Pressure-relieved valve

Abstract

The invention relates to a valve (1), in particular a hydrogen valve, having at least one inlet (I) and at least one outlet (O), a housing (2) and an actuator (3) arranged therein, wherein the actuator (3) can be moved into at least one first end position (valve closed) and into at least one second end position (valve open), and having a control device for moving the actuator (3), wherein the valve (1) has a valve seat (4) which, in the first end position, in which the valve (1) is closed, sealingly rests against an outer lateral face (3') of the actuator (3).

Description

[0001] Friedrich Müller Am Schlossgarten 1 74196 Neuenstadt

[0002] Pressure-relieved valve

[0003] The present invention relates to a valve, in particular a hydrogen valve, comprising at least one inlet and at least one outlet, a housing, and an actuator arranged therein, wherein the actuator is adjustable to at least one first end position (valve closed) and to at least one second end position (valve open), and comprising a control device for adjusting the actuator. The invention also relates to a valve seat and a support ring for such a valve.

[0004] Valves and coaxial valves have long been known and available on the market. Common coaxial valves typically feature an adjustable actuator in the form of a shaft or tube through which the medium to be controlled flows. In these conventional designs, the actuator interacts with a valve seat, against which a face of the actuator rests. Sealing is achieved by the control tube resting against the valve seat. For this purpose, the valve seat has a surface against which the actuator is pressed when the valve is closed.

[0005] For example, from DE 100 51 492 A1 a quantity control valve in the form of a coaxial valve with a control tube and a valve seat is known, in which a control tube is pressed onto a substantially flat valve seat in order to close the valve.

[0006] However, there are different designs of valve seats. For example, DE 101 08 492 A1 describes another coaxial valve with an actuator that interacts with a valve seat with a rounded seat surface. The known valves have in common that the seal is created by the actuator contacting the valve seat. For this purpose, the end face of the actuator is designed differently depending on the area of ​​application and the material of the valve seat. Depending on the application, the aim is to ensure that the control tube is as pressure-relieved as possible in every position. For this purpose, the cross-section of the end face can, for example, be designed to taper to a point in the form of a collar, the tip of which rests against a surface of the valve seat. This leaves an inclined section of the collar free, allowing the ambient pressure to act on this inclined surface.Since, due to the principle, part of the front surface must still rest on the valve seat, known coaxial valves are only approximately and not completely pressure-relieved.

[0007] Further complicating the situation is the fact that the collar can be designed differently depending on the valve seat material. For example, the tip of the face can also be manufactured with an approximately round radius. Depending on the valve seat material, particularly its hardness, the tip can penetrate more or less deeply into the valve seat or deform elastically upon contact. All of this affects the precise contact point and influences the switching and sealing behavior of the valve.

[0008] This results in the further disadvantage that the tip can deform depending on the applied pressure in the valve. For the collar or the exact contact point on the valve seat, it is generally important on which side of the control tube the pressure is applied. While the control tube can be almost (but not completely) pressure-relieved on one side, it is subject to strong pressure on the other. Depending on the design of the collar or the control tube, the contact point moves due to the applied sealing force or the deformation of the tip. This means that coaxial valves usually have a prescribed flow direction and thus a fixed installation direction and / or are only partially backpressure-tight.

[0009] Another disadvantage of the known solutions is that the point at which the actuator comes into contact with the valve seat is subject to wear. This applies particularly to very pointed end surfaces of the actuator and to particularly inelastic and / or hard valve seat materials. In order for the seal to function reliably even with hard materials, the control tube must sometimes be pressed very tightly onto the seat. However, this is only possible up to a certain point, as otherwise the control tube acts like a punching tool and destroys either the valve seat or the control tube tip. Where the actuator comes into contact with the contact surface of the valve seat when the valve is switched, microscopic wear and / or damage can also occur due to mechanical stress on the material. This has a detrimental effect on the sealing effect of the valve, resulting in a deterioration in the overall performance of the valve.This is particularly detrimental if the valve is intended for use with very light gases such as hydrogen. The extremely small hydrogen atoms or hydrogen molecules can penetrate even the smallest damage and leaks once the valve seat shows a certain degree of wear. The valve will then leak and is therefore unsuitable for such applications.

[0010] However, hydrogen is currently becoming increasingly important, not least due to the development of new propulsion technologies in the automotive sector. As an extremely light gas, hydrogen places particularly high demands on the valves used. This applies particularly when used at high pressures such as 500, 1000, 1500 bar, or even higher. In this case, even the smallest leaks between the actuator and the valve seat cause the valve to no longer be leak-tight. Thus, high hydrogen pressures cannot currently be handled with existing valves, or only with significant limitations.

[0011] To make matters worse, with existing valves the applied pressure always acts at least partially on the actuator when the valve is closed. Because the actuator is pressed against a valve seat at its front, the applied pressure also effectively acts on the actuator and presses the actuator additionally against the valve seat when the valve is closed. This is even the case with almost pressure-balanced coaxial valves. This may require high switching forces or high switching pressures to open the valve again. This can sometimes result in increased wear, which can further detrimentally affect the sealing effect of the valve. In addition, the outlet and inlet of such valves cannot be interchanged, or only with difficulty. This means they have a preferred flow direction.

[0012] One object of the present invention is to provide a valve that does not have the aforementioned disadvantages. In particular, one object is to provide a valve that operates reliably even at high pressures, even with hydrogen or other fluids.

[0013] This object is achieved according to the invention with a valve having the features of claim 1 in that the valve has a valve seat which, in the first end position in which the valve is closed, bears sealingly against an outer circumferential surface of the actuator.

[0014] Because the valve has a valve seat that forms a seal against an outer surface of the actuator when the valve is closed, the sealing effect does not have to be achieved by the actuator contacting a surface of the valve seat, or the actuator contacting a surface of a valve seat can be dispensed with entirely. Thus, mechanical wear and tear on the surface of the valve seat can no longer limit and / or impair the sealing effect of the valve. Thus, the valve according to the invention is also advantageously suitable for high applied pressures, in particular when using very light gases such as hydrogen. However, the valve according to the invention and its mode of operation are also suitable for other fluids such as other gases or liquids.

[0015] Further advantages arise from the subclaims.

[0016] In a particularly preferred embodiment, the valve seat is a substantially annular body whose inner diameter is suitable for receiving the actuator. The actuator can, for example, be moved into or out of the annular body when the valve is switched, thereby closing or opening the valve. A contact surface as in conventional valves can then be dispensed with entirely. In a further, likewise preferred embodiment, the actuator is a tubular body, in particular in the form of a hollow cylinder, which has a wall with two end faces and an outer surface, wherein the actuator has an axially extending channel which exits at each of the end faces of the actuator.A particularly suitable actuator is, for example, a shaft or a tube with an internal channel, in which the end faces of the body are arranged in a ring around the openings of the channel.

