pressure relief valve

Abstract

A valve (1), particularly a hydrogen valve, having at least one inlet (I) and at least one outlet (O), a housing (2) and an actuator (3) disposed in the housing (2), wherein the actuator (3) is adjustable to at least one first end position (valve closed) and at least one second end position (valve open), and the valve (1) having a control device for adjusting the actuator (3), wherein the valve (1) has a valve seat (4) in which the valve seat (4) is sealed against the outer peripheral surface (3') of the actuator (3) in the first end position when the valve (1) is closed.

Description

[0001] This invention relates to a valve, particularly a hydrogen valve, having at least one inlet and at least one outlet, a housing, and an actuator disposed within the housing. The actuator is adjustable to at least one first terminal position (valve closed) and at least one second terminal position (valve open), and the valve has a control device for adjusting the actuator. The invention also relates to a valve seat and a support ring for such a valve.

[0002] Valves, especially coaxial valves, have long been known and commercially available. Known coaxial valves typically have an adjustable actuator in the form of a shaft or tube through which the medium to be regulated flows. In these known designs, the actuator cooperates with a valve seat, the end face of which rests against the valve seat. A seal is achieved by pressing the control tube against the valve seat; for this purpose, the valve seat has a face against which the actuator is pressed when the valve is closed.

[0003] For example, a flow control valve in the form of a coaxial valve is known from DE 100 51 492 A1, which has a control tube and a valve seat, in which the control tube is pressed against the substantially flat valve seat to close the valve.

[0004] However, there are different valve seat design schemes. For example, another coaxial valve with an actuator is known from DE 101 08 492 A1, which cooperates with a valve seat having an arc-shaped valve seat surface.

[0005] What these known valves have in common is that sealing is achieved by the actuator abutting against the valve seat. To this end, the end face of the actuator is designed differently depending on the application and the valve seat material. Here, depending on the application, it is desirable to depressurize the control tube as much as possible at any position. To this end, the cross-section of the end face can be designed to taper into a pointed flange, with the flange tip abutting against the valve seat surface. Therefore, the inclined section of the flange remains exposed, allowing ambient pressure to act on this inclined surface. Nevertheless, due to the principle that a portion of the end face must abut against the valve seat, known coaxial valves can only approximate depressurization, and not completely depressurize.

[0006] Another disadvantage is that the flange can be designed differently for different valve seat materials. For example, the tip of the end face can also be machined to have an approximately circular radius. Depending on the valve seat material, and especially the hardness of the material, the tip may embed more or less into the valve seat, or undergo elastic deformation upon contact. This will affect the specific contact point and thus the valve's switching and sealing performance.

[0007] This leads to another drawback: the tip may deform depending on the pressure acting within the valve. Here, what is typically important for the specific contact point on the flange or valve seat is which side of the control tube is under pressure. The control tube may be nearly (but not completely) depressurized on one side, while under high pressure on the other. Depending on the design of the flange or control tube, the contact point may shift due to the applied sealing force or due to tip deformation. This results in coaxial valves typically having a predetermined flow direction, and thus a fixed installation orientation, and / or being conditionally back-pressure sealed only.

[0008] A similar disadvantage of this known approach is wear at the point where the actuator contacts the valve seat. This is especially true when the actuator's end face is designed to be very sharp and when the valve seat material is particularly inelastic and / or very hard. To ensure reliable sealing even with hard materials, the control tube often needs to be very firmly pressed against the valve seat. However, this can only be done to a certain extent, otherwise the control tube will damage the valve seat and / or the control tube tip, much like a stamping die. Furthermore, at the point where the actuator contacts the mating surface of the valve seat during valve switching, microscopic wear and / or damage can occur due to the mechanical load on the material. This adversely affects the valve's sealing performance, thus reducing overall valve performance. This is particularly detrimental if the valve is intended for very light gases (such as hydrogen, for example). Once the valve seat experiences a certain degree of wear, tiny hydrogen atoms or H2 molecules can pass through even the smallest damage and leak. Consequently, the valve becomes unsealed and is therefore unsuitable for such applications.

[0009] However, hydrogen is becoming increasingly important, especially due to the development of new drive technologies in the automotive industry. As an extremely light gas, hydrogen places particularly high demands on the valves used. This is also true, and particularly true, for applications involving pressures of, for example, 500, 1000, 1500 bar or higher. In such cases, even a tiny amount of non-sealing between the actuator and the valve seat can cause the valve to fail to seal. Therefore, until now, known valves have been unable, or rather, unable to handle the high pressures of hydrogen without significant limitations.

[0010] Furthermore, and more importantly, in known valves, the pressure acting when the valve is closed always still acts at least partially on the actuator. Because the actuator is pressed against the valve seat, the pressure effectively acts on the actuator as well, and further presses the actuator against the valve seat when the valve is closed. This is true even in coaxial valves that are approximately depressurized. This necessitates a large switching force or pressure to reopen the valve. This can sometimes lead to increased wear, which can further negatively impact the valve's sealing performance. Moreover, the outlet and inlet of such valves are not or difficult to interchange, meaning that these valves have a preferred flow direction.

[0011] The object of this invention is to provide a valve that does not have the disadvantages described above. In particular, the object is to provide a valve that can reliably operate with hydrogen or other fluids even under high pressure.

[0012] According to the present invention, the objective is achieved by means of a valve having the features of embodiment 1, wherein the valve has a valve seat that is sealingly abutting against the outer peripheral surface of the actuator in the first closed terminal position of the valve.

[0013] Because the valve has a seat, when the valve is closed, the seat seals against the outer peripheral surface of the actuator, eliminating the need for the actuator to press against the seat surface to achieve a seal, or even completely eliminating the need for the actuator to press against the seat surface. Therefore, mechanical wear and tear on the seat surface no longer limit and / or reduce the valve's sealing effect. Thus, the valve according to the invention is advantageously suitable for high operating pressures, especially for applications using very light gases (e.g., hydrogen). However, the valve and its operating principle according to the invention are also applicable to other fluids (e.g., other gases or liquids).

[0014] Other advantages are derived from the subordinate scheme.

[0015] In a particularly preferred embodiment, the valve seat is a generally annular structure with an inner diameter adapted to accommodate the actuator. During valve switching, the actuator can, for example, move into or out of the annular structure, thereby closing or opening the valve. In this case, the contact surface, as in conventional valves, can be completely eliminated.

[0016] In another equally preferred embodiment, the actuator is a tubular structure, particularly a hollow cylindrical structure, having a wall with two end faces and an outer peripheral surface, wherein the actuator has axially extending channels that penetrate at the ends of the actuator. Therefore, shafts or tubes with internal channels are particularly suitable as actuators, in which the end faces of the structure are arranged annularly around the openings of the channels.

