A second seal 21 is at least partially disposed or clamped between the tapered portion 19 and the second piston component 9. When the valve 1 is moved to the closed position, as... Figure 3 As shown, the second seal 21 is responsible for sealing the first port 3 and thus presses against the valve seat 3a.

[0050] The tapered portion 19 includes a central apex 22 around which a concave flow-guiding surface 23 surrounds. The flow-guiding surface 23 gradually converges from the outer region where the second seal 21 is disposed toward the apex 22. The flow-guiding surface 23 is specifically used to guide fluid flow and, for example, to prevent turbulence of the fluid at the sharp edges of the valve component.

[0051] In the tapered portion 19 shown here, an opening 24 is provided, which allows fluid to enter the internal passage 25. The internal passage 25 passes through the tapered portion 19, the annular passage 26, the second piston component 10, and the first piston component 9, leading to the balancing pressure chamber 27. Here, the balancing pressure chamber 27 is formed by a plurality of chambers arranged above the first piston component 9 and the second piston component 10, at least in some areas. The annular passage 26 is provided as a second longitudinal axis L around the second piston component 10. p2 Extended groove. Thus, the annular channel 26 allows fluid to enter through the opening 24 and into the internal channel 25 of the second piston component 10, regardless of the rotational position of the tapered portion 19 relative to the second piston component 10.

[0052] The first seal 15 seals the internal passage 25, preventing fluid that has entered the internal passage 25 from leaving through the gap 18. Simultaneously, the piston seal 28 is disposed between the inner wall of the housing 2 and the first piston assembly 9. The piston seal 28 contacts the housing 2. (As in...) Figure 1 and Figure 3 The comparison shows that when valve 1 moves from the open position ( Figure 1 Move to the closed position ( Figure 3When the piston seal 28 slides along the inner wall, the piston seal 28 continuously seals the balance pressure chamber 27 and allows fluid to enter or leave the balance pressure chamber 27 only through the internal passage 25.

[0053] The fluid flowing into the equilibrium pressure chamber 27, especially... Figure 3 When valve 1 is in the closed position, a force F1 is applied at this location, indicated by the arrow, and this force acts on the first pressure surface 29, i.e., in the valve closing direction. Simultaneously, fluid in the region of the first port 3 presses against the tapered portion 19 and the second seal 21, i.e., against the second pressure surface 30, where a force F2, opposite to force F1, is applied, i.e., in the valve opening direction. Ideally, the pressure surfaces are designed such that the forces are balanced, so that valve 1 is considered balanced relative to the first port 3 side.

[0054] Furthermore, valve 1 includes a third pressure surface 31 formed by a surface of the second piston member 10 that faces at least partially toward the valve opening direction. Additionally, valve 1 has a fourth pressure surface 32 formed by a surface of the first piston member 9 and facing toward the valve closing direction. The fluid pressing against the third pressure surface 31 and the fourth pressure surface 32 on one side of the outlet port (i.e., the second port 4) also generates ideally equal and opposite forces F3 and F4, as indicated by arrows. Similarly, the balance of forces ensures that valve 1 is considered balanced relative to the second port 4 side. Ideally, forces F1, F2, F3, and F4 are balanced against each other, such that valve 1 remains closed without any additional force applied in the valve closing direction, and are considered balanced. Furthermore, the self-locking threaded engagement between the guide nut 8 and the valve stem 6 can be configured to provide a biasing force to keep the valve closed. However, valve 1 may include a locking mechanism (not shown).

[0055] For clear and understandable reasons, only Figure 3 Forces F1, F2, F3, and F4, and pressure surfaces 29, 30, 31, and 32 are schematically shown. For the purposes of this invention, pressure surfaces 29, 30, 31, and 32 need not be continuous surfaces. For example, as shown here, the balancing pressure chamber 27 is formed by several chambers such that the first pressure surface 29 is not formed by a continuous surface. Therefore, a pressure surface can be understood as any surface or section of surface that exerts a force on the movable part of valve 1 in the previously described directions due to fluid pressure.

[0056] As in Figure 3 As can be seen from this, axis L p1 L p2 and L vIt is aligned. This is likely due to the fact that these tolerances have been compensated for during the manufacture and assembly of valve 1, and there is no need to tilt the second piston assembly 10 to properly close valve 1. However, also in Figures 1 to 3 In this configuration, the second piston component 10 is tiltable relative to the first piston component 9. Figure 1 Compared to the valve opening position shown, Figure 3 Valve 1 in the middle only moves to the closed position.

