Valve for automobile seat comfort system

Abstract

The invention relates to a valve (1), preferably a solenoid valve, for a seat comfort system, preferably a motor vehicle seat comfort system and in particular comprising at least one fluid actuator, and / or a seat, preferably a motor vehicle seat and equipped with such a comfort system, said valve (1) comprising a base body (2) with a linearly displaceable piston (3). The piston (3) is reversibly displaceable in the direction of the sealing seat (2d) and in the direction of the end stop (5). The piston (3) has at least one damping element (6) for reducing the impact thereof against the end stop (5) and / or against the sealing seat (2d). The piston (3) has a channel (3a) extending through the piston (3) between the two end face regions (3c, 3d) thereof. A damping element (6) is arranged in the channel (3a).

Description

Technical Field

[0001] The present invention relates to a preferably pneumatic valve, preferably a solenoid valve, for a seat comfort system and / or a seat according to the features of the preamble of claim 1 and / or the features of claim 5, wherein the seat comfort system is preferably a car seat comfort system and preferably comprises at least one fluid actuator, and the seat is preferably a car seat and is equipped with such a comfort system. Background Art

[0002] Seats used in automobiles in particular often have adjustment functions that go beyond the usual inclination and height adjustment. This makes it possible, for example, to adapt at least one seat area to the person in contact with it in accordance with ergonomic principles in order to increase their comfort. For example, a corresponding functional device can be arranged as a lumbar support in the seat backrest. In addition to other equipment features, such as seat heating, a massage system can also be integrated alternatively or additionally, preferably to allow better relaxation of the back muscles on long journeys. Actuators generate the necessary movement sequences. Their actuation can be carried out purely electrically or, preferably in order to obtain the shortest possible response time, by manipulating the fluid pressure within a fluid actuator acting in the sense of a bladder, in order to specifically change its volume. The control of the fluid actuator requires at least one valve in order to ensure rapid switching of the fluid flow.

[0003] The valves used for this purpose all include a base body in which a linearly movable piston is mounted. Depending on its variable position, the piston is used to open or close the valve. Usually, the piston can be kept in a closed position by a clamping force that is preferably mechanically generated, in which the piston is pressed against the sealing seat. In order to reach the open position, the piston can be reversibly moved in the direction of the end stop to open the valve, for example, by a preferred electromagnetic drive, overcoming the clamping force acting on it. The end stop is mainly used to limit the linear movement of the piston. Depending on the design, the path of the piston in terms of its displaceability may be affected by the possible adjustability of the end stop. Since the parts that move relative to each other are usually made of hard materials, once the moving piston is suddenly braked by hitting the end stop and / or the sealing seat, this valve will emit an operating noise, which can be described as a click. In order to reduce the impact of the piston, sometimes at least one damping element that is softer and preferably elastic than other parts is provided on the end stop or / and the sealing seat.

[0004] US 3593241A and US 8342479 B2 both disclose a solenoid valve having a damping element, which is arranged at one end of the piston facing the sealing seat and completely covers the end surface area thereof.

[0005] US2019 / 0219188 A1 also discloses a solenoid valve with damping elements, each of which is located at the end of the piston. The damping element facing the sealing seat is arranged in the associated end, while the damping element facing the end stop is arranged on the end face area of ​​the associated end. The damping elements are designed so that they protrude relative to the respective associated end face area of ​​the piston in each case to form an annular gap, which separates the piston in the closed position from the sealing seat.

[0006] Due to the quasi-shortening of the piston, which forms the annular gap by the distance between the damping element and the sealing seat, on the one hand, the magnetic field that can be generated by the electromagnetic drive is weakened, or the force of the electromagnetic drive for displacing the piston is reduced. On the other hand, the specific and different arrangement of the damping elements in the two end regions of the piston is associated with a corresponding production burden. Summary of the invention

[0007] The object of the present invention is to develop a valve which can be produced cost-effectively despite the arrangement of at least one damping element on the piston and which can maintain a strong magnetic field within the solenoid valve.

[0008] This object is achieved by a preferably pneumatic valve, in particular a solenoid valve, having the features of claim 1 and claim 5. Advantageous embodiments can be found in the dependent claims.

[0009] The invention proposes that the piston has a channel extending through the piston between its two end face regions, wherein the damping element is arranged in the channel.

[0010] The advantage resulting from this is that the piston has only one damping element, while its two end regions simultaneously have damping properties. In other words, it is no longer necessary to arrange and / or form two separate damping elements on the piston, since the cost-effective arrangement of a single damping element in the channel according to the invention is sufficient to achieve the same effect. At the same time, the damping element serves to seal the sealing seat at least in its region as soon as the piston is pressed against the sealing seat.

[0011] According to an advantageous development of the basic idea of ​​the invention, at least one end side or both end sides of the damping element can protrude relative to the piston, in particular the respectively associated end face region. In this way, when the piston moves, components that are hard in terms of their material can be prevented from colliding with each other, because the protruding part of the damping element serves to space the components apart when they approach each other. This spacing is achieved by forming, in particular, an annular gap in each case, which preferably spaces the piston apart from the sealing seat in its closed position or / and preferably spaces apart from the end stop in its open position.

[0012] Preferably, the piston is reversibly displaceable by an electromagnetic drive, preferably overcoming a clamping force, in the direction of the end stop into the open position and preferably by a clamping force in the direction of the sealing seat into the closed position.

[0013] Advantageously, at least one compensating element designed to partially bridge the annular gap can be provided so that, in the longitudinal direction of the piston, the length of the portion of the damping element protruding relative to the specifically associated end face region of the piston is smaller than the width of the specifically associated compensating element. This ensures that, when the piston moves, components that are hard in terms of their material do not collide with each other, since the protruding portion of the damping element spaces them apart from each other.

[0014] The object is also achieved by a valve, the piston of which has at least one damping element for damping the impact of the piston on the end stop and / or the sealing seat, the damping element protruding relative to the end face area of ​​the piston to form an annular gap, which annular gap separates the piston from the sealing seat in its closed position and / or from the end stop in its open position. According to the invention, an arrangement of at least one compensating element designed to partially bridge the annular gap is proposed. This means that, in the longitudinal direction of the piston, the length of the part of the damping element protruding relative to the preferably associated end face area of ​​the piston is smaller than the width of the preferably associated compensating element.

[0015] According to the invention, by arranging the compensating element for partially bridging the annular gap, a magnetic field that is as strong as possible can be maintained in the valve.

[0016] According to a preferred development of the basic inventive concept, at least a portion of the compensating element can be arranged or formed on the piston. For example, this can be achieved by arranging the compensating element on the end surface area of ​​the piston or / and by correspondingly extending a portion of the end surface area of ​​the piston.

[0017] