Valves without pressure load

Abstract

A valve (1), particularly a hydrogen valve, comprising: at least one inlet (I); at least one outlet (O); a casing (2); an operating member (3) disposed within the casing, the operating member (3) being adjustable to at least one first terminal position (closed) and at least one second terminal position (open); and a control device for adjusting the operating member (3), wherein the valve (1) has a valve seat (4), the valve seat abutting against the outer circumferential surface (3') of the operating member (3) in a sealing manner at the first terminal position where the valve (1) is closed.

Description

Technical Field

[0001] The present invention relates to a valve, in particular a hydrogen valve, comprising at least one inlet, at least one outlet, a casing, an actuating member arranged in the casing, the actuating member being adjustable to at least one first end position (valve closed) and at least one second end position (valve open), and a control device for adjusting the actuating member. The invention further relates to a valve seat and a support ring for a valve of this type.

[0002] Valves and coaxial valves have long been known and commercially available. Known coaxial valves generally have an adjustable actuating member in the form of a shaft or a tube through which a control medium flows. In known solutions, this actuating member cooperates with a valve seat against which the end face of the actuating member abuts. Sealing is achieved by the control tube abutting against the valve seat, in which case the valve seat for this purpose has a surface against which the actuating member is pressed when the valve is closed.

[0003] For example, DE 10051492 A1 discloses a quantity regulating valve in the form of a coaxial valve comprising a control tube and a valve seat, in which the control tube is pressed against a substantially flat valve seat to close the valve.

[0004] However, there is a wide variety of configurations of valve seats. For example, DE 10108492 A1 discloses another coaxial valve comprising an actuating member that cooperates with a valve seat having a rounded seating surface.

[0005] These known valves share the common feature that sealing is achieved through the contact of the actuarial member with the valve seat. For this purpose, the end face of the actuarial member is formed in various ways depending on the area of ​​use and material of the valve seat. In this way, depending on the application, efforts are made to minimize pressure load on the control tube at all positions. For this purpose, the cross-section of the end face can be configured to extend sharply, for example, in the form of a collar whose tip contacts the surface of the valve seat. As a result, the inclined portion of the collar remains exposed, and ambient pressure acts on this inclined surface. Nevertheless, since in principle a portion of the end face must be in contact with the valve seat, in known coaxial valves, the pressure load is only approximately eliminated, not completely eliminated.

[0006] A further challenge is that the collar can be formed in various ways across different valve seat materials. For example, the tip of the end face may be manufactured with a nearly circular radius. Depending on the valve seat material, particularly its hardness, the tip may penetrate more or less deeply into the valve seat, or it may elastically deform upon contact. This has various effects on the precise contact point and affects the valve's switching and sealing characteristics.

[0007] This leads to another drawback: the tip may deform depending on the pressure applied within the valve. In this case, the side of the control tube on which pressure is applied is generally important for the collar or precise contact point at the valve seat. The control tube can be almost completely free of pressure load on one side, while being subjected to strong pressure on the other. Depending on the configuration of the collar or control tube, the contact point will vary depending on the sealing force applied or the deformation of the tip. As a result, coaxial valves usually have a defined flow direction and therefore a fixed mounting direction, and / or are only partially sealed against back pressure.

[0008] Another drawback of known solutions is that the contact points between the actuarial member and the valve seat are subjected to wear. This is especially true when the end face of the actuarial member is formed to be extremely sharp, and when the valve seat material is particularly inelastic and / or rigid. For the seal to function reliably even with rigid materials, the control tube must often be pressed very firmly against the seat. However, this is only possible to a certain extent, because otherwise the control tube will destroy the valve seat and / or the end of the control tube, like a punching tool. Furthermore, at the point where the actuarial member strikes the contact surface of the valve seat during valve switching, the mechanical load on the material can cause microscopic wear and / or damage. This unfavorably affects the sealing action of the valve, resulting in a deterioration of the overall valve output. This is particularly disadvantageous when the valve should be used for very light gases, such as hydrogen. As soon as the valve seat shows some degree of wear, extremely small hydrogen atoms or H2 molecules may pass through due to very minor damage and poor sealing. Therefore, the valve becomes poorly sealed and, consequently, unsuitable for such applications.

[0009] However, hydrogen is becoming increasingly important today, particularly with the development of new drive technologies in the automotive sector. As an extremely light gas, hydrogen places particularly high demands on the valves used in it. This is especially true when used at high pressures, such as 500 bar, 1000 bar, 1500 bar, or even higher. In these cases, even a very small amount of unsealing between the working member and the valve seat means the valve is no longer properly sealed. Consequently, the high pressures of hydrogen have so far been impossible to handle with known valves, or can only be handled with significant limitations.

[0010] A further problem is that, in known valves, the applied pressure always acts on the actuarial member, at least partially, even when the valve is closed. Because the actuarial member is pressed against the valve seat at its end face, the applied pressure effectively acts on the actuarial member as well, additionally pressing it against the valve seat when the valve is closed. This is true even for coaxial valves where the pressure load is almost eliminated. This means that, in some cases, a high switching force or high switching pressure is required to reopen the valve. This often results in increased wear, which can further adversely affect the sealing action of the valve. Furthermore, the inlet and outlet of such valves are either non-replaceable or not easily replaceable. In other words, the valve inlet and outlet have a preferred flow direction.

[0011] The object of the present invention is to provide a valve that does not have the aforementioned drawbacks. In particular, the object of the present invention is to provide a valve that operates reliably with hydrogen or other fluids even under high pressure.

[0012] This problem is solved by the present invention, which provides a valve having the features of claim 1, wherein the valve has a valve seat, and the valve seat abuts against the outer circumferential surface of the operating member in a sealing manner at the first end position when the valve is closed.

[0013] The valve has a valve seat, which, when the valve is closed, abuts against the outer surface of the operating member to seal. Therefore, the sealing action does not need to be performed by contact between the operating member and the surface of the valve seat, or can be completely eliminated. Consequently, mechanical wear and abrasion of the surface of the valve seat can no longer limit and / or worsen the sealing action of the valve. Thus, the valve according to the present invention is advantageously suitable, particularly for the high pressures applied, even when using extremely light gases such as hydrogen. However, the valve or functional form according to the present invention is also suitable for other fluids, such as other gases or liquids.

[0014] Further advantages can be derived from the dependent claims.

[0015] In a particularly preferred embodiment, the valve seat is substantially a ring-shaped member, the inner diameter of which is suitable for accommodating an operating member. When the valve is switched, the operating member enters, for example, into the ring-shaped member or exits the ring-shaped member again, thereby closing or opening the valve. In this case, contact surfaces, as in the case of conventional valves, can be completely eliminated.

[0016] In an equally preferred further embodiment, the actuator is a tubular member, particularly in the form of a hollow cylinder, having a wall with two end faces and an outer circumferential surface, wherein the actuator has axially extending passages that exit outward at each end face side of the actuator. Therefore, the actuator is particularly suitable as, for example, a shaft or tube with an internally located passage, in which case the end faces of the tubular member are arranged in a ring shape around the opening of the passage.

[0017] In one embodiment, the first end of the actuator is inserted into a first cylindrical recess of the casing, sealed particularly by a sealing member, at both a first and a second terminal position, and the second end of the actuator is inserted into a second cylindrical recess of the casing, sealed particularly by a sealing member, at both a first and a second terminal position, with a connecting passage terminating within the cylindrical recess, the connecting passage connecting the recess to an inlet and an outlet. The recess in the casing may be formed, for example, by holes into which the actuator protrudes or into which the actuator is inserted.

[0018] In a particularly preferred embodiment, the end face of the actuator does not contact the inner wall of each recess at both end positions, and for this purpose, the first recess and / or the second recess each have at least one particularly conical end wall. This end wall may be located, for example, on the wall of each recess facing the actuator. The end wall may be created, for example, by a hole with a depth of several millimeters (e.g., 3-5 mm), so that the end face of the actuator is fully exposed without contacting the inner wall of the recess.

[0019] This embodiment has the significant advantage that, when the valve is closed, if the medium flows through the actuator and both end faces of the actuator are exactly the same size and shape, the pressure acts precisely and uniformly on both end faces of the actuator. Since the sealing action of the valve is guaranteed by the valve seat surrounding the actuator, none of the end faces of the actuator need to contact the valve seat. Therefore, the applied pressure acts uniformly on the entire actuator, so the actuator is not pushed in a preferred direction. As a result, the actuator is 100% or completely free of pressure load. Therefore, the actuator can advantageously be switched with relatively low force, even when a high pressure of, for example, 2000 bar is applied.

[0020] In a further embodiment, the valve seat is located within a first recess. The valve may be designed to be closed when an actuator passes through the valve seat and to be opened when the actuator is not located within the valve seat.

[0021] In a particularly preferred embodiment, the valve seat abuts against the outer circumferential surface of the actuator at a first terminal position to seal, and the first end of the actuator is moved axially outward from the valve seat at a second terminal position so that the passage of the actuator connects to the connecting passage. In this case, the valve is closed at the first terminal position and open at the second terminal position.

[0022] In a further preferred embodiment, the actuating member is adjustable by a drive device. This drive may be, for example, pressure-controlled by a control medium and / or electromagnetically configured.

[0023] In further embodiments, the actuarial member forms a piston, or the piston is rigidly coupled to the actuarial member, and the piston is located in a third cylindrical recess of the casing, particularly between the two recesses, separating the two working chambers so as to seal them from each other, and the piston is reciprocally movable between its terminal positions by a control medium that can be introduced into the working chambers. Switching of the valve can be performed, for example, by filling each of the working chambers with a control medium, such as a control gas. Of course, other control mediums, such as a liquid, are also possible.

[0024] When one working chamber is filled with the control medium, the piston and thus the working member are adjusted to increase the volume of the chamber. To adjust the working member in the opposite direction, the other chamber is filled with the control medium accordingly. Of course, these chambers must have corresponding inlets and outlets. Surprisingly, it has been found that even when the pressure applied to the valve is extremely high, for example, 1000, 1500, or 2000 bar, a low switching pressure of, for example, 5-10 bar is sufficient to switch the valve. This is because the working member is 100% or completely free of pressure load even when closed. Therefore, the sealing force is not important when switching the valve. The switching pressure only needs to overcome the friction of the working member and, in some cases, the spring force of the spring.

[0025] In a further embodiment, the member is in contact with the inner surface of the third recess at the first and second end positions of the actuator, respectively, such that these surfaces restrict the axial movement of the actuator. This allows the end positions of the actuator to be defined without the end face of the actuator contacting a surface inside the casing.

[0026] In further embodiments, the third recess is sealed and separated from the other two recesses by a sealing member, particularly in the form of an O-ring, a pneumatic seal edge, or a radial axial seal. For example, the working member can be partially positioned or inserted into the first, second, and third recesses. For this purpose, a dynamic sealing member must be provided to seal the recesses together. The dynamic sealing member may be any type of sealing member that satisfies the requirements for sealing action and wear resistance for each medium and each pressure. Basically, in this case, piston seals and rod seals can be considered that are fixedly positioned within the casing or fixedly positioned on the working member and are accompanied by movement.

[0027] In a particularly preferred embodiment, at least one, and more particularly two, sealing means have a support ring and a grooved ring, and the operating member is adjustably positioned within the sealing means. The support ring can be positioned in particular in a recess provided for the support ring inside the casing, and the support ring may be sized to abut against the casing wall radially outward and against the operating member radially inward. This allows the support ring to support the sealing member in the form of a grooved ring on the one hand, and simultaneously form a guide for the operating member. The grooved ring can be fitted over the support ring, for example, to form a seal, while the support ring is automatically centered to hold the sealing member in place.

[0028] In essence, embodiments in which at least one sealing means is located on the operating member are also conceivable. This sealing means may be a piston seal. However, particularly when using light gases, the requirements for the surface to be sealed are extremely high. Therefore, in this embodiment, a recess within which the piston seal moves is extremely important.

[0029] In further embodiments, the groove ring is made of polyurethane, for example, H-ECOPUR. Such groove rings are commercially available and therefore readily available.

[0030] In a particularly preferred embodiment, the valve seat is made of a high-performance plastic, for example polyaryl ether ketone (PEEK), or comprises a component made of such a high-performance plastic. Such a material is particularly suitable for valve seats, because such a material meets the high requirements for processability, wear and sealing performance even in hydrogen applications.

[0031] In a further embodiment, the valve is a coaxial valve, i.e., the inlet and the outlet are located on a common axis. Of course, the inlet and / or outlet of the valve or the corresponding passages must in this case optionally be deflected to enable coaxial connection. However, particularly in the case of light gases such as hydrogen, such a deflection has little or no disadvantage with respect to the performance of the valve.

[0032] In a further embodiment, the inlet can also be used as the outlet, and in this case the outlet can be used as the inlet. This is enabled in particular by a completely pressure-unloaded valve configuration, because the actuating member is not pressed into a specific position by the applied pressure in the closed valve state. In such a configuration, back pressure and sealing force are no longer relevant. Therefore, with this valve, it does not matter on which side of the valve the pressure is applied. In this way, the valve can be used very flexibly; for example, incorrect installation with reversed flow direction cannot occur if the valve is appropriately configured.

[0033] In a further embodiment, the valve additionally has at least one passage that terminates in the region of a recess between two sealing means, and this passage is used for leak monitoring and measurement. Thereby, leakage can be detected, and if a plurality of passages each corresponding to exactly one sealing member are used, the leakage can be associated with a specific sealing member.

[0034] In further embodiments, the valve has a spring indirectly or directly acting-connected to the actuarial member, which holds the actuarial member in a first or second terminal position when no force is applied to the actuarial member by the drive mechanism, or only a small force is applied to it. In this case, the force means the force applied to the actuarial member to switch the valve. In particular, this force may be the pressure of a control medium acting on the piston of the actuarial member.

[0035] Depending on the design and arrangement of the spring, the valve may be normally closed or normally open. Of course, the valve may also have an end position switch to monitor the valve's position.

[0036] In further embodiments, the drive device may additionally or alternatively have magnets, thereby allowing the valve to be opened and closed by (electro)magnets as well. Of course, in such configurations, the valve can be designed to be either an unenergized open type or an unenergized closed type.

[0037] The valve according to the present invention may have three or more ports and three or more switching positions. Therefore, the inlet and / or outlet may be formed by at least two ports. For example, the valve may have a total of three ports, in which case one port forms the inlet and two ports each form one outlet. The valve may have two or more inlets and / or two or more outlets, in which case the inlets and / or outlets may be connected to each other in different ways.

[0038] Various configurations of the valve can be formed by changing the sealing means, sealing members, the number and arrangement of ports, and the various controllable switching positions of the operating member. For example, one port may form an inlet and two ports may form outlets, in which case the valve is closed at one switching position of the operating member. At a second switching position, both ports forming the outlets may be open. In this example, the valve is formed as a possible 3-port 2-position switching valve.

[0039] However, it is also possible for one port to form an inlet and two ports to each form an outlet, with the operating member connecting the inlet to the first outlet at the first switching position and the inlet to the second outlet at the second switching position. This valve is also a 3-port 2-position switching valve, but it is a different embodiment.

[0040] In the last embodiment, a third switching position in which the valve is closed can also be provided. In this case, the valve is a 3-port 3-position switching valve.

[0041] It is also possible for two ports to form an inlet and one port to form an outlet. In this case, of course, various switching positions with various port connections are possible. Four or more ports, for example, a 5-port 3-position switching valve, are also possible.

[0042] The operating member can also be configured in various ways. For example, the operating member may have one or more openings in its wall, for example, in the form of holes. These lateral openings can function as branching points in the passage of the operating member, providing options for additional, more complex connections to other ports. Thus, each opening can correspond to one or more ports, thereby providing the possibility of further switching positions for various different configurations.

[0043] The operating member may have, for example, two or more openings, each opening assigned to exactly one port. In the first switching position, for example, the first port may be open, and in the second switching position, the second port may be open. This, in particular, can reduce the required switching distance that the operating member must travel and / or allow multiple ports to be connected.

[0044] Furthermore, the operating member may have multiple openings, in which case at least two openings may have different cross-sections. Thus, the flow rate through one or more ports can be varied by allowing one opening to allow a higher flow rate and the other opening to allow a lower flow rate. These openings may also correspond to one or more or the same port.

[0045] In some embodiments, the operating member may have at least one opening having a non-rotationally symmetric cross-section. Non-rotationally symmetric in this context should be understood in particular as a cross-section that changes with respect to the corresponding port each time.

[0046] Therefore, the opening may, for example, have a substantially triangular cross-section, in which case, at the first switching position, only the tip of the triangle releases fluid flow to the corresponding port. As the operating member moves, the triangular cross-section releases an increasingly larger flow opening, so that the flow rate to this port increases. In particular, a metering valve and / or control valve can be realized in this way. Furthermore, the operating member formed as a control tube may be moved axially as well as rotated about its longitudinal axis to take on different switching positions, in which case a corresponding drive device and, if applicable, a transmission device must be provided. For example, the control tube may have a partially or completely annular toothed row on its circumferential outer wall, and this toothed row allows the control tube to rotate about its axis. Additionally, an axial adjustment drive device can be provided.

[0047] The present invention further relates to a valve seat for a valve according to the present invention.

[0048] In a particularly preferred embodiment, the valve seat is substantially ring-shaped, and in particular has a mirror-symmetric cross-section. The substantially ring-shaped nature of the valve seat allows the actuator to enter the valve seat without contacting the valve seat surface. Since the valve seat may also have a mirror-symmetric cross-section, it can operate similarly on both sides.

[0049] In another preferred embodiment, the valve seat is a sealing member.

[0050] In further embodiments, the outer circumferential surface of the valve seat has an annular groove, which is used to accommodate a sealing means, such as an O-ring. This sealing means can, for example, improve the sealing action and / or hold the valve seat in place.

[0051] In a particularly preferred further embodiment, at least one, and especially both, axial end faces of the valve seat have a recess or groove, particularly an annular one. This groove distributes the pressure applied to the valve seat radially inward and outward, thereby assisting the sealing action when pressure is applied. This prevents the pressure from acting on the valve seat only axially, thereby preventing the valve seat from potentially being crushed or slipping. In the case of a mirror-symmetric valve seat, the grooves can similarly be arranged on both end faces of the valve seat.

[0052] In further embodiments, a seal lip is formed by a recess or groove. In this case, the seal lip can be pressed against the operating member or casing wall by applied pressure in a predetermined manner, which further assists the sealing action.

[0053] In a further preferred embodiment, the valve seat has at least one, particularly two, annular projections on the radially inward side that form a sealing projection. The sealing projection may be positioned such that pressure applied to its end face through a recess presses the sealing projection against the actuating member, thereby further assisting the sealing action.

[0054] In particularly preferred embodiments, the valve seat is manufactured from a high-performance plastic, especially PEEK. This material meets high requirements for sealing properties, strength, processability, and coefficient of friction, making the valve seat particularly suitable for high-pressure hydrogen applications.

[0055] The present invention further relates to a support ring for a valve according to the present invention.

[0056] In one embodiment, the support ring has an axially extending annular first segment having at least one face located radially inward and at least one face located radially outward, the radially inward face extending substantially parallel to the longitudinal axis of the support ring, and the at least one radially outward face extending at an angle greater than 0° with respect to the longitudinal axis of the support ring, particularly between 10° and 80°. An angle of 45° ± 10° is particularly suitable. Support rings of this type are known and commercially available. In particular, support rings of this type are available together with groove rings that fit this support ring. According to the present invention, the support ring additionally has at least one axially extending second segment, particularly cylindrical, the outer diameter of the second segment is greater than the maximum outer diameter of the first segment.

[0057] This at least second section of the support ring may be sized to abut against, for example, the casing wall on the outside, and against the operating member on the inside. Thus, in addition to its support and holding functions for the groove ring, the support ring also performs a guiding function for the operating member.

[0058] In further embodiments, the first section of the support ring can be inserted into or pressed into the housing of the groove ring. In particular, the first section can be sized to be used with conventional commercially available groove rings.

[0059] In a further embodiment, the second section has a first contact surface for contacting the groove ring. This allows the support ring to also support the fitted groove ring in the axial direction.

[0060] In a further embodiment, the second section has a second contact surface for contacting a wall within the valve casing. This allows the support ring to be supported axially by the casing wall.