[0057] exist Figure 4 middle, Figure 1 The valve 1 shown is illustrated as having an inclined second piston component 10. The inclination of the second piston component 10 relative to the first piston component 9 may be understood here for illustrative purposes only, since typically the inclination of the second piston component 10 only occurs when the second seal 21 contacts the first port 3 (i.e., valve seat 3a), or the inclination may be understood here as the effect of the flow that deflects the second piston component 10, even when the valve 1 is in the open position.

[0058] Therefore, in Figure 4 In this configuration, the second piston component 10 is tilted relative to the first piston component 9. This means that the second piston component 10 is deflected by a tilt angle α. More precisely, the tilt angle α is formed along the first longitudinal axis L. p1 With the second longitudinal axis L p2 The angle α typically lies between 0.2° and 5°.

[0059] Figure 5 More details are shown in the middle. Figure 4 Section B is depicted in the figure. Due to the deflection of the second piston component 10 relative to the first piston component 9, it can be noted that... Figure 5 The gap 18 is larger in the upper left region (i.e., further away from bearing 13) than in the lower left region (i.e., closer to bearing 13). However, tilting is limited because the plug section 11 abuts against the socket section 12.

[0060] Furthermore, the structures of the second seal 21 and the piston seal 28 can also be... Figure 5 The seals 21 and 28 are easily identifiable. Both seals include two sealing elements: an O-ring and an additional sealing element similar to that of the first seal 15. Preferably, the additional sealing element is made of a more robust, less elastic material, such as PEEK or PTFE, while the O-ring is made of a softer, more elastic material, such as rubber. In the second seal 21, the additional sealing element that contacts the valve seat 3a when the valve 1 is in the closed position is made of PEEK. In the piston seal 28, the additional sealing element that contacts the top part 2a of the housing 2 is made of PTFE. This makes the valve 1 particularly suitable for use at pressures exceeding 90 bar.

[0061] Figure 6 Showing more details Figure 5 The cross section C, where the cross section C is similar to Figure 2 The section A depicted in the image differs in that... Figure 6 The tilting state of the second piston component 10 and its corresponding effect on the gap 18 are shown.

[0062] Figure 7 It shows along Figure 4 The cross-sectional view of line DD is shown. The housing 2 and the first piston component 9 cover the first port 3, therefore... Figure 7 Only the second port 4 is visible. Additionally, the valve stem 6 is visible, with the guide nut 8 surrounding it. Furthermore, a washer 33 with a protruding key 34 is shown, which is guided in the keyway 35 of the housing 2, allowing rotational movement of the valve stem 6 to be converted into axial movement of the first piston component 9.

[0063] Figure 8 shown Figure 4 Section E also shows a cross-sectional view of the guide nut 8, washer 33, key 34, and keyway 35, but shown as a side cross-sectional view. As noted above, the guide nut 8 can be in self-locking thread engagement with the valve stem 6. Furthermore, the washer 33 can slide on the guide nut 8. The guide nut 8 can, for example, include a hexagonal shape, such as in… Figure 7 This can be seen in the image. Therefore, it prevents relative rotation between the washer 33 and the guide nut 8.

[0064] Furthermore, the first piston component 9 includes a collar 9a that protrudes above and partially surrounds the washer 33. When the valve 1 is assembled, the collar 9a can be bent above the washer 33. This allows a biasing force to be applied to the washer 33. The preload applied to the washer 33, along with the shapes of the washer 33 and the guide nut 8, prevents the washer 33 from rotating relative to the guide nut 8, thereby ensuring a secure connection between the first piston component 9 and the guide nut 8, and thus allowing the transmission of force and movement between the guide nut 8 and the first piston component 9.

[0065] When the electric motor 7 operates and the valve stem 6 begins to rotate, the guide nut 8, including the washer 33, converts the rotational movement into axial movement of the first piston component 9. The first piston component 9 can then move to either the open or closed position depending on the rotational direction of the valve stem 6. Considering the valve 1 in the open position (which allows fluid to flow from the first port 3 to the second port 4), the clockwise rotational movement of the valve stem 6 can close the valve 1, thereby interrupting the fluid flow from the first port 3 to the second port 4. Once the second piston component 10, including the second seal 21, reaches the first port 3 and thus begins to contact the valve seat 3a, the tiltable second piston component 10 can be positioned perpendicular to the first longitudinal axis L. p1 Inclination direction T d The upper part moves. When the second seal 21 first comes into contact with one side of the valve seat 3a (e.g., due to misalignment of the valve components), Figure 4 When the valve seat 3a (the side closer to the second port 4) is in contact with the first piston 9, and the second piston component 10 moves further in the valve closing direction, the second piston component 10 deflects relative to the first piston component 9, forming an inclination angle α. Therefore, the second piston component 10 is tilted relative to the first piston component 9. However, when the valve 1 is fully closed, the second seal 21 fully abuts against the valve seat 3a. Figure 4 In this case, the second seal 21 is also located on the upper left side of the valve seat 3a, wherein the second piston component 10 is tilted. This tilting movement allows the second piston component 10 to compensate for tolerance deviations and for misalignments that occur during the manufacture and assembly of the valve components. Therefore, the tiltable second piston component 10 allows for reliable closure of the valve 1, i.e., a leak-free or leak-proof valve 1.