[0017] In one embodiment, at both the first and second terminal positions, the first end of the actuator is hermetically inserted into a first cylindrical cavity of the housing, particularly by means of a seal. Similarly, at both the first and second terminal positions, the second end of the actuator is hermetically inserted into a second cylindrical cavity of the housing, also particularly by means of a seal. A connecting channel terminates in the cylindrical cavity and connects the cavity to the inlet and outlet. The cavity of the housing can be created, for example, by drilling, into which the actuator extends or is placed.

[0018] In a particularly preferred embodiment, at both terminal positions, the end face of the actuator does not contact the inner wall of the corresponding cavity, wherein, for this purpose, the first cavity and / or the second cavity each have at least one end wall, particularly a tapered end wall. The end wall may, for example, be disposed in the wall portion of the corresponding cavity opposite to the actuator. The end wall may be formed, for example, by drilling a hole a few millimeters deep (e.g., 3-5 mm), so that the end face or all end faces of the actuator are not in contact with the inner wall of the cavity, but are completely exposed.

[0019] This embodiment has a significant advantage: when the valve is closed, the medium flows through the actuator, and the pressure acting on both end faces of the actuator is exactly the same, given that both end faces are identical in size and shape. Since the valve's sealing effect is ensured by the valve seat surrounding the actuator, neither end face of the actuator needs to be in contact with the valve seat. Therefore, the applied pressure is evenly distributed across the entire actuator, preventing it from being pushed along a single preferred direction. The actuator thus achieves 100% or complete pressure relief. Therefore, even at high operating pressures, such as 2000 bar, switching of the actuator can be advantageously achieved with a smaller force.

[0020] In another embodiment, the valve seat is disposed in the first recess. The valve may be designed such that it closes as the actuator passes through the valve seat, and opens when the actuator is not disposed in the valve seat.

[0021] In a particularly preferred embodiment, in the first terminal position, the valve seat is sealed against the outer peripheral surface of the actuator, and in the second terminal position, the first end of the actuator is moved axially out of the valve seat, such that the actuator's passage is connected to the connecting passage. At this time, the valve is closed in the first terminal position and open in the second terminal position.

[0022] In another preferred embodiment, the actuator can be adjusted by a drive device. The drive device can be pressure-controlled, for example, via a control medium, and / or can be designed to be electromagnetic.

[0023] In another embodiment, the actuator forms a piston, or a piston is fixedly connected to the actuator, and the piston is disposed in a third cylindrical cavity of the housing, the third cavity being located between the other two cavities. The piston sealably separates the two working chambers, wherein the piston is reciprocating between its terminal positions by means of a control medium that can be introduced into the working chambers. In this case, the switching of the valve can be achieved, for example, by filling the two working chambers with a control medium (e.g., a control gas). Of course, it is also conceivable to use other control media (e.g., liquids).

[0024] If a working chamber is filled with control medium, the piston, and thus the actuator, adjusts to increase the volume of that chamber. To adjust the actuator in the opposite direction, another chamber is filled with control medium accordingly. Of course, each chamber must have a corresponding inlet and outlet. It has been surprisingly shown that even at very high pressures (e.g., 1000 bar, 1500 bar, or 2000 bar) acting on the valve, a lower switching pressure, such as 5-10 bar, is sufficient to achieve valve switching. This is particularly due to the fact that the actuator is 100% or completely depressurized even in the closed state. Therefore, the sealing force has no effect during valve switching. The switching pressure only needs to overcome the friction of the actuator and, if necessary, the spring force of the spring.

[0025] In another embodiment, the structure rests against surfaces within a third cavity at the first and second end positions of the actuator, respectively, such that these surfaces limit the axial adjustability of the actuator. This allows the respective end positions of the actuator to be defined without requiring the actuator's end face to rest against a surface within the housing.

[0026] In another embodiment, the third cavity is sealed to the other two cavities by a seal (especially an O-ring, a pneumatic sealing flange, or a radial shaft seal). For example, the actuator may be partially disposed in or located within the first, second, and third cavities. For this purpose, dynamic seals must be provided to seal the cavities to each other. The dynamic seals can be of any form that meets the requirements for sealing effectiveness and wear for the corresponding medium and pressure. Here, in principle, piston seals and rod seals can be envisioned, either fixedly disposed within the housing or fixedly disposed within the actuator and actuated during adjustment.

[0027] In a particularly preferred embodiment, at least one sealing device includes a support ring and a grooved ring, and more particularly, two sealing devices include a support ring and a grooved ring, wherein an actuator is adjustably disposed within the sealing device. The support ring may, in particular, be disposed within a recess provided for this purpose within the housing, and the support ring is sized such that it abuts against the housing wall radially outward and against the actuator radially inward. Thus, the support ring supports the seal in the form of a grooved ring and simultaneously constitutes a guide structure for the actuator. The grooved ring may, for example, be fitted onto the support ring and constitute the seal, while the support ring automatically centers and holds the seal in place.

[0028] In principle, an embodiment could also be conceivable in which at least one sealing device is disposed on the actuator. The sealing device could be a piston seal. However, especially when using low-density gases, the requirements for the sealing surface are very high. Therefore, in this embodiment, the focus must be on the recess in which the piston seal is adjusted.

[0029] In another embodiment, the grooved ring is made of polyurethane, such as hydrolysis-resistant thermoplastic polyurethane (H-ECOPUR). Such grooved rings are commercially available and therefore readily available.

[0030] In a particularly preferred embodiment, the valve seat is made of a high-performance plastic, such as polyetheretherketone (PEEK), or the valve seat has a component made of said high-performance plastic. This material is particularly suitable for valve seats because it meets the high requirements for machinability, abrasion resistance, and sealing performance when using hydrogen.

[0031] In another embodiment, the valve is a coaxial valve, meaning the inlet and outlet are located on a common axis. Of course, in this case, the valve's inlet and / or outlet, or the corresponding channel, must be diverted if necessary to achieve a coaxial interface. However, especially for light gases (such as hydrogen), such diversion poses little or no disadvantage to the valve's performance.

[0032] In another embodiment, the inlet can also be used as an outlet, and in this case, the outlet can be used as an inlet. This can be achieved, in particular, by a fully depressurized embodiment of the valve, since the actuator is not forced into a specific position by the applied pressure when the valve is closed. Back pressure and sealing force no longer play a role in this embodiment. Therefore, it is not important which side of the valve the pressure acts on. This allows for extremely flexible use of the valve, and when the valve is properly designed, erroneous installations, such as reversed flow direction, are avoided.

[0033] In another embodiment, the valve additionally has at least one channel terminating in a cavity region between the two sealing devices, and this channel is used to monitor and measure leaks. In this way, leaks can be detected, and in the case of using multiple channels, each corresponding to exactly one seal, a specific seal corresponding to the leak can also be identified.

[0034] In another embodiment, the valve has a spring that is operatively connected to the actuator, either directly or indirectly, and holds the actuator in a first or second terminal position when no force is applied to the actuator by the drive mechanism, or only a very small force is applied. Here, the force refers to the force applied to the actuator to switch the valve. This can be, in particular, the pressure of the control medium acting on the piston of the actuator.