[0061] Several embodiments of the present invention will be described in detail below with reference to the drawings. Of course, the present invention is not limited to the illustrated embodiments. [Brief explanation of the drawing]

[0062] [Figure 1a] This is a cross-sectional view of the valve according to the present invention. [Figure 1b] This figure shows the same valve as in Figure 1a in the open position. [Figure 2] This is a cross-sectional view showing the valve shown in Figure 1 from a different perspective. [Figure 3] Figure 1 is a detailed view of the valve seat and sealing means of the valve shown. [Figure 4] This figure shows the external appearance of the valve shown in Figure 1. [Figure 5a] This is a cross-sectional view of the valve seat according to the present invention. [Figure 5b] Figure 5a is a perspective view of the valve seat. [Figure 6a] This is a cross-sectional view of a sealing means comprising a support ring and a groove ring according to the present invention. [Figure 6b] Figure 6a is a perspective view of the support ring. [Figure 7a] This is a cross-sectional view showing a further valve according to the present invention from two different viewpoints. [Figure 7b] This is a cross-sectional view showing the valve shown in Figure 7a in the open position. [Figure 8a] This diagram shows a schematic embodiment of a valve formed as a 3-port, 3-position switching valve, with one switching position. [Figure 8b]This diagram shows a schematic embodiment of a valve formed as a 3-port, 3-position switching valve, with one switching position. [Figure 8c] This diagram shows a schematic embodiment of a valve formed as a 3-port, 3-position switching valve, with one switching position. [Figure 9a] This figure shows a schematic embodiment of a valve formed as a 3-port, 3-position switching valve, equipped with an operating member having a hole in the wall, in one switching position. [Figure 9b] This figure shows a schematic embodiment of a valve formed as a 3-port, 3-position switching valve, equipped with an operating member having a hole in the wall, in one switching position. [Figure 9c] This figure shows a schematic embodiment of a valve formed as a 3-port, 3-position switching valve, equipped with an operating member having a hole in the wall, in one switching position. [Figure 10a] This diagram shows the configuration of an operating member with openings of different sizes at a single switching position. [Figure 10b] This diagram shows the configuration of an operating member with openings of different sizes at a single switching position. [Figure 11a] This figure shows a further embodiment of an operating member having a non-rotationally symmetric opening. [Figure 11b] This figure shows a further embodiment of an operating member having a non-rotationally symmetric opening. [Figure 12a] This figure shows a further embodiment of an operating member that can be brought to different switching positions by rotation. [Figure 12b] This figure shows a further embodiment of an operating member that can be brought to different switching positions by rotation. [Figure 12c] This is a schematic diagram showing a sealing mechanism for a rotating working member.

[0063] Figure 1a shows a cross-sectional view of valve 1 according to the present invention. Valve 1 has a casing 2 consisting of multiple parts, which has an inlet I and an outlet O. An operating member 3 in the form of a hollow cylinder is disposed in valve 1. The operating member has a wall 3'' with an outer peripheral surface 3'. A passage 3a is provided inside the operating member 3, so that a medium can pass through the operating member 3. In the illustrated configuration, valve 1 is closed and the operating member 3 is in the first terminal position. At this time, the first end 3b of the operating member 3 is located in the first recess H1 of the casing 2. Correspondingly, the second end 3c of the operating member 3 is located in the second recess H2 of the casing 2. The recesses H1 and H2 are connected to the outlet O or inlet I via passages K1 and K2.

[0064] The first end 3b of the actuator 3 is located on an annular valve seat 4, which seals the passage 3a of the actuator 3 to the outlet O. In other words, in this case, the valve seat 4 forms a seal. Therefore, the valve 1 is closed and the medium cannot flow from the inlet I to the outlet O. The illustrated valve 1 is formed laterally, that is, the outlet O and inlet I are not located on a common axis. To reiterate, the valve may be designed as a coaxial valve. In this case, designing it as a coaxial valve requires appropriately deflecting the orientation of either the inlet I or the outlet O. As already mentioned, deflection has few disadvantages, or in some individual cases, the advantages of coaxial arrangement may outweigh the disadvantages of deflection, especially when using lightweight gases such as hydrogen.

[0065] Since the recess H1 has a conical end wall H1' formed by a hole, the first end face F1 of the actuator 3 is not in contact with the inner wall H1'' of the recess H1 and is substantially exposed. Pressure P is applied to the inlet I of the valve 1. Because the end face F1 of the actuator 3 is exposed, this pressure P acts uniformly on the end face F1 and the opposite second end face F2 of the actuator 3. Therefore, the net pressure applied to the actuator 3 in the axial direction is zero, i.e., zero in both the illustrated closed state and the not-illustrated open state of the valve 1. Thus, the actuator 3 is free from pressure load at all times with respect to the applied pressure P.

[0066] The actuator 3 further includes a piston 5 for adjusting the actuator 3. The piston 5 is adjustablely positioned within a third recess H3 of the casing 2 and is held in the illustrated first terminal position by a spring 6. In other words, the illustrated valve 1 is normally closed. Of course, the valve 1 may also be designed to be normally open. The piston 5 is in contact with the casing wall 2a, and this casing wall thus defines the first terminal position of the actuator 3.

[0067] Along the operating member 3, separate sealing means are arranged to seal the recesses H1, H2, and H3 from one another. The sealing means shown in Figure 1 is fixedly positioned within the casing 2, so the sealing means is stationary relative to the operating member 3. Of course, a sealing means that is fixedly positioned on the operating member 3, for example in the form of a piston seal, is also conceivable.

[0068] The illustrated sealing means is a sealing means 7 comprising a support ring 7a and a groove ring 7b according to the present invention. Furthermore, the illustrated valve 1 has another sealing means in the form of O-rings 8, 8'. Between the O-ring 8 and the sealing means 7 are each one passage 9 for monitoring and measuring leaks. The O-ring 8' is positioned on the piston 5 and seals the two working chambers A1, A2 of the recess H3 to each other.

[0069] Figure 1b shows the same valve as in Figure 1a, but the actuarial member 3 is in the second terminal position. Therefore, valve 1 is open. For this purpose, the pressure medium is introduced into the working chamber A1 of recess H3, thereby causing piston 3 to slide against the spring force of spring 6 inside the third recess H3 until piston 5 contacts the casing wall 2b. In this case, the working chamber A2 of recess H3 is reduced. The first end 3b of the actuarial member is moved outside the valve seat 4, thereby connecting the passage 3a of actuarial member 3 to the outlet O. Therefore, the valve is open.

[0070] Figure 2 shows the same valve 1 as in Figure 1a, but from a different side. The drawing shows two passages 10a and 10b used to fill the working chambers A1 and A2 of the recess H3 with a control medium. In the illustrated position, valve 1 is closed. To open it, a control medium, such as gas, is sent through passage 10a, causing the piston 5 to slide axially against the spring force of spring 6 until the piston disc 5 contacts the wall 2b of casing 2, as shown in Figure 1b. This defines the second terminal position of the actuarial member 3. As the piston 5 moves, the pressure medium must simultaneously be expelled from the working chamber A2 through passage 10b. To close valve 1, it is sufficient to simply cut off the pressure from passage 10a, causing spring 6 to slide the piston 5 to its starting position, or additionally, pressurizing the control medium into passage 10b to assist or accelerate the closing process. It is clear that passages 10a and 10b can, or must, function as both inflow and outflow points.