[0017] In one embodiment, the first end of the actuator is sealingly engaged, in particular by means of seals, in a first cylindrical recess of the housing in both the first and second end positions, and the second end of the actuator is sealingly engaged, in particular by means of seals, in a second cylindrical recess of the housing in both the first and second end positions. Connecting channels terminate in the cylindrical recesses and connect the recesses to the inlet and the outlet. The recesses in the housing can be created, for example, by bores into which the actuator projects or in which the actuator is inserted.

[0018] In a particularly preferred embodiment, the end faces of the actuator are not in contact with the inner wall of the respective recess in either end position, wherein for this purpose, in particular the first recess and / or the second recess each have at least one, in particular conical, end wall. The end wall can be arranged, for example, on a wall of the respective recess opposite the actuator. The end wall can be created, for example, by a bore a few millimeters (e.g., 3-5 mm) deep, so that the end face(s) of the actuator do not come into contact with the inner wall of the recess, but are completely exposed.

[0019] This design has the significant advantage that when the valve is closed, the medium flows through the actuator and the pressure acts exactly the same on both end faces of the actuator, provided the end faces are of exactly the same size and type. Since the sealing effect of the valve is ensured by the valve seat surrounding the actuator, none of the end faces of the actuator needs to come into contact with a valve seat. The applied pressure thus acts evenly on the entire actuator, so that the actuator is not forced in a preferred direction. The actuator is thus 100% or completely pressure-relieved. This means that the actuator can advantageously be switched with comparatively low forces even at high applied pressure, e.g., 2000 bar.

[0020] In a further embodiment, the valve seat is arranged in the first recess. The valve can be designed such that the valve is closed when the actuator passes through the valve seat and is open when the actuator is not arranged in the valve seat.

[0021] In a particularly preferred embodiment, the valve seat in the first end position rests sealingly against the outer surface of the actuator, and the first end of the actuator is displaced axially out of the valve seat in the second end position, such that the channel of the actuator communicates with the connecting channel. The valve is then closed in the first end position and open in the second end position.

[0022] In a further preferred embodiment, the actuator is adjustable by means of a drive. This drive can, for example, be pressure-controlled by means of a control medium and / or be electromagnetic.

[0023] In a further embodiment, the actuator forms a piston or a piston is firmly connected to the actuator and the piston is arranged in a third cylindrical recess of the housing, which recess is located in particular between the two recesses and separates two working chambers from one another in a sealing manner, wherein the piston can be adjusted back and forth between its end positions by means of a control medium that can be introduced into the working chambers. The valve can then be switched, for example, by each of the two working chambers being able to be filled with a control medium, such as a control gas. Other control media, such as a liquid, are of course also conceivable. If one of the working chambers is filled with a control medium, the piston and thus the actuator moves in such a way that the volume of the chamber increases.To move the actuator in the opposite direction, the other chamber is filled with the control medium. Naturally, the chambers must have appropriate inlets and outlets. Surprisingly, it has been found that even at very high pressures applied to the valve, such as 1000, 1500, or 2000 bar, a low switching pressure of, for example, 5-10 bar is sufficient to switch the valve. This is primarily due to the fact that the actuator is 100% or completely pressure-relieved even when closed. Therefore, the sealing force plays no role in switching the valve. The switching pressure only has to overcome the friction of the actuator and, if necessary, the spring force of a spring.

[0024] In a further embodiment, the body rests against a surface within the third recess in the first end position of the actuator and in the second end position of the actuator, such that these surfaces limit the axial adjustability of the actuator. In this way, the end positions of the actuator can be defined without the actuator coming into contact with a surface with its end faces within the housing.

[0025] In a further embodiment, the third recess is sealed off from the other two recesses by means of seals, in particular in the form of an O-ring, a pneumatic sealing edge, or a radial shaft seal. For example, the actuator can be partially arranged or embedded in the first, second, and third recesses. For this purpose, dynamic seals must be present to seal the recesses from one another. These can be any type of seal that meets the sealing effect and wear requirements for the respective medium and pressure. Piston and rod seals are generally conceivable, which are either permanently arranged in the housing or permanently arranged on the actuator and are moved along during adjustment.In a particularly preferred embodiment, at least one, in particular two, sealing means comprises a support ring and a grooved ring, wherein the actuator is adjustably arranged in the sealing means. The support ring can in particular be arranged in a recess provided for this purpose within the housing and be dimensioned such that it rests both radially outwardly against a housing wall and radially inwardly against the actuator. As a result, the support ring can support the seal in the form of a grooved ring and at the same time forms a guide for the actuator. The grooved ring can, for example, be slipped onto the support ring and forms the seal, while the support ring automatically centers itself and holds the seal in position.

[0026] In principle, an embodiment is also conceivable in which at least one sealing means is arranged on the actuator. This could be a piston seal. However, especially when using thin gases, the requirements for the sealing surface are very high. In this embodiment, great importance must therefore be attached to the recess in which the piston seal is adjusted.

[0027] In another embodiment, the grooved ring is made of a polyurethane such as H-ECOPUR. Such grooved rings are commercially available and therefore easy to obtain.

[0028] In a particularly preferred embodiment, the valve seat is made of a high-performance plastic such as polyaryletherketone (PEEK), or has a component made of such a high-performance plastic. This material is particularly suitable for the valve seat because it meets the high requirements for processability, wear resistance, and sealing effectiveness, even in hydrogen.

[0029] In another embodiment, the valve is a coaxial valve, meaning the inlet and outlet are located on a common axis. Of course, the inlet and / or outlet of the valve, or the corresponding channels, may then need to be redirected to enable a coaxial connection. However, especially with light gases such as hydrogen, such redirections pose little or no disadvantage to the valve's performance.

[0030] In a further embodiment, the inlet can also be used as an outlet, in which case the outlet can then be used as an inlet. This is particularly possible with fully pressure-relieved valve designs, since the actuator is not forced into a specific position by the applied pressure when the valve is closed. Backpressure and sealing force are no longer important in this design. It is therefore irrelevant on which side of the valve the pressure is applied. This makes the valve extremely flexible to use, and incorrect installation, for example, with the wrong flow direction, is not possible with a suitable valve design.

[0031] In a further embodiment, the valve additionally has at least one channel that ends between two sealing means in the region of a recess and serves to monitor and measure leaks. In this way, leaks can be detected and, when using multiple channels, each corresponding to exactly one seal, can be assigned to a specific seal.

[0032] In a further embodiment, the valve has a spring that is directly or indirectly operatively connected to the actuator and holds the actuator in the first or second end position when no or only a small force is exerted on the actuator by the drive. Force here refers to the force exerted on the actuator to switch the valve. In particular, this can be the pressure of the control medium acting on the piston of the actuator.

[0033] Depending on the design and arrangement of the spring, the valve can be normally closed or normally open. Of course, the valve can also be equipped with a limit switch that monitors the valve position.

[0034] In a further embodiment, the actuator can additionally or alternatively have a magnet, so that the valve can also be opened or closed (electro)magnetically. Of course, in this configuration, the valve can be designed to be either normally open or normally closed.

[0035] The valve according to the invention can also provide more than two ports and more than two switching positions. Thus, the inlet and / or the outlet can also be formed by at least two ports. For example, the valve can have a total of three ports, with one of the ports forming the inlet and two ports each forming an outlet. The valve can also have more than one inlet and / or more than one outlet, with the inlets and / or outlets being interconnected in a variety of ways.

[0036] By varying the number and arrangement of the seals, gaskets, and connections, and by varying the controllable switching positions of the actuator, different valve configurations can be created. For example, one port can form the inlet and two ports can form the outlet, with the valve being closed in one switching position of the actuator. In a second switching position, both ports, which form the outlet, can be open. In this example, the valve is designed as a possible 3 / 2-way valve.

[0037] However, it is also possible for one port to form an inlet and two ports to form an outlet, and for the actuator to connect the inlet to the first outlet in a first switching position and the inlet to the second outlet in a second switching position. This is also a 3 / 2-way valve, but in a different version.

[0038] In the latter variant, a third switching position can also be provided, in which the valve is closed. In this case, the valve is a variant of a 3 / 3-way valve.

[0039] It is also possible for two connections to form the inlet and one connection to form the outlet. Here, too, different switching positions with different connection configurations are of course possible. More than three connections are also possible, for example 5 / 3-way valves. The actuator can also be designed in different ways. For example, the actuator can have one or more openings on its wall, for example in the form of bores. These lateral openings can act as branches of the actuator channel and offer the option for additional, more complex connections with further connections. The openings can each correspond to one or more connections, thus offering the option of providing further switching positions for different configurations.

[0040] The actuator can, for example, have two or more openings, with each opening being assigned to exactly one connection. In a first switching position, the first connection can be enabled, and in a second switching position, the second connection can be enabled. This can, among other things, shorten the switching distance the actuator must travel and / or allow multiple connections to be connected.

[0041] The actuator can also have multiple openings, with at least two openings having different cross-sections. Thus, the flow through one or more ports can be varied by allowing one opening to allow a higher flow rate while another allows a lower flow rate. These openings can also each correspond to one or more ports, or to the same port.

[0042] In some variants, the actuator can have at least one opening with a non-rotationally symmetrical cross-section. Non-rotationally symmetrical here refers in particular to a cross-section whose cross-section changes with respect to the respective corresponding connection.

[0043] For example, the opening can have a substantially triangular cross-section, with only the tip of the triangle releasing the fluid flow to the corresponding connection in a first switching position. As the actuator is moved, the cross-section of the triangle releases an increasingly larger flow opening, so that the flow to this connection becomes increasingly larger. This is one of the ways in which a dosing and / or control valve can be implemented. It is also possible for the actuator designed as a control tube to be adjusted not only in the axial direction but also rotated around its longitudinal axis in order to assume the various switching positions, whereby the corresponding drives and, if necessary, gears must be provided. For example, it is conceivable for the control tube to have partially or fully circumferential teeth on its jacket-shaped outer wall, by means of which teeth the control tube can be rotated around its axis.Additionally, an axial adjustment drive can be provided.

[0044] The invention also relates to a valve seat for a valve according to the invention.

[0045] In a particularly preferred embodiment, the valve seat is substantially annular and, in particular, has a mirror-symmetrical cross-section. Because the valve seat is substantially annular, the actuator can move into the valve seat without coming into contact with a valve seat surface. The valve seat can, in particular, also have a mirror-symmetrical cross-section, so that the valve seat can act in the same way on both sides.

[0046] In a likewise preferred embodiment, the valve seat is a seal.

[0047] In a further embodiment, the outer surface of the valve seat has a circumferential groove, which serves to accommodate a sealing agent such as an O-ring. The sealing agent can, for example, improve the sealing effect and / or hold the valve seat in position.

[0048] In a further particularly preferred embodiment, at least one, in particular both, axial end face(s) of the valve seat has(have) a recess or groove, in particular a circumferential one. The groove causes the applied pressure on the valve seat to be distributed radially inwards and outwards, so that the sealing effect is supported when pressure is applied. This also prevents the pressure from acting exclusively in the axial direction on the valve seat, which could potentially crush the valve seat or cause it to slip. In the case of a mirror-symmetrical valve seat, the groove can be arranged identically on both end faces of the valve seat.

[0049] In another embodiment, a sealing lip is formed through the recess or groove. The sealing lip can then be pressed against the actuator or housing wall by the applied pressure in the manner described above, further supporting the sealing effect.

[0050] In a further preferred embodiment, the valve seat has at least one, in particular two, circumferential projections on a radially inner side, forming a sealing nose. This sealing nose can be arranged such that the applied pressure through the recess on the end face presses the sealing nose against the actuator, thus further supporting the sealing effect.

[0051] In a particularly preferred embodiment, the valve seat is made of a high-performance plastic, in particular PEEK. This material meets the high requirements for tightness, strength, processability, and coefficient of friction, making the valve seat suitable for high pressures, especially hydrogen.

[0052] The invention also relates to a support ring for a valve according to the invention.

[0053] In one embodiment, the support ring has a circumferential first section extending in the axial direction with at least one radially inner surface and at least one radially outer surface, wherein the radially inner surface runs essentially parallel to the longitudinal axis of the support ring and wherein at least one radially outer surface runs at an angle greater than 0°, in particular between 10° and 80°, to the longitudinal axis of the support ring. An angle of 45°±10° is particularly suitable. Such support rings are known and commercially available. In particular, such support rings are available with matching grooved rings. According to the invention, the support ring additionally has at least one second, in particular cylindrical, section extending in the axial direction, wherein an outer diameter of the second section is larger than a largest outer diameter of the first section.This at least second section of the support ring can be dimensioned such that it rests on the outside, for example, against a housing wall and on the inside against the actuator. Thus, in addition to supporting and holding the grooved ring, the support ring also serves as a guide for the actuator.

[0054] In a further embodiment, the first section of the support ring can be inserted or pushed into a receptacle of a grooved ring. In particular, the first section can be dimensioned such that it can be used with conventional and commercially available grooved rings.

[0055] In a further embodiment, the second section has a first contact surface for the engagement of a grooved ring. In this way, the support ring can also support an attached grooved ring in the axial direction.

[0056] In a further embodiment, the second portion has a second contact surface for engagement with a wall in a housing of the valve. In this way, the support ring can be supported in the axial direction by a wall of the housing.

[0057] Some embodiments of the invention are described in more detail below with reference to figures. Of course, the invention is not limited to the embodiments shown.

[0058] They show:

[0059] Fig. 1a shows a cross section through a valve according to the invention;

[0060] Fig. lb the same valve as in figure la in the open state;

[0061] Fig. 2 shows a cross-section through the valve shown in Figure 1 in another view;

[0062] Fig. 3 a detailed view of the valve seat and the sealant of the

[0063] valve shown in Figure 1;

[0064] Fig. 4 is an external view of the valve shown in Fig. 1; Fig. 5a is a cross-section through a valve seat according to the invention;

[0065] Fig. 5b is a perspective view of the valve seat shown in Figure 5a;

[0066] Fig. 6a shows a cross section through a sealing means with a support ring according to the invention and a grooved ring;

[0067] Fig. 6b is a perspective view of the one shown in Figure 6a

[0068] support ring;

[0069] Fig. 7a shows a cross section through another valve according to the invention in two different views;

[0070] Fig. 7b a cross-section through the valve shown in Figure 7a in the open state;

[0071] Fig. 8a - 8c a schematic embodiment of a valve which is designed as a 3 / 3-way valve, in three different switching positions;

[0072] Fig. 9a - 9c a schematic embodiment of a valve which is designed as a 3 / 3-way valve, with an actuator which has bores in its wall, in three different switching positions;

[0073] Fig. 10a, 10b a variant of an actuator with openings of different sizes in two switching positions;

[0074] Fig. 11a, 11b a further variant of an actuator with non-rotationally symmetric openings;

[0075] Fig. 12a, 12b a further variant of an actuator which can be brought into different switching positions by rotation;

[0076] Fig. 12c schematic representation of a sealing agent for a rotating

[0077] Actuator. Figure 1a shows a cross-section through a valve 1 according to the invention. The valve 1 has a housing 2 consisting of several parts with an inlet 1 and an outlet 0. An actuator 3 in the form of a hollow cylinder is arranged in the valve 1. The actuator has a wall 3" with an outer surface 3'. A channel 3a is arranged in the actuator 3 so that a medium can flow through the actuator 3. In the configuration shown, the valve 1 is closed and the actuator 3 is in a first end position. The first end 3b of the actuator 3 is located in a first recess HI in the housing 2. Accordingly, the second end 3c of the actuator 3 is located in a second recess H2 in the housing 2. The recesses HI, H2 are connected to the outlet 0 and the inlet 1, respectively, via channels K1, K2.

[0078] The first end 3b of the actuator 3 is located in an annular valve seat 4, which seals the channel 3a of the actuator 3 from the outlet 0. The valve seat 4 thus forms a seal in this case. The valve 1 is consequently closed and no medium can flow from the inlet I to the outlet 0. The valve 1 shown is designed laterally, which means that the outlet 0 and the inlet I are not on a common axis. It is again pointed out that the valve can also be designed as a coaxial valve. This then requires a suitable deflection of the inlet I or the outlet 0. As already mentioned, a deflection has hardly any disadvantages, especially when using light gases such as hydrogen, or the advantages of a coaxial arrangement can outweigh the disadvantages of a deflection in individual cases.

[0079] The recess Hl has a conical end wall Hl', which is created by a bore, so that a first end face Fl of the actuating means 3 does not touch the inner wall Hl" of the recess Hl, but is essentially exposed. A pressure P is applied to the inlet I of the valve 1. Because the end face Fl of the actuating element 3 is exposed, the pressure P acts evenly on the end face Fl and a second opposite end face F2 of the actuating element 3. Consequently, no net pressure acts in the axial direction on the actuating element 3, neither in the closed state shown nor in the open state (not shown) of the valve 1. The actuating element 3 is thus pressure-relieved at all times with regard to the applied pressure P.

[0080] A piston 5 for adjusting the actuator 3 is also arranged on the actuator 3. The piston 5 is adjustably arranged in a third recess H3 of the housing 2 and is held in the first end position shown by a spring 6. The valve 1 shown is therefore normally closed. Of course, the valve 1 can also be designed to be normally open. The piston 5 rests against a housing wall 2a, which thus defines the first end position of the actuator 3.

[0081] Additional sealing means are arranged along the actuator 3, each sealing the recesses H1, H2, and H3 from each other. The sealing means shown in Figure 1 are fixedly arranged in the housing 2, so that they are stationary relative to the actuator 3. Of course, sealing means that are fixedly arranged on the actuator 3 are also conceivable, for example, in the form of piston seals.

[0082] The sealing means shown are sealing means 7 with a support ring 7a according to the invention and a grooved ring 7b. Furthermore, the valve 1 shown has additional sealing means in the form of O-rings 8, 8'. A channel 9 for monitoring and measuring leaks is arranged between the O-rings 8 and the sealing means 7. The O-ring 8' is arranged on the piston 5 and seals the two working chambers A1, A2 of the recess H3 from each other.

[0083] Figure 1b shows the same valve as Figure 1a, but the actuator 3 is in the second end position. The valve 1 is thus open. For this purpose, a pressure medium was fed into a working chamber A1 of the recess H3, so that the piston 3 was displaced within the third recess H3 against the spring force of the spring 6 until the piston 5 came to rest on a housing wall 2b. The working chamber A2 of the recess H3 has thereby decreased. The first end 3b of the actuator was moved out of the valve seat 4, so that the channel 3a of the actuator 3 is connected to the outlet 0. The valve is thus open. Figure 2 shows the same valve 1 as Figure 1a from a different side. The illustration shows two channels 10a, 10b, which serve to fill the working chambers A1, A2 of the recess H3 with a control medium. In the position shown, the valve 1 is closed.If it is to be opened, a control medium such as a gas is conveyed through the channel 10a so that the piston 5 moves in the axial direction against the spring force of the spring 6 until the piston disc 5 comes to rest on a wall 2b of the housing 2, as shown in Figure 1b. This defines the second end position of the actuator 3. When the piston 5 is adjusted, pressure medium must simultaneously be conveyed out of the working chamber A2 through the channel 10b. To close the valve 1, it is sufficient either to switch off the pressure in the channel 10a so that the spring 6 moves the piston 5 to its starting position, or additional control medium is conveyed under pressure into the channel 10b to support or accelerate the closing process. It is obvious that the channels 10, 10b can and must serve both as inlet and outlet.

[0084] Figure 3 shows a detailed view of the valve seat 4 and the actuator 3 arranged therein. The actuator 3 rests with its outer surface 3' against the valve seat 4. In the closed position shown, the valve seat 4 seals the channel 3a from the outlet O. At the same time, the conical end wall H1' ensures that the first end face Fl is exposed. The pressure P applied to the inlet I thus acts equally on the first end face Fl and the opposite end face F2 (not shown). The actuator 3 is thus pressure-relieved even when the valve 1 is in the closed position, whereby comparatively low switching forces are sufficient to switch the valve even at high applied pressures. Because the actuator 3 does not come into contact with a surface of a valve seat, as in previously known solutions, the problem of wear on the contact surface is also eliminated.Thus, the valve 1 according to the invention is also suitable for particularly thin gases such as hydrogen, even and in particular at high pressures. If the actuator 3 is adjusted as described above and moved out of the valve seat 4, the outlet O is connected to the channel 3a and thus to the inlet I, and the valve 1 is thus opened. The valve seat 4 has a circumferential groove 4a which serves to accommodate an O-ring (not shown), which stabilizes the valve seat 4 and can improve the sealing effect. Circumferential recesses in the form of a groove 4b are arranged on both end faces of the valve seat 4, whereby the end faces have sealing lips 4c. If pressure acts on the end faces, the pressure is redirected in the direction of the sealing lips 4c and in this way supports the sealing effect by pressing the sealing lips 4c against the outer surface 3' of the actuator 3 or against a wall of the housing 2.

[0085] Furthermore, the ends 3b, 3c of the actuator 3 have a conical section 3d to counteract damage to the valve seat 4 when the actuator 3 moves in and out.

[0086] Also shown in Figure 3 is a sealing means 7 with a support ring 7a and a grooved ring 7b fitted thereon. The support ring 7a has a section 7g whose outer diameter is larger than the outer diameter of a conical section 7c arranged adjacent to it. The support ring 7a thus serves as a guide on one side and as a support for the grooved ring 7b on the other side. The precise design of the support ring will be described in more detail in connection with Figures 6a and 6b.

[0087] The U-ring 7b is a seal made of H-ECOPUR with two sealing lips. When the valve 1 is opened, the sealant 7 seals the recess H1 against the recess H3, with the sealing lips being forced apart by the pressure. At the same time, the support ring 7a stabilizes the U-ring 7b, preventing it from slipping or being compressed. This configuration has been shown to withstand many thousands of switching cycles at very high pressures of 1000 bar and more, especially when using hydrogen, and to operate reliably.

[0088] Figure 4 shows an external view of the valve 1 with the cylindrical housing 2 and the inlet I and the outlet O. The control connections to the channels 10a, 10b can also be seen on the side wall of the housing 2. The contacts 11 for a limit switch (not shown) are also shown. Figure 5a shows a cross-section through a valve seat 4 according to the invention. On the outer surface, the valve seat 4a has a circumferential groove 4a for receiving an O-ring. The two end faces also have circumferential recesses 4b for distributing the applied pressure. The recesses 4b are arranged such that the end faces of the valve seat have sealing lips 4c, which are pressurized when pressure is applied and support the sealing effect of the valve seat 4. Furthermore, the valve seat 4 has two projections 4d on a radially inner side, which form sealing noses and rest against the actuator 3 when installed.When pressure is applied, the sealing lugs are pressed against the outer surface 3' of the actuator 3.

[0089] Figure 5b shows a valve seat 4 according to the invention in a perspective external view.

[0090] Figure 6a shows a cross-section through a support ring 7a of a sealing means 7 according to the invention. A grooved ring 7b is also shown, which is inserted onto the support ring 7a in the assembled state. The support ring 7a has a first section 7c extending in the axial direction. The section 7c is inserted into the receptacle 7d of the grooved ring 7b. Radially outwardly, the first section 7c has an inclined surface 7e for this purpose. Radially inwardly, the support ring 7a has a surface 7f running parallel to the longitudinal axis of the support ring 7a. This surface 7f bears against the outer circumferential surface 3' of the actuator 3.

[0091] In addition, according to the invention, the support ring 7a has a second section 7g whose outer diameter is larger than the largest outer diameter of the first section 7c. The second section 7g is dimensioned such that it forms a guide between a housing wall and the actuator 3. The second section 7g also has a surface 7h that comes into contact with a housing wall and a surface 7i against which the U-ring 7b comes into contact. Due to the aforementioned features, the support ring automatically centers itself between the housing 2 and the actuator 3 and simultaneously stabilizes the U-ring 7b, so that it forms a reliable seal. The U-ring 7b is a commercially available U-ring with two circumferential sealing lips 7j.

[0092] Figure 6b shows a support ring 7b according to the invention in a perspective external view.

[0093] Figure 7a shows a further embodiment of a valve 1 according to the invention in two different cross-sectional views. The features largely correspond to the embodiment shown in Figure 1a. Only the inlet I is arranged on the opposite side of the valve 1, so that the distance between inlet I and outlet O is significantly shorter than in the embodiment shown in Figure 1a. Accordingly, the second recess H2 of the housing 2 has a conical end wall H2' so that the actuator 3 is pressure-relieved in the second end position, i.e. in the open state. Consequently, the end face F2 of the actuator 3 is exposed in the second end position. The limit switch 11a detects, by means of the contacts 11, whether the valve is closed or open.

[0094] Figure 7b shows the valve of Figure 7a in the open position. The actuator 3, together with the piston 5, is adjusted to its second end position analogous to the position shown in Figure 1b. In the position shown, the inlet I and the outlet O are directly connected to each other via the recess H1, i.e., the medium does not have to first flow through the channel 3a of the actuator 3 to reach the outlet O from the inlet I. The second end face F2 of the actuator 3 remains free due to the conical end wall H2' of the recess H2 and does not touch the inner wall H2". The actuator 3 is thus also pressure-relieved in this position. The limit switch 11a is now connected to the other contact and thus detects that the valve 1 is open.

[0095] This embodiment has the advantage that the nominal diameter of the valve is not determined by the channel 3a in the actuator 3, but by the recess H1. The recess H1 has a diameter that corresponds to the outer diameter of the actuator 3. The nominal diameter of the valve shown thus no longer depends on the control tube 3 or its inner diameter. If one wanted to make the channel 3a in the actuator in the embodiment shown in Figure 1a larger in order to increase the nominal diameter of the valve, the actuator 3 would have to be made correspondingly more stable and the outer wall 3" correspondingly stronger in order to counteract destruction or deformation of the control tube. This would quickly make the control tube and thus the valve very large, expensive and impractical, or in some cases, impossible to manufacture at all.

[0096] In the illustrated embodiment, channels K1, K2 are narrower than recess H1. The flow velocity within the valve is thus reduced. It should be noted that channel 3a within actuator 3 is nevertheless necessary to relieve pressure on actuator 3. However, the diameter of channel 3a is not important. In particular, channel 3a is not important for the nominal diameter of the valve.