[0035] Depending on the design and arrangement of the spring, the valve can be designed to be normally closed or normally open. Alternatively, the valve can also have a limit switch to monitor the valve's position.

[0036] In another embodiment, the actuation device may additionally or alternatively include a magnet, thereby enabling the valve to open or close magnetically. Of course, in this configuration, the valve may be designed to both open and close without power.

[0037] In the valve according to the invention, more than two ports and more than two switching positions may be provided. Therefore, the inlet and / or outlet may also be formed by at least two ports. For example, the valve may have a total of three ports, one forming an inlet and two other ports each forming an outlet. The valve may also have more than one inlet and / or more than one outlet, and these inlets and / or outlets may be interconnected in different ways.

[0038] Different configurations of the valve can be achieved by changing the number and arrangement of the sealing devices, seals, and interfaces, and by adjusting the switching positions of the actuator. For example, one interface can constitute an inlet, and two interfaces can constitute an outlet, wherein the valve is closed in one switching position of the actuator. In a second switching position, the two interfaces constituting the outlet can be opened. In this example, the valve is constructed as a possible two-position three-way valve.

[0039] Similarly, it's possible that one interface constitutes an inlet, and two other interfaces each constitute an outlet, with the actuator connecting the inlet to the first outlet in a first switching position and connecting the inlet to the second outlet in a second switching position. This is also a two-position three-way valve, but a variation thereof.

[0040] In the aforementioned 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 three-position three-way valve.

[0041] It's also possible that two interfaces form the inlet, and another interface forms the outlet. Of course, different switching positions for interfaces with different connection types can also be implemented here. More than three interfaces can also be provided, such as in a three-position five-way valve.

[0042] The actuator can also have different designs. For example, the actuator may have one or more openings in its wall, such as holes. These lateral openings can function as branches of the actuator's channels and provide options for additional, more complex connections to other interfaces. Thus, these openings can each correspond to one or more interfaces, thereby providing the possibility of setting more switching positions for different configurations.

[0043] For example, the actuator may have two or more openings, each of which is assigned to exactly one interface. For instance, a first interface can be activated in a first switching position, and a second interface can be activated in a second switching position. This further reduces the switching distance the actuator must traverse and / or allows for the connection of multiple interfaces.

[0044] The actuator may also have multiple openings, with at least two openings having different cross-sections. Therefore, the flow rate through one or more interfaces can be varied, allowing one opening to allow a larger flow rate while another allows a smaller flow rate. These openings may also correspond to one, multiple, or the same interface, respectively.

[0045] In some variations, the actuator may have at least one opening with a non-rotationally symmetric cross-section. Here, non-rotationally symmetric specifically refers to a cross-section whose flow cross-section changes relative to the corresponding interface.

[0046] Therefore, the opening can, for example, have a generally triangular cross-section, in which, in the first switching position, only the apex of the triangle allows fluid flow to the corresponding interface. As the actuator moves, the triangular cross-section releases a gradually increasing flow opening, thus continuously increasing the flow rate to that interface. Furthermore, a metering valve and / or regulating valve can be implemented in this way. It is also possible that the actuator configured as a control tube can not only adjust axially but also rotate about its longitudinal axis to be in different switching positions, wherein a corresponding drive device and, if necessary, a transmission mechanism must be provided. Thus, for example, it is conceivable that the control tube may have partially or completely circumferential teeth on its cylindrical outer wall, by means of which the control tube can rotate about its axis. Furthermore, an axial adjustment drive device can be provided.

[0047] The present invention also relates to a valve seat for use in a valve according to the present invention.

[0048] In a particularly preferred embodiment, the valve seat is generally annular, and in particular, has a mirror-symmetrical cross-section. Because the valve seat is generally annular, the actuator can be moved into the valve seat without abutting against the valve seat surface. The valve seat can also, in particular, have a mirror-symmetrical cross-section, thus allowing it to function equally on both sides.

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

[0050] In another embodiment, the outer peripheral surface of the valve seat is provided with a circumferential groove for receiving a seal (such as an O-ring). The seal may, for example, improve the sealing effect and / or hold the valve seat in place.

[0051] In another particularly preferred embodiment, at least one, especially both, axial end faces of the valve seat have recesses or grooves, particularly circumferential ones. These grooves distribute the pressure acting on the valve seat radially inward and outward, thereby enhancing the sealing effect under pressure. This also prevents pressure from acting solely in the axial direction, which could lead to valve seat damage or slippage. In the case of a mirror-symmetrical valve seat, the grooves can be equally positioned on both end faces of the valve seat.

[0052] In another embodiment, the recess or groove forms a sealing lip. This sealing lip can then be pressed against the actuator or housing wall by the applied pressure in the manner described above, further enhancing the sealing effect.

[0053] In another preferred embodiment, the valve seat has at least one, particularly two, circumferential protrusions on its radially inward side, which form a sealing flange. The sealing flange can be configured such that the applied pressure presses the sealing flange against the actuator through a recess on the end face, thereby further enhancing the sealing effect.

[0054] In a particularly preferred embodiment, the valve seat is made of a high-performance plastic, especially polyetheretherketone (PEEK). This material meets high requirements for sealing performance, strength, processability, and coefficient of friction; therefore, the valve seat is also suitable for high pressures, especially for the high pressures of hydrogen.

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

[0056] In one embodiment, the support ring has a first circumferential segment extending in an axial direction, the first segment having at least one radially inner face and at least one radially outer face, the radially inner face extending substantially parallel to the longitudinal axis of the support ring, and the at least one radially outer face extending relative to the longitudinal axis of the support ring at an angle greater than 0°, particularly between 10° and 80°. An angle of 45° ± 10° is particularly suitable. Such support rings are known and commercially available. Such support rings, in particular, are available with adaptable grooved rings. According to the invention, the support ring additionally has at least one second axially extending segment, the second segment being particularly cylindrical, the outer diameter of the second segment being larger than the maximum outer diameter of the first segment.

[0057] The dimensions of the at least second section of the support ring can be designed such that the second section abuts against the housing wall on the outer side and against the actuator on the inner side. Therefore, in addition to the support and retention functions of a grooved ring, the support ring also performs a guiding function for the actuator.

[0058] In another embodiment, a first segment of the support ring can be inserted into or pushed into a receiving portion of the grooved ring. The dimensions of the first segment are particularly designed to allow its use with conventional and commercially available grooved rings.

[0059] In another embodiment, the second segment has a first abutment surface for abutting the grooved ring. In this way, the support ring can also support the installed grooved ring in the axial direction.

[0060] In another embodiment, the second section has a second abutment surface for abutting against a wall portion of the valve housing. In this way, the support ring can be supported axially by the wall portion of the housing.

[0061] Several embodiments of the present invention will now be described in detail with reference to the accompanying drawings. Of course, the present invention is not limited to the embodiments shown.

[0062] in: Figure 1a A transverse sectional view of the valve according to the present invention; Figure 1b and Figure 1a The same valve in the open state; Figure 2 A cross-sectional view of the valve shown in Figure 1 is shown in another view; Figure 3 Figure 1 shows a detailed view of the valve seat and sealing device; Figure 4 Figure 1 shows an external view of the valve; Figure 5a A transverse sectional view of the valve seat according to the present invention; Figure 5b Figure 5a A perspective view of the valve seat shown; Figure 6a A transverse sectional view of a sealing device having a support ring and a grooved ring according to the present invention; Figure 6b Figure 6a A three-dimensional view of the support ring shown; Figure 7a Another valve according to the invention is shown in a transverse sectional view from two different perspectives; Figure 7b Figure 7a The valve shown is a cross-sectional view in the open state; Figures 8a-8c A schematic embodiment of a valve configured as a three-position three-way valve in three different switching positions; Figures 9a-9c Schematic embodiments of a valve configured as a three-position three-way valve are shown in three different switching positions, the valve having an actuator having an orifice in its wall; Figure 10a , 10b The two switching positions show variations of the actuator with openings of different sizes; Figure 11a , 11b Another variation of the actuator with a non-rotationally symmetric opening; Figure 12a ,12b Another variation of the actuator is that the actuator can be rotated to different switching positions; Figure 12c A schematic diagram of a sealing device used for a rotatable actuator.

[0063] Figure 1a A cross-sectional view of a valve 1 according to the present invention is shown. The valve 1 has a housing 2 comprising multiple parts, the housing 2 having an inlet I and an outlet O. The valve 1 is provided with an actuator 3 in the form of a hollow cylinder. The actuator has a wall portion 3'', the wall portion 3'' having an outer peripheral surface 3'. A channel 3a is provided in the actuator 3, thereby enabling the medium to flow through the actuator 3. In the illustrated configuration, the valve 1 is closed, and the actuator 3 is in a first terminal position. At this time, the first end portion 3b of the actuator 3 is located in a first cavity H1 of the housing 2. Correspondingly, the second end portion 3c of the actuator 3 is located in a second cavity H2 of the housing 2. The cavities H1 and H2 are connected to the outlet O and the inlet I via channels K1 and K2, respectively.

[0064] The first end 3b of the actuator 3 is located in an annular valve seat 4, which seals the passage 3a of the actuator 3 relative to the outlet O. Therefore, the valve seat 4 constitutes a seal in this case. Valve 1 is closed and no medium flows from inlet I to outlet O. The valve 1 shown is configured laterally, meaning that outlet O and inlet I are not on a common axis. It should be noted again that the valve can also be designed as a coaxial valve. In this case, it requires a proper reversal of inlet I or outlet O. As already explained, this reversal has almost no disadvantage, especially when using light gases (such as, for example, hydrogen), or in some cases, the advantages of the coaxial arrangement outweigh the disadvantages of the reversal.

[0065] The cavity H1 has a tapered end wall H1', ​​which is formed by drilling, so that the first end face F1 of the actuator 3 is not in contact with the inner wall H1'' of the cavity H1 but is substantially exposed. A pressure P exists at the inlet I of valve 1. Because the end face F1 of the actuator 3 is exposed, the pressure P acts uniformly on the end face F1 and the other opposing end face F2 of the actuator 3. Therefore, there is no net pressure acting on the actuator 3 in the axial direction; that is, there is no net pressure acting on the actuator 3 in the axial direction in both the closed state shown for valve 1 and the open state (not shown). Thus, the actuator 3 is in a depressurized state with respect to the applied pressure P at any given time.

[0066] Furthermore, a piston 5 is provided on the actuator 3, which is used to adjust the actuator 3. The piston 5 is adjustablely disposed in the third cavity H3 of the housing 2 and held in the first terminal position shown by the spring 6. Therefore, the valve 1 shown is normally closed. Of course, the valve 1 can also be designed to be normally open. The piston 5 rests against the housing wall 2a, thereby defining the first terminal position of the actuator 3.

[0067] An additional sealing device is provided along the actuator 3, which seals the cavities H1, H2, and H3 to each other. The sealing device shown in Figure 1 is fixedly mounted on the housing 2, thereby fixing its position relative to the actuator 3. Of course, it is also conceivable to use a sealing device (e.g., in the form of a piston seal) that is fixedly mounted on the actuator 3.

[0068] The sealing device shown is sealing device 7, which has a support ring 7a and a grooved ring 7b according to the invention. Furthermore, the valve 1 shown also has additional sealing devices in the form of O-rings 8 and 8'. Channels 9 for monitoring and measuring leakage are respectively provided between the O-ring 8 and the sealing device 7. The O-ring 8' is disposed on the piston 5 and seals the two working chambers A1 and A2 of the cavity H3 relative to each other.

[0069] Figure 1b Showing with Figure 1a The same valve is used, but the actuator 3 is in the second terminal position. Therefore, valve 1 is open. To this end, pressure medium is introduced into the working chamber A1 of the cavity H3, causing the piston 3 in the third cavity H3 to move against the spring force of the spring 6 until the piston 5 is against the housing wall 2b. At this time, the working chamber A2 of the cavity H3 decreases. The first end 3b of the actuator has moved out of the valve seat 4, so that the passage 3a of the actuator 3 is connected to the outlet O. Therefore, the valve is open.

[0070] Figure 2 This shows from another perspective... Figure 1a The same valve 1. Two channels 10a and 10b are shown in the figure. These channels 10a and 10b are used to fill the working chambers A1 and A2 of the cavity H3 with control medium. In the position shown, valve 1 is closed. If valve 1 should be opened, control medium (e.g., gas) is supplied through channel 10a, causing piston 5 to move axially against the spring force of spring 6 until piston disc 5 abuts against the wall 2b of housing 2 (e.g., gas). Figure 1b(As shown). This defines the second terminal position of actuator 3. As piston 5 moves, the pressurized medium must simultaneously be discharged from working chamber A2 through channel 10b. To close valve 1, it is sufficient to cut off the pressure in channel 10a so that spring 6 moves piston 5 to its initial position, or additionally, pressurized control medium is supplied to channel 10b to assist or accelerate the closing process. It is evident that channels 10 and 10b can or must serve as both inlets and outlets.

[0071] Figure 3 A detailed view is shown of the valve seat 4 and the actuator 3 arranged on the valve seat 4. The actuator 3 rests against the valve seat 4 with its outer peripheral surface 3'. In the closed position shown, the valve seat 4 seals the passage 3a relative to the outlet O. At the same time, the tapered end wall H1' ensures that the first end face F1 remains exposed. Thus, the pressure P applied at the inlet I acts uniformly on the first end face F1 and the opposing end face F2 (not shown). Therefore, even in the closed position of the valve 1, the actuator 3 is depressurized, and thus, relatively speaking, a smaller switching force is sufficient to switch the valve when high pressure is applied. Since the actuator 3 does not rest against the valve seat surface as in currently known solutions, the problem of wear on the contact surface is also avoided. Therefore, the valve 1 according to the invention is also suitable, and especially, for particularly low-density gases (such as hydrogen) under high pressure. If the actuator 3 is adjusted and displaced from the valve seat 4 as described above, the outlet O communicates with the passage 3a and thus with the inlet I, and the valve 1 is thus opened.

[0072] The valve seat 4 has a groove 4a surrounding it, which is used to accommodate an O-ring (not shown). This stabilizes the valve seat 4 and improves the sealing effect. Both end faces of the valve seat 4 have circumferential recesses 4b in the form of grooves, thereby providing sealing lips 4c. If pressure is applied to the end faces, this pressure is redirected towards the sealing lips 4c, and the sealing effect is enhanced by pressing the sealing lips 4c against the outer peripheral surface 3' of the actuator 3 or against the wall of the housing 2.

[0073] In addition, the ends 3b and 3c of the actuator 3 also have a tapered section 3d to prevent damage to the valve seat 4 when the actuator 3 is moved in and out.

[0074] Figure 3 The diagram also shows a sealing device 7 having a support ring 7a and a grooved ring 7b, the grooved ring 7b being fitted onto the support ring 7a. The support ring 7a has a segment 7g, the outer diameter of which is larger than the outer diameter of a tapered segment 7c arranged adjacent to the segment 7g. Thus, the support ring 7a serves both as a guide structure and as a support structure for the grooved ring 7b. (The diagram will also be combined with...) Figure 6a , 6b The specific design of the support ring will be further explained.

[0075] The grooved ring 7b is a seal with two sealing lips made of thermoplastic polyurethane. When valve 1 is open, the sealing device 7b seals cavity H1 relative to cavity H3, wherein the sealing lips are pushed apart by pressure. The support ring 7a simultaneously stabilizes the grooved ring 7b, preventing slippage or compression. This configuration has been proven to withstand thousands of switching operations and operate reliably at extremely high pressures of 1000 bar and above, especially when using hydrogen.

[0076] Figure 4 An external view of valve 1 is shown, which has a cylindrical housing 2, an inlet 1, and an outlet 0. Furthermore, control interfaces leading to the channels 10a and 10b are visible on the side wall of the housing 2. Also shown are contacts 11 for a limit switch (not shown).

[0077] Figure 5a A transverse sectional view of a valve seat 4 according to the invention is shown. The valve seat 4 has a circumferential groove 4a on its outer peripheral surface for receiving an O-ring. Furthermore, both end faces also have circumferential recesses 4b for distributing the applied pressure. The recesses 4b are configured such that the end faces of the valve seat have sealing lips 4c, which are pressurized when pressure is applied, thus enhancing the sealing effect of the valve seat 4. Additionally, the valve seat 4 has two protrusions 4d on its radially inwardly located side surface, which form sealing flanges and abut against the actuator 3 in the assembled state. When pressure is applied, the sealing flanges are pressed against the outer peripheral surface 3' of the actuator 3.

[0078] Figure 5b The valve seat 4 of the present invention is shown in a three-dimensional external view.

[0079] Figure 6a A transverse sectional view of the support ring 7a of the sealing device 7 according to the invention is shown. A grooved ring 7b is shown beside the support ring 7a, which is fitted onto the support ring 7a in the assembled state. The support ring 7a has a first segment 7c extending in the axial direction. The first segment 7c is inserted into the receiving portion 7d of the grooved ring 7b. Furthermore, the first segment 7c has a radially outwardly inclined surface 7e. The support ring 7a has a radially inwardly extending surface 7f parallel to the longitudinal axis of the support ring 7a. This surface 7f abuts against the outer peripheral surface 3' of the actuator 3.

[0080] According to the present invention, the support ring 7a additionally has a second section 7g, the outer diameter of which is larger than the maximum outer diameter of the first section 7c. The second section 7g is sized such that it forms a guide structure between the housing wall and the actuator 3. Furthermore, the second section 7g also has a surface 7h and a surface 7i, the surface 7h abutting against the housing wall and the surface 7i abutting against the grooved ring 7b. Through the features described above, the support ring automatically centers between the housing 2 and the actuator 3 and simultaneously stabilizes the grooved ring 7b, thereby forming a reliable sealing structure. The grooved ring 7b is a commercially available grooved ring with two surrounding sealing lips 7j.

[0081] Figure 6b The support ring 7a of the present invention is shown in a perspective view.

[0082] Figure 7a Another embodiment of the valve 1 of the present invention is shown in two different transverse sectional views. Most of the features are similar to... Figure 1a The embodiment described above is the same. The only difference is that inlet I is located on the side opposite valve 1, thus... Figure 1a Compared to the illustrated embodiment, the path between inlet I and outlet O is significantly shorter. Correspondingly, the second cavity H2 of housing 2 has a tapered end wall H2', whereby actuator 3 is depressurized in the second terminal position (i.e., in the open state). Therefore, the end face F2 of actuator 3 is exposed in the second terminal position. Limit switch 11a detects whether the valve is closed or open via contact 11.

[0083] Figure 7b Show Figure 7a The valve in the middle is in the open position. Similar to... Figure 1b In the position shown, actuator 3 moves together with piston 5 to the second terminal position. In this position, inlet I and outlet O are directly interconnected through cavity H1, meaning that the medium does not need to flow through channel 3a of actuator 3 to reach outlet O from inlet I. Due to the tapered end wall H2' of cavity H2, the second end face F2 of actuator 3 remains exposed and does not contact the inner wall H2''. Thus, actuator 3 is also depressurized in this position. At this time, limit switch 11a connects to another contact and is thus detected, therefore, valve 1 is open.

[0084] The advantage of this embodiment is that the nominal diameter of the valve is not determined by the channel 3a of the actuator 3, but by the cavity H1. The cavity H1 has a diameter that matches the outer diameter of the actuator 3. Therefore, the nominal diameter of the valve shown no longer depends on the control pipe 3 or the inner diameter of the control pipe 3. Figure 1aIn the illustrated embodiment, if it is desirable to increase the passage 3a in the actuator to increase the nominal diameter of the valve, the actuator 3 must be designed to be more stable and the outer wall 3'' must be designed to be thicker to prevent damage or deformation of the control tube. As a result, the control tube, and consequently the valve, quickly becomes very large, expensive, and impractical, or in some cases, completely impossible to manufacture.

[0085] In the illustrated embodiment, channels K1 and K2 are narrower than cavity H1. Therefore, the flow velocity inside the valve is reduced. It should be noted that the channel 3a inside the actuator 3 is still necessary for pressure relief. However, in this case, the diameter of channel 3a is not important. In particular, channel 3a has no effect on the nominal diameter of the valve.

[0086] Figures 8a to 8c Another possible embodiment of the pressure relief valve 100 of the present invention is illustrated schematically. The actuator 3, valve seat 4, seal 8, and sealing devices 7, 7a, 7b are in principle identical to the corresponding previously described components of the previously described embodiment. Figure 1a The illustrated embodiment differs from the standard one; this embodiment is a three-position three-way valve, meaning that the valve has three ports A, B, and C and three switching positions. Port A can be used, for example, as inlet I, and ports B and C can be used as outlets O. The passage K is closed at both ends E.

[0087] exist Figure 8a The diagram shows the first switching position, in which valve 100 is closed. A pressure P acts at inlet O (port A), and this pressure P is distributed from the left side of the housing 2 through the tubular actuator 3 to the right side of the housing, and acts on valve seat 4 from the right side of port C. Pressures P0 act at ports B and C, where P > P0. Therefore, valve seat 4 seals port C relative to port A in a manner described in the preceding embodiments, preventing fluid from flowing from inlet I to outlet O.

[0088] Similarly, the valve seat 4 on the left side of interface B also bears the pressure P acting on interface A, sealing interface B relative to interface A. Instead of a valve seat 4 between interfaces B and C, a sealing device 7 of the type described earlier is provided. This sealing device 7 includes a support ring 7a and a grooved ring 7b. The actuator 3 is slidably supported on, or adjustablely disposed on, the sealing device 7, wherein the actuator 3 is disposed on the sealing device 7 in each switching position. As an auxiliary measure, two O-ring type seals 8 are provided between interfaces B and C, and between interfaces A and B, respectively. Another valve seat 4 is disposed next to interface 4.

[0089] The actuator 3 can be adjusted to two other positions using an adjusting device (not shown). The adjusting device can, in principle, be any suitable adjusting device, especially a pneumatic, hydraulic, or magnetic one. Of course, the valve 100 can be designed to open or close without power, depending on the structure of the adjusting device.

[0090] Figure 8b The valve 100 is shown in the second switching position. An adjusting device (not shown) has adjusted the actuator 3 to the right. Therefore, port B is released, while port C remains closed. Port C is sealed by the sealing device 7 on the left side of the figure, the additional seal 8 between ports B and C, and by the valve seat 4 adjacent to port C on the right side. Thus, in the shown switching position, port A constitutes the inlet I of valve 100, and port B constitutes the outlet O of valve 100.

[0091] Figure 8c The diagram shows the third switching position of valve 100. An adjusting device (not shown) has adjusted actuator 3 to the third position, in which port B is sealed relative to ports A and C. Therefore, fluid flow can proceed from port A to port C, which thus forms outlet O. Actuator 3 has thus moved into valve seat 4 on the left side of the diagram. This seal of port B is achieved through valve seat 4 on the left and sealing device 7 on the right side of the diagram.

[0092] In all switching positions, the actuator 3 is embedded in or axially movable within the two sealing devices 7. Conversely, in each switching position, the actuator 3 is removed from at least one valve seat 4.

[0093] certainly, Figures 8a to 8c The illustrated embodiment can also be designed as a two-position three-way valve, in that the actuator 3 can only be adjusted between two switching positions. For example, it can only be adjusted to... Figure 8b and Figure 8c The valve 100 has two switching positions, allowing it to switch between ports B and C, where one of ports B and C forms an open outlet O at exactly one switching position. In this configuration, the valve 100 is never closed; it simply switches the fluid flow from A to B or C. The valve seat 4 in the middle of the diagram can be omitted in this case.

[0094] Similarly, other structural forms can be achieved, such as a three-position five-way valve. Furthermore, the arrangement and quantity of the valve seat 4, sealing device 7, and seal 8 can be changed according to requirements, pressure, and interface configuration, and adapted to corresponding conditions. Therefore, the illustrated embodiments do not constitute any limitation, but are merely illustrative of how a multi-way valve can be constructed and switched using the valve seat 4 and sealing device 7 according to the present invention.

[0095] Figure 9a and 9b Another possible embodiment of valve 1000 is shown. Valve seat 4, sealing device 7, and seal 8 also correspond to the components described above. However, unlike the previously described embodiment, the actuator 3000 has two additional holes Ha and Hb in its wall 3'', through which fluid can also flow laterally from channel 3a.

[0096] exist Figure 9a In this configuration, valve 1000 is closed. Pressure P acts at interface A, and as in the previously described embodiment, this pressure P is also guided to the section to the right of interface C via channel 3a of actuator 3000. Valve seat 4 seals interfaces B and C relative to interface A, respectively. Figures 8a to 8c Unlike the previous embodiment, this pressure P is additionally distributed to the middle region of the housing 2 through an opening or orifice Ha, which is located between ports B and C. Therefore, ports B and C are also sealed relative to port A by sealing devices 7 and seals 8 disposed in this region. In particular, of these four sealing devices 7, the two middle sealing devices 7 in the figure are responsible for sealing ports B and C by oriented the grooved rings 7b of the sealing devices toward the pressure side P as described above. Since the actuator 3000 does not leave or move from the valve seat 4 on the left side of the figure in any switching position, the valve seat 4 can also be replaced by the sealing devices 7.

[0097] It is understandable that other combinations / arrangements / quantities of the seal 8, sealing device 7, and valve seat 4 can be envisioned and implemented, and are advantageous where necessary, so that the valve 1000 can be adapted to the pressure used and the requirements in terms of sealing.

[0098] Figure 9b Showing with Figure 9a The same valve 1000 is used, but the actuator 3000 has been adjusted to a second switching position by an adjustment device (not shown). The two orifices Ha and Hb are now at the height of interfaces B and C, thereby enabling fluid flow from interface A to interfaces B and C. Thus, in the position shown, interface A constitutes the inlet I for valve 1000, and interfaces B and C respectively constitute the outlet O for said valve 1000.

[0099] Of the four sealing devices 7, the two sealing devices arranged on the outside in the figure seal interface B relative to interface C. Depending on the configuration of each interface, especially when the flow rates of the two interfaces B and C are the same and the same pressure is applied, these two sealing devices 7 may be redundant or unnecessary as needed, and depending on whether a sealing function is required for the function of valve 1000 at this position, these two sealing devices can be omitted or replaced with conventional sealing devices.

[0100] When the pressure P is very high, as the orifices Ha and Hb pass through two side-by-side sealing devices 7 rotated 180° relative to each other, the pressure P may act between the two sealing devices 7. In this case, the high pressure P acts on the sealing device 7 not on the side designed for this purpose, i.e., on the support ring 7a side, but on the grooved ring 7b side. One possible solution to this problem is to depressurize the valve 1000 when this passage occurs. Similarly, it is conceivable and feasible to provide at least one balancing passage X between these sealing devices to balance or release the overpressure P between two adjacent sealing devices 7. The at least one balancing passage X may be closable and, if necessary, must be closable.

[0101] exist Figure 9c In the middle, actuator 3000 is adjusted to the third switching position. Orifice Ha is in the same housing section as interface A, and therefore has no effect in this switching position. Pressure is again introduced into the housing section between the two interfaces B and C through orifice Hb. Interface B is connected via valve seat 4 on the left side of the figure and as shown in the figure. Figure 9a As explained, through (in) Figure 9c The sealing device 7 (marked with reference numerals in the attached diagram) seals relative to interface A. Therefore, no fluid flows from interface A to interface B.

[0102] In this switching position, a path from interface A to interface C can be established through channel 3a of actuator 3000. Therefore, interface C constitutes outlet O in this switching position. Thus, the illustrated embodiment is also a three-position three-way valve with three interfaces and three switching positions.

[0103] Of course, this embodiment can also be adapted variably, for example, by changing the number and arrangement of the interfaces, switching positions, sealing devices, and valve seats. For example, the valve can also be configured as a two-position three-way valve with only two switching positions. Valves 100 and 1000 can also be configured as coaxial valves such that end E is not closed. In this case, by adjusting actuators 3 and 3000, for example, the lateral interfaces A, B, and C can be connected or disconnected, in which case end E constitutes a normally open inlet I or outlet O, respectively.

[0104] Figure 10a and 10b An example of another possible variation of actuator 3000' is shown. For clarity, the remaining components of the valve are not shown, and the locations of interfaces A, B, and C are shown only schematically. Actuator 3000' has multiple orifices Ha', Hb', and the rest is designed as described in the previous embodiments. Figure 10a As shown in the switching positions, the first hole Ha' is at the height of interface B and the second hole is at the height of interface C. Therefore, fluid flow can proceed from interface A to either interface B or interface C.

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

[0106] Figure 10b The same actuator is shown in the second switching position, where the second orifice Hb' is at the height of interface B. This means that the flow rate to interface B is smaller in this switching position compared to the first switching position. Conversely, in this switching position, fluid flow from interface A to interface C can be achieved through channel 3a, therefore, the flow rate to interface C is larger in this switching position compared to the first switching position. Thus, the valve is a two-position three-way valve, wherein these two switching positions regulate the flow rate to interfaces B and C. Of course, this embodiment can also be adjusted, i.e., other switching positions may exist, for example, an additional "closed" switching position may exist.

[0107] Figure 11a and 11b Another alternative for actuator 3000'' is shown. The two holes Ha'', Hb'', or openings are constructed not circularly or rotationally symmetrically, but rather in a roughly triangular configuration. Figure 11a The switching positions shown have only the apex of the triangle located at the height of one of interfaces B and C. Therefore, the traffic to interfaces B and C is relatively small. Figure 11b The switching position shown has the wider end of the triangle at the height of interfaces B and C, and the flow rate to interfaces B and C is correspondingly larger. Of course, an intermediate switching position can also be set, which can also achieve gradual stepless adjustment of the actuator 3000'. Therefore, in particular, but not limited to, various variations of the metering valve and regulating valve can be implemented using the illustrated embodiment.

[0108] Figure 12a and 12bAnother alternative to actuator 3000''' is shown. Opening Ha''' includes two holes arranged side by side circumferentially. Opening Hb''' includes only one hole. In the shown switching position, the hole above opening Ha''' in the figure corresponds to interface B. For this purpose, for example, a channel corresponding to interface B can be provided in a sealing device (not shown) that seals the hole below the figure relative to interface B and communicates the hole above this hole in the figure with interface B. Therefore, in the shown switching position, interface B constitutes an outlet O with a smaller flow rate.

[0109] Unlike the variant described above, actuator 3000''' adjusts to the second switching position by rotating about its longitudinal axis AX. Figure 12b In this position, the actuator 3000''' is in the second switching position. In this position, both openings Ha''' of the opening correspond to interface B. At this time, the corresponding channels in the sealing device (not shown) must be designed such that they connect the two openings Ha'''' to interface B. Therefore, the flow rate to interface B is greater compared to the first switching position.

[0110] The second opening Hb''' corresponds to interface C with its single orifice in this switching position. Therefore, interface C also constitutes outlet O in this switching position. Since opening Hb''' is only a single orifice, the flow rate is less than that of interface B. Of course, a variation can be adopted in which both openings Ha''' and Hb''' are constructed identically, thus the valve has a closed switching position and a switching position in which both interfaces B and C are open. It is also possible that the two openings are identical but oriented offset from each other in the circumferential direction. In this way, the valve can, for example, have three switching positions, in which the valve is closed in the first switching position. In the other two switching positions, one of interfaces B and C is opened respectively, and at this time, the flow rate of the two interfaces is the same in the respective open switching positions.

[0111] Of course, this variant solution can also be changed and adapted to different switching locations and interface configurations.

[0112] Figure 12cAn example of a sealing device 4''' that can be used in conjunction with an actuator 3000''' is schematically shown. The sealing device 4''' is similar to a valve seat 4 or a surrounding sealing ring and is immovably disposed in the region of interface B. The sealing device 4''' has a channel 4a''', which corresponds to interface B. An orifice H is arranged in the actuator 3000''' (shown only schematically), and the orifice H can communicate with or be sealed relative to the channel 4a''' by rotation of the actuator 3000'''. A sealing device 4''' may also be provided in the region of interface C, having the same channel or different channels in cross-section.

[0113] Of course, the aforementioned technical features and associated advantages can be combined in a technically reasonable manner. The valve according to the invention can thus be adapted to different requirements, pressures, and interface combinations. Furthermore, multiple inlets I can be provided instead of multiple outlets O. Additionally, the valve can also have multiple inlets I and multiple outlets O, which can be switched between each other in different ways and forms by appropriately modifying the aforementioned technical features.

Claims

1. A valve (1, 100, 1000), particularly a hydrogen valve, said valve (1, 100, 1000) having at least one inlet (I) and at least one outlet (O), a housing (2), and an actuator (3) disposed in said housing (2), wherein, The actuator (3) is adjustable to at least one first terminal position (valve closed) and at least one second terminal position (valve open), and the valve (1, 100, 1000) has a control device for adjusting the actuator (3), characterized in that the valve (1) has a valve seat (4), and in the first terminal position when the valve (1) is closed, the valve seat (4) is sealed against the outer peripheral surface (3') of the actuator (3).

2. The valve (1, 100, 1000) according to claim 1, characterized in that, The valve seat (4) is a generally annular structure with an inner diameter suitable for accommodating the actuator.

3. The valve (1, 100, 1000) according to claim 1 or 2, characterized in that, The actuator (3) is a tubular structure, especially a hollow cylindrical structure. The actuator (3) has a wall (3'') with two end faces (F1, F2) and an outer peripheral face (3'). The actuator (3) has an axially extending channel (3a) that passes through the ends (3b, 3c) on the end side of the actuator (3).