[0071] Figure 3 shows a detailed view of the valve seat 4 and the actuator 3 positioned inside it. The actuator 3 is in contact with the valve seat 4 at its outer circumferential surface 3'. In the illustrated closed position, the valve seat 4 seals the passage 3a to the outlet O. At the same time, the conical end face wall H1' exposes the first end face F1. Therefore, the pressure P applied to the inlet I acts uniformly on the first end face F1 and the opposite end face F2 (not shown). Consequently, the actuator 3 is not subjected to pressure load even in the closed position of the valve 1, and thus a relatively small switching force is sufficient to switch the valve even when high pressure is applied. Since the actuator 3 does not contact the surface of the valve seat as in previously known solutions, the problem of wear on the contact surface is eliminated. Therefore, the valve 1 according to the present invention is suitable for particularly light gases such as hydrogen, and is especially suitable under high pressure. As described above, when the actuarial member 3 is adjusted and moved outside the valve seat 4, the outlet O is connected to the passage 3a and, consequently, to the inlet I, and thus the valve 1 is opened.

[0072] The valve seat 4 has an annular groove 4a that functions to accommodate an O-ring (not shown), which stabilizes the valve seat 4 and improves the sealing action. Annular recesses in the form of grooves 4b are provided on both end faces of the valve seat 4, so that these end faces have seal lips 4c. When pressure is applied to the end faces, the pressure is redirected toward the seal lips 4c, thereby supporting the sealing action by pressing the seal lips 4c against the circumferential surface 3' of the actuating member 3 or against the wall of the casing 2.

[0073] Furthermore, the ends 3b and 3c of the operating member 3 have a conical section 3d, which prevents damage to the valve seat 4 when the operating member 3 moves in and out.

[0074] Also shown in Figure 3 is a sealing means 7 comprising a support ring 7a and a grooved ring 7b fitted over it. The support ring 7a has a section 7g having an outer diameter larger than the outer diameter of the conical section 7c located to its side. Thus, the support ring 7a acts as a guide on one side and as a support for the grooved ring 7b on the other side. The exact configuration of the support ring will be described in more detail in relation to Figures 6a and 6b.

[0075] The grooved ring 7b is a seal consisting of an H-ECOPUR with two seal lips. When the valve 1 is opened, the sealing means 7 seals the recess H1 against the recess H3, in which case the seal lips are pressed apart by the pressure. At the same time, the support ring 7a stabilizes the grooved ring 7b so that the grooved ring does not slip or compress. This configuration has been shown to withstand thousands of switching cycles and operate reliably, especially under extremely high pressures of over 1000 bar, even when using hydrogen.

[0076] Figure 4 shows an external view of a valve 1 comprising a cylindrical casing 2 and an inlet I and an outlet O. Control ports leading to passages 10a and 10b are visible on the side wall of the casing 2. Additionally, a contact 11 for a terminal position switch (not shown) is also illustrated.

[0077] Figure 5a shows a cross-sectional view of the valve seat 4 according to the present invention. The valve seat 4a has an annular groove 4a on its outer circumferential surface for accommodating an O-ring. Both end faces also have annular recesses 4b for distributing applied pressure. These recesses 4b are positioned such that the end faces of the valve seat have seal lips 4c, and when pressure is applied, these seal lips are pressure-loaded, assisting the sealing action of the valve seat 4. Furthermore, the valve seat 4 has two projections 4d on the radially inward side, which form sealing protrusions that contact the actuator 3 when installed. When pressure is applied, the sealing protrusions are pressed against the circumferential surface 3' of the actuator 3.

[0078] Figure 5b shows a perspective view of the valve seat 4 according to the present invention.

[0079] Figure 6a shows a cross-sectional view of the support ring 7a of the sealing means 7 according to the present invention. Next to it is shown a grooved ring 7b, which is inserted into the support ring 7a when assembled. The support ring 7a has a first section 7c that extends in the axial direction. This section 7c is inserted into the housing section 7d of the grooved ring 7b. The first section 7c further has an inclined surface 7e on its radially outward side. On its radially inward side, the support ring 7a has a surface 7f that extends parallel to the longitudinal axis of the support ring 7a. This surface 7f is in contact with the outer circumferential surface 3' of the operating member 3.

[0080] Additionally, the support ring 7a has a second section 7g according to the present invention, the outer diameter of this second section is larger than the maximum outer diameter of the first section 7c. The second section 7g is dimensionally set to form a guide between the casing wall and the operating member 3. The second section 7g further has a surface 7h that abuts against the casing wall and a surface 7i that abuts against the groove ring 7b. Due to the above features, the support ring is automatically centered between the casing 2 and the operating member 3 and at the same time stabilizes the groove ring 7b, so that the groove ring forms a reliable seal. The groove ring 7b is a commercially available groove ring with two annular seal lips 7j.

[0081] Figure 6b shows a perspective view of the support ring 7b according to the present invention.

[0082] Figure 7a shows another embodiment of the valve 1 according to the present invention in two different cross-sectional views. These features are almost identical to the embodiment shown in Figure 1a. Since only the inlet I is located on the opposite side of the valve 1, the distance between the inlet I and the outlet O is significantly shorter than in the embodiment shown in Figure 1a. Accordingly, the second recess H2 of the casing 2 has a conical end wall H2', thereby eliminating the pressure load on the actuator 3 at the second terminal position, i.e., in the open state. Thus, the end face F2 of the actuator 3 is exposed at the second terminal position. The terminal position switch 11a detects whether the valve is closed or open using the contact 11.

[0083] Figure 7b shows the valve in the open position as in Figure 7a. The actuator 3, along with the piston 5, has been moved to the second terminal position of the piston, similar to the position shown in Figure 1b. The inlet I and outlet O are directly connected to each other via the recess H1 in the illustrated position. That is, the medium does not need to first pass through the passage 3a of the actuator 3 to reach the outlet O from the inlet I. The second end face F2 of the actuator 3 remains exposed based on the conical end wall H2' of the recess H2 and is not in contact with the inner wall H2''. Therefore, there is no pressure load on the actuator 3 even in this position. The terminal position switch 11a is now connected to the other contact, thereby detecting that the valve 1 is open.

[0084] This embodiment has the advantage that the nominal width of the valve is determined by the recess H1 rather than by the passage 3a provided in the actuating member 3. The recess H1 has a diameter corresponding to the outer diameter of the actuating member 3. Therefore, the nominal width of the illustrated valve no longer depends on the control pipe 3 or its inner diameter. In the embodiment shown in Figure 1a, if it is desired to increase the size of the passage 3a in the actuating member in order to increase the nominal width of the valve, the actuating member 3 must be made correspondingly more stable and its outer wall 3'' correspondingly thicker in order to prevent the control pipe from breaking or deforming. As a result, the control pipe and thus the valve become extremely large, expensive, impractical, or in some cases, completely unmanufacturable.

[0085] In the illustrated embodiment, passages K1 and K2 are narrower than recess H1. Therefore, the flow velocity inside the valve is reduced. Note that passage 3a inside the actuator 3 is still necessary to eliminate the pressure load on the actuator 3. However, the diameter of passage 3a is not important. In particular, passage 3a is not important to the nominal width of the valve.