[0097] A further possible embodiment of a pressure-relieved valve 100 according to the invention is shown schematically in Figures 8a to 8c. The actuator 3, the valve seats 4, the seals 8 and the sealing means 7, 7a, 7b are essentially identical to the corresponding components of the previously described embodiments. In contrast to the embodiment shown in Figure 1a, the embodiment shown is a 3 / 3-way valve, which means it has three ports A, B, C and three switching positions. Port A can, for example, function as inlet I and the two ports B, C as outlet O. The channel K is closed at its two ends E.

[0098] The first switching position is shown in Figure 8a, with the valve 100 being closed in this switching position. A pressure P is present at the inlet O (port A), which is distributed via the tubular actuator 3 from the left section within the housing 2 to the right area within the housing and is applied to the valve seat 4 to the right of port C. A pressure Po is applied to the ports B, C, where P>Po applies. The valve seat 4 thus seals off port C from port A in the manner described in connection with the previous exemplary embodiment, so that no fluid can flow from the inlet I to the outlet O. In the same way, the valve seat 4 to the left of port B, to which the pressure P of port A is also applied, seals off port B from port A.Between ports B and C, there are no valve seats 4, but rather sealing means 7 of the type described above, consisting of a support ring 7a and a grooved ring 7b, in which the actuator 3 is slidably mounted or adjustably arranged, with the actuator 3 being arranged in the sealing means 7 in every switching position. Two seals 8 in the form of O-rings are arranged between ports B, C and between ports A, B for support. A further valve seat 4 is arranged next to port 4.

[0099] The actuator 3 can be adjusted to two further positions using an adjustment device (not shown). The adjustment device can, in principle, be any suitable adjustment device, in particular a pneumatic, hydraulic, or magnetic adjustment device. Of course, the valve 100 can be designed to be de-energized or de-energized, depending on the design of the adjustment device.

[0100] Figure 8b shows the valve 100 in the second switching position. The adjustment device (not shown) has moved the actuator 3 to the right. Port B has thus been opened, while port C remains closed. Port C is sealed by the left-hand seal 7 of the two sealants shown in the figure and the additional seals 8 between ports B and C and the valve seat 4 to the right of port C. In the switching position shown, port A thus forms the inlet I and port B forms the outlet O of the valve 100.

[0101] Figure 8c shows a third switching position of the valve 100. The adjustment device (not shown) has moved the actuator 3 into a third position, in which the port B is sealed off from the ports A and C. The fluid flow can thus run from the port A to the port C, which thus forms the outlet O. The actuator 3 has thus been moved into the valve seat 4 on the left in the figure. The sealing of the port B is thus achieved via the left valve seat 4 and the sealing means 7 on the right in the figure. In all switching positions, the actuator 3 lies in the two sealing means

[0102] 7 or is arranged longitudinally displaceably therein. The actuator 3, on the other hand, is moved out of at least one valve seat 4 in each switching position.

[0103] Of course, the embodiment shown in Figures 8a to 8c can also be designed as a 3 / 2-way valve, in which the actuator 3 can only be adjusted between two switching positions. For example, only the two switching positions of Figures 8b and 8c could be adjustable, so that the valve 100 switches the two ports B and C, with one of the two ports B, C forming an open outlet 0 in exactly one switching position. In this configuration, the valve 100 would then never be closed, but could switch the fluid flow from A to B or to C. The valve seat 4 in the middle of the image could then be omitted.

[0104] Other configurations can also be implemented, including 5 / 3-way valves. The arrangement and number of valve seats 4, seals 7, and gaskets 8 can also be varied and adapted to the specific requirements, pressure, and connection configuration. The embodiments shown are therefore in no way limiting, but are intended merely to schematically illustrate how a multi-way valve with a valve seat 4 or seal 7 according to the invention can be constructed and switched.

[0105] Another possible embodiment of a valve 1000 is shown in Figures 9a and 9b. The valve seats 4, the sealing means 7, and the seals 8 correspond to the previously described components. However, unlike the previously described embodiments, the actuator 3000 additionally has two bores Ha, Hb in its wall 3" through which the fluid flow can also exit laterally from the channel 3a.

[0106] In Figure 9a, valve 1000 is closed. A pressure P is present at port A, which is passed via channel 3a of actuator 3000, as in the previously described embodiment, into the section to the right of port C. The valve seats 4 each seal one of ports B, C from port A. In contrast to the embodiment of Figures 8a to 8c, the pressure P is also distributed via the opening or bore Ha into the central region of the housing 2, which lies between ports B and C. Therefore, ports B, C are each sealed from port A by the sealing means 7 and seals 8 arranged in this area. In particular, the two middle of the four sealing means 7 in the figure are responsible for sealing ports B, C, in that their grooved ring 7b is oriented towards the pressure side P in the manner described above.Since the actuator 3000 does not leave or exit the valve seat 4 on the left in the figure in any of the switching positions, this valve seat 4 could also be replaced by a sealing agent 7.

[0107] It goes without saying that other combinations / arrangements / numbers of seals 8, sealing means 7 and valve seats 4 are also conceivable and possible and may be advantageous, so that the valve 1000 can be adapted to the pressures used and requirements with regard to tightness.

[0108] Figure 9b shows the same valve 1000 as in Figure 9a, but the actuator 3000 has been adjusted to a second switching position by an adjustment device (not shown). The two bores Ha, Hb are now at the level of ports B and C, allowing fluid flow from port A to ports B, C. In the position shown, port A thus forms inlet I, and ports B, C each form an outlet O for valve 1000.

[0109] The two of the four sealing means 7 arranged on the outside in the figure seal the connection B from the connection C. Depending on the configuration of the connections, in particular when the flow rate of the two connections B, C and the same applied pressure, these two sealing means 7 may be redundant or not required and can be omitted or replaced by conventional sealing means, depending on whether the sealing effect at this position is required for the function of the valve 1000 or not.

[0110] In the case of very high pressures P, the transition between the holes Ha, Hb via the two sealing means 7 arranged next to one another and rotated by 180° to one another can result in the pressure P being present between the two sealing means 7. In this case, a high pressure P is present on the side of the sealing means 7 not intended for this purpose, namely on the side of the support ring 7a and not on the side of the grooved ring 7b. One possible solution to this problem can be that the valve 1000 is depressurized when this transition occurs. It is also conceivable and possible that at least one equalization channel X exists between these sealing means in order to equalize or release the excess pressure P between the two adjacent sealing means 7. This at least one equalization channel X can and must be closable if necessary.