4. The valve (1, 100, 1000) according to claim 3, characterized in that, At both the first and second terminal positions, the first end (3b) of the actuator (3) is sealed into the first cylindrical cavity (H1) of the housing (2), and the first end (3b) of the actuator (3) is sealed into the first cylindrical cavity (H1) of the housing (2) in particular by means of seals (7, 8). At both the first and second terminal positions, the second end (3c) of the actuator (3) is sealed into the second cylindrical cavity (H2) of the housing (2), and the second end (3c) of the actuator (3) is sealed into the second cylindrical cavity (H2) of the housing (2) in particular by means of seals (7, 8). The connecting channels (K1, K2) terminate at the cylindrical cavities (H1, H2) and connect the cavities (H1, H2) with the inlet (I) and the outlet (O).

5. The valve (1, 100, 1000) according to claim 4, characterized in that, At both terminal positions, the end faces (F1, F2) of the actuator (3) do not contact the inner walls (H1'', H2'') of the corresponding cavities (H1, H2), wherein, for this purpose, the first cavity (H1) and / or the second cavity (H2) each have at least one end wall (H1', H2'), especially a tapered end wall (H1', H2').

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

7. The valve (1, 100, 1000) according to any one of claims 3 to 6, characterized in that, At the first terminal position, the valve seat (4) is sealed against the outer peripheral surface (3') of the actuator (3), and at the second terminal position, the first end (3b) of the actuator (3) moves out of the valve seat (4) in the axial direction, so that the channel (3a) of the actuator (3) is connected to the connecting channel (K1).

8. The valve (1, 100, 1000) according to any one of the preceding claims, characterized in that, The actuator (3) can be adjusted by the drive device.

9. The valve (1, 100, 1000) according to claim 8, characterized in that, The actuator (3) is configured as a piston, or the piston (5) is fixedly connected to the actuator (3), and the piston (5) is disposed in the third cylindrical cavity (H3) of the housing, the third cylindrical cavity (H3) being located between the two cavities (H1, H2), the piston (5) sealingly separating the two working chambers (A1, A2), the piston (5) being able to reciprocate between its terminal positions by means of 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, At the first terminal position and the second terminal position of the actuator (3), the structure abuts against the surfaces (2a, 2b) inside the third cavity (H3), such that the surfaces (2a, 2b) define the axial adjustability of the actuator (3).

11. The valve (1, 100, 1000) according to any one of claims 4 to 10, characterized in that, The third cavity (H3) is sealed to the other two cavities (H1, H2) by means of a seal (8), which is in particular in the form of an O-ring, a pneumatic sealing flange, or a radial shaft seal.

12. The valve (1, 100, 1000) according to any one of claims 4 to 11, characterized in that, At least one sealing device (7) has a support ring (7a) and a grooved ring (7b), and in particular two sealing devices (7) have a support ring (7a) and a grooved ring (7b), wherein the actuator (3) is adjustablely disposed in the sealing device (7) or each of the sealing devices (7).

13. The valve (1, 100, 1000) according to any one of claims 4 to 12, characterized in that, At least one sealing device (7) is provided on the actuator (3), the sealing device (7) being in particular in the form of a piston seal.

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

15. The valve (1, 100, 1000) according to any one of the preceding claims, characterized in that, The valve seat (4) is made of high-performance plastic, especially polyetheretherketone / PEEK, or the valve seat (4) has components made of high-performance plastic.

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

17. The valve (1, 100, 1000) according to any one of the preceding claims, 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. The valve (1, 100, 1000) according to any one of the preceding claims, characterized in that, Additionally, at least one channel (9) is provided, which terminates in the region of the cavity (H1, H2) between the two sealing devices (7, 8), and the channel (9) is used to monitor and measure leakage.

19. The valve (1, 100, 1000) according to any one of the preceding claims, characterized in that, The spring (6) is operatively connected to the actuator (3) indirectly or directly, and when the drive device does not apply force to the actuator (3) or only applies a small force, the spring (6) holds the actuator (3) in a first end position or a second end position.

20. The valve (1, 100, 1000) according to any one of the preceding claims, characterized in that, The drive unit may additionally or alternatively include a magnet.

21. The valve (100, 1000) according to any one of the preceding claims, characterized in that, The valve (100, 1000) has two or more ports (A, B, C), wherein at least one port (A) constitutes an inlet (I) and at least one port (B, C) constitutes an outlet (O), and in particular, the valve is a two-position three-way valve or a three-position three-way valve.

22. The valve (100, 1000) according to claim 21, characterized in that, The valves (100, 1000) have two or more switching positions.

23. The valve (1000) according to any 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''), and the at least one opening (Ha, Hb, Ha', Hb', Ha'', Hb'', Ha''', Hb''') is in particular in the form of at least one hole.

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

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

26. The valve (1000) according to any one of claims 23 to 25, characterized in that, The actuator (3000''') can be adjusted 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, The sealing device (4''') has at least one channel (4''') disposed in the sealing device (4'''), wherein the channel (4''') corresponds to at least one interface (A, B, C).

28. The valve (1, 100, 1000) according to any one of the preceding claims, characterized in that, The valves (1, 100, 1000) are metering valves and / or regulating valves.

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

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

31. The valve seat (4) according to claim 29 or 30, characterized in that, The outer circumferential surface of the valve seat (4) is provided with a surrounding groove (4a), wherein the groove (4a) is used to accommodate a seal, and in particular, the groove (4a) is used to accommodate an O-ring.

32. The valve seat (4) according to any one of claims 29 to 31, characterized in that, At least one axial end face of the valve seat (4) has a recess or groove (4b), and in particular both axial end faces of the valve seat (4) have recesses or grooves (4b), the recesses or grooves (4b) being particularly circumferential recesses or grooves (4b).

33. The valve seat (4) according to claim 32, characterized in that, The recess or groove (4b) forms a sealing lip (4c).

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 circumferential protrusion (4d) on the radially inner side, and in particular, the valve seat (4) has two circumferential protrusions (4d) on the radially inner side, the protrusions (4d) forming a sealing flange.

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

36. A support ring (7a) for use in a valve (1, 100, 1000) according to any one of claims 1 to 28, the support ring (7a) having a surrounding first segment (7c) extending in an axial direction, the first segment (7c) having at least one radially inner face (7f) and at least one radially outer face (7e), wherein, The radially inner surface (7c) extends substantially parallel to the longitudinal axis of the support ring, and at least one radially outer surface (7e) extends at an angle to the longitudinal axis of the support ring (7a), the angle being greater than 0°, and particularly between 10° and 80°. The support ring (7a) is characterized by having at least one second segment (7g) extending in an axial direction, the second segment (7g) being particularly cylindrical, wherein the outer diameter of the second segment (7g) is greater than the maximum outer diameter of the first segment (7c).

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

38. The support ring (7a) according to claim 37, characterized in that, The second section (7g) has a first abutting surface (7i) for abutting the grooved 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 the wall of the housing (2) of the valve (1).

Images