[0086] Another possible embodiment of the pressure-free valve 100 according to the present invention is schematically shown in Figures 8a to 8c. The actuating member 3, valve seat 4, sealing member 8, and sealing means 7, 7a, 7b are, in principle, the same as the corresponding components described above in the embodiments described above. The illustrated embodiment differs from the embodiment shown in Figure 1a in that it is a 3-port 3-position switching valve, that is, it has three ports A, B, and C and three switching positions. Port A can function, for example, as an inlet I, and both ports B and C can function as outlets O. The passage K is closed at both ends E.

[0087] The first switching position is shown in Figure 8a, and the valve 100 is closed at this switching position. Pressure P is applied to the inlet O (port A), and this pressure is distributed from the left side of the casing 2 to the right side of the casing via the tubular operating member 3, and is applied to the valve seat 4 on the right side of port C. Pressure P0 is applied to ports B and C, in which case P > P0 holds. Therefore, the valve seat 4 seals port C to port A in the manner described in relation to the previous embodiment, so the fluid cannot flow from inlet I to outlet O.

[0088] Similarly, valve seat 4 is located adjacent to port B on the left side, where the same pressure P from port A is applied, sealing port B to port A. Between port B and port C, instead of valve seat 4, a sealing means 7 of the type described above is located, consisting of a support ring 7a and a groove ring 7b, within which the operating member 3 is supported to slide or is adjustable. In this case, the operating member 3 is located within the sealing means 7 at each switching position. Additionally, two sealing members 8 in the form of O-rings are located between ports B and C and between ports A and B. Another valve seat 4 is located next to port 4.

[0089] The operating member 3 is adjustable to two different positions by an adjustment device (not shown). The adjustment device may be any suitable adjustment device, in particular a pneumatic, hydraulic, or magnetic adjustment device. Of course, the valve 100 may be configured to be open when there is no current or closed when there is no current, depending on the structure of the adjustment device.

[0090] Figure 8b shows valve 100 in the second switching position. An adjustment device (not shown) has moved the actuarial member 3 to the right. Thus, port B is opened, while port C remains closed. Sealing of port C is achieved through the left-hand sealing means of both sealing means 7, an additional sealing member 8 between ports B and C, and the valve seat 4 to the right of port C. Thus, in the switching position shown, port A forms the inlet I, and port B forms the outlet O of valve 100.

[0091] Figure 8c shows the third switching position of valve 100. An adjustment device (not shown) moves the actuator 3 to the third position, in which port B is sealed relative to ports A and C. Thus, the fluid flow can extend from port A to port C, and port C thus forms outlet O. Accordingly, the actuator 3 is moved into the valve seat 4 on the left side in the figure. Thus, sealing of port B is achieved via the valve seat 4 on the left side and the sealing means 7 on the right side in the figure.

[0092] In all switching positions, the actuator 3 is located within both sealing means 7, or is arranged to slide longitudinally within them. In contrast, the actuator 3 is moved outside at least one valve seat 4 in each switching position.

[0093] Of course, the embodiments shown in Figures 8a to 8c may be configured as a 3-port 2-position switching valve, provided that the operating member 3 can only be adjusted between two switching positions. For example, only the two switching positions in Figures 8b and 8c may be adjustable, thereby allowing the valve 100 to switch between both ports B and C, in which case one of the ports B and C each time forms a single open outlet O at only one switching position. In this case, the valve 100 is never closed in this configuration and can switch the fluid flow from A to B or C. In this case, the middle valve seat 4 in the figure can be omitted.

[0094] Other configurations can be realized; for example, a 5-port, 3-position directional control valve is also possible. Furthermore, the arrangement and number of the valve seat 4, sealing means 7, and sealing member 8 may be changed as needed according to the pressure and port structure, and can be adapted to the situation at hand. Therefore, the illustrated embodiment is not limiting and merely provides a schematic representation of how a multi-position switching valve equipped with a valve seat 4 or sealing means 7 according to the present invention may be configured and connected.

[0095] Another possible embodiment of the valve 1000 is shown in Figures 9a and 9b. The valve seat 4, sealing means 7, and sealing member 8 are again the same components as described above. However, unlike the embodiments described above, the actuating member 3000 additionally has two holes Ha,Hb in the wall 3'' through which the fluid flow can also flow out from the side through the passage 3a.

[0096] In Figure 9a, the valve 1000 is closed. Pressure P is applied to port A, and this pressure is also directed to the right-hand section of port C through the passage 3a of the actuator 3000, as in the embodiment described above. The valve seat 4 seals one of ports B and C with respect to port A each time. Unlike the embodiment in Figures 8a to 8c, the pressure P is also distributed through an opening or hole Ha to the central region of the casing 2 located between port B and port C. Therefore, ports B and C are also sealed with respect to port A via the sealing means 7 and sealing member 8 located in this region. In particular, the two middle sealing means of the four sealing means 7 in the figure are responsible for sealing ports B and C because the groove rings 7b of these sealing means are oriented toward the pressure side P as described above. Since the actuator 3000 does not move away from the valve seat 4 on the left side of the drawing, or moves out of this switching position, at any switching position, this valve seat 4 may be replaced by the sealing means 7.

[0097] Naturally, other combinations / arrangements / numbers of the sealing member 8, sealing means 7, and valve seat 4 are conceivable, possible, and in some cases advantageous, so that the valve 1000 can be adapted to the requirements for the pressure and sealing performance used.

[0098] Figure 9b shows the same valve 1000 as in Figure 9a, but the actuarial member 3000 has been moved to a second switching position by an adjustment device not shown. Now both holes Ha and Hb are at the same height as ports B and C, so fluid flow from port A to ports B and C is possible. Thus, in the shown position, port A forms the inlet I, and ports B and C each form the outlet O for valve 1000.

[0099] Of the four sealing means 7, the two located on the outside in the figure seal port B against port C. Depending on the configuration of the ports, especially when the flow rates and applied pressures of both ports B and C are the same, these two sealing means 7 may be redundant or unnecessary and can be omitted or replaced with conventional sealing means depending on whether sealing action at this position is necessary for the function of valve 1000.

[0100] If the pressure P is extremely high, during the transition between holes Ha and Hb, the pressure P may be applied between the two sealing means 7, which are positioned adjacent to each other and rotated 180° relative to each other. In such a case, the high pressure P is applied to the side of the sealing means 7 that is not provided for this purpose, i.e., to the side of the support ring 7a, and not to the side of the groove ring 7b. A possible solution to this problem is that when such a transition occurs, the valve 1000 may be switched to a no-pressure state. It is also conceivable and possible that at least one compensatory passage X exists between these sealing means, which can compensate for or release the excess pressure P between the two adjacent sealing means 7. At least one such compensatory passage X may, and in some cases must be, closable.

[0101] In Figure 9c, the actuator 3000 is moved to the third switching position. Hole Ha is located in the same casing section as port A and therefore has no function in this switching position. Pressure is newly introduced through hole Hb into the casing section between ports B and C. Port B is sealed from port A via the valve seat 4 on the left side of the figure and by the sealing means 7 (indicated in Figure 9c) as described in relation to Figure 9a. Therefore, fluid does not flow from port A to port B.