[0111] In Figure 9c, the actuator 3000 is adjusted to a third switching position. The bore Ha is located in the same housing section as port A and therefore has no function in this switching position. The pressure is again directed through the bore Hb into the housing section between the two ports B and C. Port B is sealed from port A by the valve seat 4 on the left in the figure and, as described in connection with Figure 9a, by the sealing means 7 (identified by reference numeral in Figure 9c). Thus, no fluid flows from port A to port B.

[0112] In this switching position, the passage from port A to port C is possible through channel 3a of actuator 3000. In this switching position, port C thus forms an outlet 0. The illustrated embodiment is therefore also a 3 / 3-way valve with three ports and three switching positions.

[0113] Of course, this embodiment is also variably adaptable; for example, the number and arrangement of the connections, switching positions, sealing means, and valve seats can be varied. For example, the valve can also be designed as a 3 / 2-way valve with only two switching positions. The valve 100, 1000 can also be designed as a coaxial valve in which the ends E are not closed. In this case, by adjusting the actuator 3, 3000, for example, lateral connections A, B, C can be added or removed, with the ends E each forming a permanently open inlet I or outlet O.

[0114] An example of a further possible variant of an actuator 3000' is shown in Figures 10a and 10b. For the sake of clarity, the remaining components of the valve are not shown, and the positions of ports A, B, and C are only indicated. The actuator 3000' has a plurality of bores Ha', Hb' and is otherwise designed as described in the previous embodiments. In the switching position shown in Figure 10a, the first bore Ha' is at the level of port B, and the second bore is at the level of port C. The fluid flow can thus flow from port A to both port B and port C.

[0115] The cross-section of the first bore Ha' is larger than the cross-section of the second bore Hb'. The flow to port B is therefore greater than the flow to port C (indicated by the different-sized arrows).

[0116] Figure 10b shows the same actuator in a second switching position, with the second bore Hb' at the level of port B. This means that the flow to port B is smaller in this switching position than in the first switching position. However, the fluid flow from port A to port C is possible through channel 3a in this switching position, so that the flow to port C is greater in this switching position than in the first switching position. This is therefore a 3 / 2-way valve, with the two switching positions regulating the flow to ports B and C. Of course, this embodiment can also be adapted to include additional switching positions, for example, an additional "closed" switching position.

[0117] A further alternative for an actuator 3000'' is shown in Figures 11a and 11b. The two bores Ha'', Hb'' or openings are not round or rotationally symmetrical, but essentially triangular. In the switching position shown in Figure 11a, only the tips of the triangles are at the level of one of the ports B, C. The flow to the ports B, C is therefore comparatively low. In the switching position shown in Figure 11b, the wide ends of the triangles are at the level of the ports B, C, and the flow to the ports B, C is correspondingly greater. Of course, intermediate switching positions are also possible, as is gradual, stepless adjustment of the actuator 3000'. Various variants of metering and control valves are thus possible, including but not limited to the embodiment shown.

[0118] A further alternative for an actuator 3000"' is shown in Figures 12a and 12b. The opening Ha'" consists of two bores arranged side by side in the circumferential direction. The opening Hb"' consists of only one bore. In the switching position shown, the upper bore of the opening Ha"' in the figure corresponds to the connection B. For this purpose, for example, a channel corresponding to the connection B can be provided in a sealing means not shown, which seals the lower of the two bores in the figure from the connection B and connects the bore arranged above it in the figure to the connection B. In the switching position shown, the connection B thus forms an outlet O with a comparatively low flow rate.

[0119] Unlike the previously described variants, the actuator 3000"' is adjusted to a second switching position by rotation about its longitudinal axis AX. In Figure 12b, the actuator 3000"' is in a second switching position. In this switching position, the two bores of the opening Ha"' both correspond to the connection B, whereby the corresponding channel in the sealing means (not shown) must be designed such that it connects both bores of the opening Ha"' with the connection B. The flow to the connection B is thus greater than in the first switching position.

[0120] In this switching position, the second opening Hb"' corresponds with its one bore to port C. Port C therefore also forms an outlet O in this switching position. Since this opening Hb"' only has one bore, the flow is smaller than at port B. Of course, variants are also possible in which both openings Ha"', Hb"' are of the same design, so that the valve has a closed switching position and a switching position in which both ports B, C are open. It is also possible for both openings to be of the same type but to be offset from one another in the circumferential direction. In this way, the valve can, for example, have three switching positions, with the valve being closed in the first switching position. In the two other switching positions, one of the ports B, C is open, with the flow rate of the two ports being the same in the open switching position.

[0121] Of course, this variant can also be varied and adapted to different switching positions and connection configurations.

[0122] Figure 12c schematically shows an example of a sealing means 4"' that can be used in conjunction with the actuator 3000"'. The sealing means 4"' resembles a valve seat 4 or a circumferential sealing ring and is arranged immovably in the region of the connection B. The sealing means 4"' has a channel 4a'", which corresponds to the connection B. A bore H, which is arranged on the only indicated actuator 3000"', can be connected to the channel 4a"' or sealed against the channel 4a"' by rotating the actuator 3000"'. A similar sealing means 4"' with a channel of the same type or with a different cross-section can or must also be arranged in the region of the connection C.

[0123] Of course, the above-described technical features and the associated advantages can be combined in a technically feasible manner. The valve according to the invention can thus be adapted to a wide variety of requirements, pressures, and connection combinations. Instead of multiple outlets O, multiple inlets I can be provided. The valve can also have multiple inlets I and multiple outlets O, which can be interconnected in different ways by appropriately varying the above technical features.

Claims

Patent claims 1. Valve (1, 100, 1000), in particular a hydrogen valve, with at least one inlet (I) and at least one outlet (O), a housing (2) and an actuator (3) arranged therein, wherein the actuator (3) is adjustable into at least a first end position (valve closed) and into at least a second end position (valve open), and with a control device for adjusting the actuator (3), characterized in that the valve (1) has a valve seat (4) which, in the first end position in which the valve (1) is closed, bears sealingly against an outer circumferential surface (3') of the actuator (3).

2. Valve (1, 100, 1000) according to claim 1, characterized in that the valve seat (4) is a substantially annular body whose inner diameter is suitable for receiving the actuator.

3. Valve (1, 100, 1000) according to claim 1 or 2, characterized in that the actuator (3) is a tubular body, in particular in the form of a hollow cylinder, which has a wall (3") which has two end faces (F1, F2) and an outer jacket surface (3'), wherein the actuator (3) has an axially extending channel (3a) which exits at the front ends (3b, 3c) of the actuator (3).

4. Valve (1, 100, 1000) according to claim 3, characterized in that the first end (3b) of the actuator (3) lies in a first cylindrical recess (Hl) of the housing (2) in a sealing manner, in particular by means of seals (7, 8), both in the first and in the second end position, and that the second end (3c) of the actuator (3) lies in a second cylindrical recess (H2) of the housing (2) in a sealing manner, in particular by means of seals 7, 8), both in the first and in the second end position, wherein connecting channels (Kl, K2) end in the cylindrical recesses (Hl, H2), which connect the recesses (Hl, H2) to the inlet (I) and the outlet (0).