[0066] When valve 1 is closed, fluid can also pass through opening 24 into annular channel 26 and internal channel 25 and into balancing pressure chamber 27. This applies a force F1 to the first pressure surface 29, acting in the direction of valve closure. Similarly, additional forces F2, F3, and F4 act on components of valve 1 and pressure surfaces 30, 31, and 32. Preferably, forces F1 and F2 are equal and act in opposite directions. The same applies to forces F3 and F4. Therefore, these forces are preferably balanced, allowing valve 1 to remain balanced and in its closed position without further force application. Subsequently, fluid flow from the first port 3 to the second port 4 can be kept blocked by the second piston component 10 until the electric motor 7 receives a signal, for example, from a control unit that can be part of a network, which causes valve 1 to reopen. At this point, valve stem 6 can then rotate counterclockwise, causing the first piston component 9 and the axially coupled second piston component 10 to move in the direction of valve opening.

[0067] Therefore, the present invention provides a valve 1 that can be closed particularly well because it allows one piston component to be tilted relative to another piston component, and thus can compensate for misalignment and tolerance.

[0068] List of reference numerals

[0069] 1 valve

[0070] 2 shells

[0071] 2a Top Component

[0072] 2b Lower component

[0073] 3 First Port

[0074] 3a valve seat

[0075] 4 Second Port

[0076] 5 bolts

[0077] 6 valve stems

[0078] 7 electric motors

[0079] 8 guide nuts

[0080] 9 First Piston Component

[0081] 9a ring

[0082] 10 Second Piston Component

[0083] 11 plug section

[0084] 12 socket sections

[0085] 13 bearings

[0086] 14 flathead screws

[0087] 15 First Seal

[0088] 16 First sealing element

[0089] 17 Second sealing element

[0090] 18 gaps

[0091] 19 Conical Sections

[0092] 20 sales

[0093] 21 Second seal

[0094] 22 vertices

[0095] 23 Flow guiding surface

[0096] 24 openings

[0097] 25 internal passages

[0098] 26 Circular Channels

[0099] 27 Balanced pressure chamber

[0100] 28 Piston Seals

[0101] 29 First pressure surface

[0102] 30 Second pressure surface

[0103] 31 Third pressure surface

[0104] 32 Fourth pressure surface

[0105] 33 Washer

[0106] 34 keys

[0107] 35 key slots

[0108] L v Longitudinal axis (valve stem)

[0109] L p1 First longitudinal axis (first piston assembly)

[0110] L p2 Second longitudinal axis (second piston assembly)

[0111] α tilt angle

[0112] β gap angle

[0113] T d Incline direction

[0114] D i inner diameter

[0115] D o outer diameter

[0116] F1 force (acting on the first pressure surface)

[0117] Force F2 (acting on the second pressure surface)

[0118] Force F3 (acting on the third pressure surface)

[0119] F4 force (acting on the fourth pressure surface).

Claims

1. A valve (1), such as a shut-off valve, comprising: The housing (2) has a first port (3) and a second port (4). Valve stem (6), which is arranged inside the housing (2), The first piston component (9) is located along the first longitudinal axis (L). p1 ) extends and connects to the valve stem (6). The valve stem (6) is capable of rotating around the longitudinal axis (L) of the valve stem. v It moves in a rotational manner. The first piston component (9) is capable of moving along the first longitudinal axis (L). p1 ) Axial movement, The valve (1) is characterized in that it includes a second piston component (10) along a second longitudinal axis (L). p2 The second piston component (10) extends and is axially connected to the first piston component (9) and is movable together with the first piston component (9) between an open position and a closed position, wherein the second piston component (10) is tiltable relative to the first piston component (9).