[0102] At this switching position, flow from port A to port C is possible through the passage 3a of the operating member 3000. Therefore, at this switching position, port C forms the outlet O. Thus, the illustrated embodiment is also a 3-port, 3-position switching valve having 3 ports and 3 switching positions.

[0103] This embodiment is, of course, adaptable, and for example, the number and arrangement of ports, switching positions, sealing means, and valve seats may be changed. For example, the valve may be formed as a 3-port 2-position switching valve having only two switching positions. Valves 100, 1000 may be formed as coaxial valves with both ends E not closed. In this case, the lateral ports A, B, C can be connected or disconnected, for example, by adjusting the actuating member 3, 3000. In this case, the ends E each form a normally open inlet I or outlet O.

[0104] Examples of other possible variations of the actuator 3000' are shown in Figures 10a and 10b. For clarity, the remaining components of the valve are not shown, and the positions of ports A, B, and C are merely indicated. The actuator 3000' has multiple holes Ha', Hb', and is otherwise configured as described in the preceding embodiments. The first hole Ha' is at the height of port B in the switching position shown in Figure 10a, and the second hole is at the height of port C. Thus, the fluid flow can flow from port A to both ports B and C.

[0105] The cross-section of the first hole Ha' is larger than that of the second hole Hb'. Therefore, the flow rate to port B is greater than the flow rate to port C (indicated by arrows of different sizes).

[0106] Figure 10b shows the same operating member in a second switching position, in which case the second hole Hb' is located at the height of port B. That is, the flow rate to port B is smaller in this switching position than in the first switching position. In contrast, fluid flow from port A to port C is possible through passage 3a in this switching position, so the flow rate to port C is larger in this switching position than in the first switching position. Thus, this is a 3-port 2-position switching valve, in which case both switching positions adjust the flow rates to ports B and C. Of course, this embodiment can also be adapted to have other switching positions, for example, an additionally "closed" switching position.

[0107] Another alternative example of the actuarial member 3000'' is shown in Figures 11a and 11b. Both holes Ha'', Hb'', or openings are formed substantially triangularly, rather than being circular or rotationally symmetrical. In the switching position shown in Figure 11a, only the tip of the triangle is at the height of one of the ports B, C, respectively. Therefore, the flow rate to ports B, C is relatively small. In the switching position shown in Figure 11b, the wider end of the triangle is at the height of ports B, C, and therefore, the flow rate to ports B, C is larger. Of course, intermediate switching positions are also possible, such as the continuous stepless adjustment of the actuarial member 3000''. Therefore, various different embodiments of metering valves and control valves are possible, rather than being limited to the illustrated embodiments.

[0108] Another alternative example of the operating member 3000'' is shown in Figures 12a and 12b. Opening Ha'' consists of two holes arranged side by side in the circumferential direction. Opening Hb'' consists of a single hole. In the illustrated switching position, the upper hole of opening Ha'' in the figure corresponds to port B. For this purpose, a passage corresponding to port B may be provided in a sealing means (not shown), for example. This sealing means seals the lower hole in the figure to port B and connects the hole located above it in the figure to port B. Thus, in the illustrated switching position, port B forms an outlet O with a relatively small flow rate.

[0109] Unlike the change modes described above, the operating member 3000''' is moved to a second switching position by rotation about its longitudinal axis AX. In Figure 12b, the operating member 3000''' is in the second switching position. At this switching position, both holes of opening Ha''' correspond to port B, and in this case, the corresponding passages provided in the sealing means (not shown) must be appropriately configured to connect both holes of opening Ha''' to port B. Therefore, the flow rate to port B is greater than at the first switching position.

[0110] The second opening Hb'' corresponds to port C with its single hole in this switching position. Therefore, port C also forms outlet O in this switching position. Since this opening Hb'' has only one hole, the flow rate is smaller than that of port B. Of course, it is also possible that both openings Ha'''',Hb'''' are similarly formed, so that the valve has a closed switching position and a switching position in which both ports B and C are open. Alternatively, both openings may be similar but oriented offset from each other in the circumferential direction. In this way, the valve can have, for example, three switching positions, in which case the valve is closed in the first switching position. In the two further switching positions, one of ports B and C is open each time, and the flow rates of both ports in the switching position that is opened each time are the same.

[0111] Of course, this mode of change can also be modified and adapted to various different switching positions and port configurations.

[0112] Figure 12c schematically shows an example of a sealing means 4'' that can be used in conjunction with the actuating member 3000''. The sealing means 4'' is similar to a valve seat 4 or an annular sealing ring and is fixedly positioned in the region of port B. The sealing means 4'' has a passage 4a'' corresponding to port B. The hole H located in the actuating member 3000'', which is only schematically shown, can be connected to or sealed against the passage 4a'''' by the rotation of the actuating member 3000''''. Similar sealing means 4'', which also have passages with similar or different cross-sections, may or must be located in the region of port C.

[0113] Of course, the technical features and associated advantages described above can be combined with each other in a technically meaningful manner. Therefore, the valve according to the present invention can be adapted to a wide variety of requirements, pressures, and port combinations. Multiple inlets I may be provided instead of multiple outlets O. The valve may have multiple inlets I and multiple outlets O, and these inlets and outlets may be switchable with each other in various ways by appropriate variations of the technical features described above.

Claims

1. A valve (1,100,1000), particularly a hydrogen valve, comprising at least one inlet (I), at least one outlet (O), a casing (2), an operating member (3) disposed within the casing, the operating member (3) being adjustable to at least one first terminal position (closed) and at least one second terminal position (open), and a control device for adjusting the operating member (3), wherein the valve (1,100,1000) The valve (1) has a valve seat (4), the valve seat is in contact with the outer circumferential surface (3') of the operating member (3) so as to seal it at the first terminal position when the valve (1) is closed, and the valve (1) (1,100,1000) is characterized in that the valve (1) has a valve seat (4), the valve seat (4) is in contact with the outer circumferential surface (3') of the operating member (3) so as to seal it.

2. The valve (1,100,1000) according to claim 1, wherein the valve seat (4) is substantially a ring-shaped member, and the inner diameter of the member is suitable for accommodating the operating member.

3. The valve according to claim 1 or 2 (1,100,1000), characterized in that the operating member (3) is a tubular member having a wall (3'') having two end faces (F1, F2) and an outer peripheral surface (3'), and the operating member (3) has axially extending passages (3a) that exit outward at the end faces (3b, 3c) of the operating member (3).

4. The valve according to claim 3 (1,100,1000), characterized in that the first end (3b) of the operating member (3) is inserted into the first cylindrical recess (H1) of the casing (2) and sealed particularly by sealing members (7,8) at both the first and second terminal positions, and the second end (3c) of the operating member (3) is inserted into the second cylindrical recess (H2) of the casing (2) and sealed particularly by sealing members 7,8) at both the first and second terminal positions, and connecting passages (K1,K2) terminate within the cylindrical recesses (H1,H2), and the connecting passages connect the recesses (H1,H2) to the inlet (I) and the outlet (O).

5. The valve (1,100,1000) according to claim 4, characterized in that the end faces (F1, F2) of the operating member (3) do not contact the inner walls (H1'', H2'') of the respective recesses (H1, H2) at both end positions, and for this reason the first recess (H1) and / or the second recess (H2) each have at least one particularly conical end wall (H1', H2').