5. Valve (1, 100, 1000) according to claim 4, characterized in that the end faces (Fl, F2) of the actuator (3) in both end positions are not in contact with the inner wall (Hl", H2") of the respective recess (Hl, H2), wherein for this purpose in particular the first recess (Hl) and / or the second recess (H2) each has or have at least one, in particular conical, end wall (Hl', H2').

6. Valve (1, 100, 1000) according to claim 4 or 5, characterized in that the valve seat (4) is arranged in the first recess (Hl).

7. Valve (1, 100, 1000) according to one of claims 3 to 6, characterized in that the valve seat (4) in the first end position lies sealingly against the outer circumferential surface (3') of the actuator (3), and that the first end (3b) of the actuator (3) in the second end position is adjusted out of the valve seat (4) in the axial direction, such that the channel (3a) of the actuator (3) is in communication with the connecting channel (Kl).

8. Valve (1, 100, 1000) according to one of the preceding claims, characterized in that the actuator (3) is adjustable by means of a drive.

9. Valve (1, 100, 1000) according to claim 8, characterized in that the actuator (3) forms a piston or a piston (5) is firmly connected to the actuator (3), and the piston (5) is arranged in a third cylindrical recess (H3) of the housing, which is located in particular between the two recesses (H1, H2) and seals off two working spaces (A1, A2) from one another, wherein the piston (5) is adjustable back and forth between its end positions by means of a control medium which can be introduced into the working spaces (A1, A2).

10. Valve (1, 100, 1000) according to claim 9, characterized in that the body in the first end position of the actuator (3) and in the second end position of the actuator (3) in each case bears against a surface (2a, 2b) within the third recess (H3), such that these surfaces (2a, 2b) limit the axial adjustability of the actuator (3).

11. Valve (1, 100, 1000) according to one of claims 4 to 10, characterized in that the third recess (H3) is sealingly separated from the two other recesses (H1, H2) by means of seals (8), in particular in the form of an O-ring, a pneumatic sealing edge or a radial shaft seal.

12. Valve (1, 100, 1000) according to one of claims 4 to 11, characterized in that at least one, in particular two, sealing means (7) has or have a support ring (7a) and a grooved ring (7b), wherein the actuator (3) is adjustably arranged in the sealing means(s) (7), 13. Valve (1, 100, 1000) according to one of claims 4 to 12, characterized in that at least one sealing means (7) is arranged on the actuator (3), in particular in the form of a piston seal.

14. Valve (1, 100, 1000) according to claim 12, characterized in that the grooved ring (7b) consists of a polyurethane, in particular of H-ECOPUR.

15. Valve (1, 100, 1000) according to one of the preceding claims, characterized in that the valve seat (4) consists of a high-performance plastic, in particular of polyaryletherketone / PEEK, or has a component made of high-performance plastic.

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

17. Valve (1, 100, 1000) according to one of the preceding claims, characterized in that the inlet (I) can also be used as an outlet (O), wherein the outlet (O) can then be used as an inlet (I).

18. Valve (1, 100, 1000) according to one of the preceding claims, characterized by additionally at least one channel (9) which ends between two sealing means (7, 8) in the region of a recess (H1, H2) and which serves to monitor and measure leaks.

19. Valve (1, 100, 1000) according to one of the preceding claims, characterized by a spring (6) which is directly or indirectly operatively connected to the actuator (3) and holds the actuator (3) in the first or in the second end position when no or only a small force is exerted on the actuator (3) by means of the drive.

20. Valve (1, 100, 1000) according to one of the preceding claims, characterized in that the drive additionally or alternatively comprises a magnet.

21. Valve (100, 1000) according to one of the preceding claims, characterized in that the valve (100, 1000) has more than two connections (A, B, C), wherein at least one connection (A) forms an inlet (I) and at least one connection (B, C) forms an outlet (O), in particular that the valve is a 3 / 2-way or a 3 / 3-way valve.

22. Valve (100, 1000) according to claim 21, characterized in that the valve (100, 1000) has more than two switching positions.

23. Valve (1000) according to one of the preceding claims, characterized in that the actuator (3000, 3000', 3000", 3000"') has at least one opening (Ha, Hb, Ha', Hb', Ha", Hb", Ha"', Hb"') in its wall (3"), in particular in the form of at least one bore.

24. Valve (1000) according to claim 23, characterized in that the actuator (3000') has at least two openings (Ha', Hb'), wherein at least two openings (Ha', Hb') each have a different cross-section.

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

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

27. Valve (1000) according to claim 26, characterized by a sealing means (4"') with at least one channel (4"') arranged therein, wherein the channel (4"') corresponds to at least one connection (A, B, C).

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

29. Valve seat (4) for a valve (1, 100, 1000) according to one of the preceding claims, characterized in that the valve seat (4) is substantially annular and in particular has a mirror-symmetrical cross-section.

30. Valve seat (4) according to claim 29, characterized in that the valve seat is a seal.

31. Valve seat (4) according to claim 29 or 30, characterized in that the outer circumferential surface of the valve seat (4) has a circumferential groove (4a), wherein the groove (4a) serves to receive a sealing means, in particular an O-ring.

32. Valve seat (4) according to one of claims 29 to 31, characterized in that at least one, in particular both, axial end face or end faces of the valve seat (4) has or have a, in particular circumferential, recess or groove (4b).

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

34. Valve seat (4) according to one of claims 29 to 33, characterized in that the valve seat (4) on a radially inner side at least one, in particular two, circumferential projections (4d) which form a sealing nose.

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

36. Support ring (7a) for a valve (1, 100, 1000) according to one of claims 1 to 28, with a circumferential first section (7c) extending in the axial direction, with at least one radially inner surface (7f) and at least one radially outer surface (7e), wherein the radially inner surface (7c) runs substantially parallel to the longitudinal axis of the support ring, and wherein at least one radially outer surface (7e) runs at an angle greater than 0°, in particular between 10° and 80°, to the longitudinal axis of the support ring (7a), characterized by at least one second section (7g) extending in the axial direction, in particular cylindrical, wherein an outer diameter of the second section (7g) is greater than a largest outer diameter of the first section (7c).

37. Support ring (7a) according to claim 36, characterized in that the first section (7c) of the support ring (7a) can be inserted or pushed into a receptacle (7d) of a grooved ring (7b).

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

39. Support ring (7a) according to one of claims 36 to 38, characterized in that the second section (7g) has a second contact surface (7h) for contact with a wall in a housing (2) of the valve (1).

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