2. The valve (1) according to claim 1, characterized in that, The second piston component (10) can be tilted relative to the first piston component (9) along the first longitudinal axis (L). p1 ) and the second longitudinal axis (L) p2 The tilt angle (α) between the two piston components (10) is defined, wherein the second piston component (10) is capable of tilting at least 0.2°, preferably at least 0.5°.

3. The valve (1) according to claim 1 or 2, characterized in that, The first piston component (9) and the second piston component (10) are partially arranged inside each other, wherein one of the first piston component (9) and the second piston component (10) includes a first outer diameter (D). o A portion of the plug section (11) of the first piston component (9) and the second piston component (10) is disposed inside the socket section (12) of the other, wherein the second inner diameter (D) of the socket section (12) is... i ) is greater than the first diameter (D) o ), and there is a gap (18) formed by lateral distance between the plug section (11) and the socket section (12).

4. The valve (1) according to claim 3, characterized in that, The first piston component (9) is partially disposed inside the second piston component (10), wherein the first outer diameter (D) of the plug section (11) is... o ) and the second inner diameter (D) of the socket section (12) i They differ from each other in the range of 0.2 mm to 0.6 mm, preferably by 0.4 mm.

5. The valve (1) according to any one of claims 3 to 4, characterized in that, The second piston component (10) is axially connected to the first piston component (9) via a bearing (13) arranged between the socket section (12) and the plug section (11).

6. The valve (1) according to any one of claims 3 to 5, characterized in that, A first seal (15) is disposed between the socket section (12) and the plug section (11), wherein the first seal (15) seals the gap (18) formed by the lateral distance.

7. The valve (1) according to claim 6, characterized in that, The first seal (15) includes a first sealing element (16) and a second sealing element (17), the first sealing element including an O-ring, the second sealing element partially surrounding the first sealing element (16), wherein the first sealing element (16) abuts against the second sealing element (17).

8. The valve (1) according to any one of the preceding claims, characterized in that, The valve (1) includes a tapered portion (19) at the end of the second piston component (10) away from the first piston component (9), wherein the tapered portion (19) includes a central apex (22) and a flow guide surface (23) of a concave shape that gradually converges toward the apex (22) surrounds the central apex.

9. The valve (1) according to claim 8, characterized in that, The valve (1) further includes a second seal (21) configured to seal the first port (3) relative to the second port (4) when the valve (1) is in the closed position, wherein the second seal (21) is at least partially disposed between the second piston member (10) and the conical portion (19).

10. The valve (1) according to claims 6 to 9, characterized in that, The second seal (21) comprises polyetheretherketone (PEEK) and / or the first seal (15) comprises polytetrafluoroethylene (PTFE). For example, the first sealing element (16) is made of an elastic material such as rubber, and the second sealing element (17) is made of PTFE.

11. The valve (1) according to any one of the preceding claims, characterized in that, When the second piston component (10) is relative to the first longitudinal axis (L) p1 When tilted, the second piston component (10) is in the tilt direction (T) d The upper part can move, wherein the vertical axis (L) is allowed to move. p1 Each direction of ) is the tilt direction (T) d ).

12. The valve (1) according to any one of the preceding claims, characterized in that, The valve (1) includes a pressure balancing chamber (27) and an internal passage (25), wherein when the valve (1) is in the closed position, the internal passage (25) is configured to fluidly connect the first port (3) to the pressure balancing chamber (27).

13. The valve (1) according to claim 12, characterized in that, The internal passage (25) includes an opening (24) that is at least partially facing the closing direction of the valve (1), wherein the internal passage (25) is at least partially disposed inside the first piston component (9), the second piston component (10), and the conical portion (19), if present.

14. The valve (1) according to claim 13, characterized in that, The second piston component (10) includes an end portion disposed perpendicular to the second longitudinal axis (L) at the end portion of the second piston component (10) facing away from the first piston component (9). p2 An annular channel (26) in the plane of the second piston component (1), wherein the tapered portion (19) is disposed at the end of the second piston component (10) facing away from the first piston component (9), and wherein the annular channel (26) opens toward the closing direction of the valve (1), such that a portion of the internal channel (25) of the tapered portion (19) is always fluidly connected to the remainder of the internal channel (25) via the annular channel (26), regardless of the tapered portion relative to the second longitudinal axis (L). p2 How is the rotation position of ? 15. The valve (1) according to any one of the preceding claims, characterized in that, The valve (1) includes an electric motor (7) configured to apply a maximum torque of less than 30 Nm on the valve stem (6).

Images