6. The valve (1,100,1000) according to claim 4 or 5, characterized in that the valve seat (4) is located within the first recess (H1).

7. The valve (1,100,1000) according to any one of claims 3 to 6, characterized in that the valve seat (4) abuts against the outer peripheral surface (3') of the operating member (3) at the first terminal position so as to seal, and the first end (3b) of the operating member (3) is moved axially out of the valve seat (4) at the second terminal position so as to connect the passage (3a) of the operating member (3) to the connecting passage (K1).

8. The valve according to any one of claims 1 to 7, characterized in that the operating member (3) is adjustable by a drive device.

9. The valve according to claim 8 (1,100,1000), characterized in that the actuating member (3) forms a piston, or a piston (5) is firmly coupled to the actuating member (3), the piston (5) is located in the casing, in particular in a third cylindrical recess (H3) located between the two recesses (H1, H2), separating the two working chambers (A1, A2) so as to seal them from each other, and the piston (5) is reciprocally movable between the terminal positions of the piston by a control medium that can be introduced into the working chambers (A1, A2).

10. The valve (1,100,1000) according to claim 9, characterized in that the member is in contact with the inner surfaces (2a, 2b) of the third recess (H3) at the first end position and the second end position of the operating member (3), respectively, such that the surfaces (2a, 2b) restrict the axial movement of the operating member (3).

11. The valve according to any one of claims 4 to 10, characterized in that the third recess (H3) is sealed and separated from the other two recesses (H1, H2) by a sealing member (8) in the form of an O-ring, a pneumatic seal edge, or a radial axial seal.

12. A valve according to any one of claims 4 to 11, characterized in that at least one, in particular two, sealing means (7) have a support ring (7a) and a groove ring (7b), and the operating member (3) is adjustablely positioned within the sealing means (7).

13. The valve according to any one of claims 4 to 12, characterized in that at least one sealing means (7) is arranged on the operating member (3), particularly in the form of a piston seal.

14. The valve (1,100,1000) according to claim 12, characterized in that the groove ring (7b) is made of polyurethane, particularly H-ECOPUR.

15. The valve (1,100,1000) according to any one of claims 1 to 14, characterized in that the valve seat (4) is made of a high-performance plastic, particularly polyaryletherketone / PEEK, or has a component made of a high-performance plastic.

16. The valve according to any one of claims 1 to 15, characterized in that the valve is a coaxial valve (1,100,1000).

17. The valve according to any one of claims 1 to 16, characterized in that the inlet (I) can also be used as an outlet (O), and in this case, the outlet (O) can be used as an inlet (I).

18. A valve (1,100,1000) according to any one of claims 1 to 17, characterized in that at least one passage (9) is provided between two sealing means (7,8) and terminates in the region of recesses (H1,H2), the passage being used for monitoring and measuring leaks.

19. A spring (6) is provided that is indirectly or directly connected to the actuating member (3), and the spring holds the actuating member (3) at the first or second terminal position when no force is applied to the actuating member (3) by the drive device, or when only a small force is applied to it, the valve according to any one of claims 1 to 18 (1,100,1000).

20. The valve (1,100,1000) according to any one of claims 1 to 19, characterized in that the drive device additionally or alternatively has a magnet.

21. The valve (100, 1000) has three or more ports (A, B, C), at least one port (A) forms an inlet (I), at least one port (B, C) forms an outlet (O), and in particular the valve is a 3-port 2-position switching valve or a 3-port 3-position switching valve, as described in any one of claims 1 to 20.

22. The valve (100, 1000) according to claim 21, characterized in that the valve (100, 1000) has three or more switching positions.

23. The valve (1000) according to any one of claims 1 to 22, characterized in that the operating member (3000, 3000', 3000'', 3000'''') has at least one opening (Ha, Hb, Ha', Hb', Ha'', Hb'', Ha'''', Hb'''') in particular in its wall (3'').

24. The valve (1000) according to claim 23, characterized in that the operating member (3000') has at least two openings (Ha', Hb'), and at least two openings (Ha', Hb') each have different cross-sectional surfaces.

25. The valve (1000) according to claim 23 or 24, characterized in that the at least one opening (Ha'', Hb'', has a non-rotationally symmetric, and in particular substantially triangular, cross-section.

26. The valve (1000) according to any one of claims 23 to 25, characterized in that the operating member (3000'') is adjustable from a first switching position to at least one second switching position by rotation about its longitudinal axis (AX).

27. The valve (1000) according to claim 26, characterized in that it is provided with a sealing means (4''') having at least one passage (4''') located inside, wherein the passage (4''') corresponds to at least one port (A, B, C).

28. The valve according to any one of claims 1 to 27, characterized in that the valve is a metering valve and / or a control valve (1,100,1000).

29. A valve seat (4) for a valve (1,100,1000) according to any one of claims 1 to 28, The valve seat (4) is substantially ring-shaped and is characterized in that it has a cross-section that is mirror-symmetrical.

30. The valve seat (4) according to claim 29, characterized in that the valve seat is a sealing member.

31. The valve seat (4) according to claim 29 or 30, wherein the outer circumferential surface of the valve seat (4) has an annular groove (4a), and the groove (4a) is used to accommodate a sealing means, in particular an O-ring.

32. The valve seat (4) according to any one of claims 29 to 31, characterized in that at least one, particularly both, axial end faces of the valve seat (4) have an annular recess or groove (4b).

33. The valve seat (4) according to claim 32, characterized in that a seal lip (4c) is formed by the recess or groove (4b).

34. The valve seat (4) according to any one of claims 29 to 33, characterized in that the valve seat (4) has at least one, particularly two, annular projections (4d) that form a sealing projection on the radially inward side.

35. The valve seat (4) according to any one of claims 29 to 34, characterized in that the valve seat (4) is made from a high-performance plastic, particularly PEEK.

36. A support ring (7a) for a valve (1,100,1000) according to any one of claims 1 to 28, having an axially extending annular first segment (7c) comprising at least one radially inward surface (7f) and at least one radially outward surface (7e), wherein the radially inward surface (7c) extends substantially parallel to the longitudinal axis of the support ring, and the at least one radially outward surface (7e) extends at an angle greater than 0°, particularly between 10° and 80°, with respect to the longitudinal axis of the support ring (7a), in the support ring (7a), A support ring (7a) is provided with at least one second section (7g) that extends in the axial direction and is particularly cylindrical, wherein the outer diameter of the second section (7g) is larger than the maximum outer diameter of the first section (7c).

37. The support ring (7a) according to claim 36, characterized in that the first portion (7c) of the support ring (7a) can be inserted into or pushed into the housing portion (7d) of the groove ring (7b).

38. The support ring (7a) according to claim 37, characterized in that the second section (7g) has a first contact surface (7i) for contacting the groove ring (7b).

39. The support ring (7a) according to any one of claims 36 to 38, characterized in that the second section (7g) has a second contact surface (7h) for contacting a wall within the casing (2) of the valve (1).

Images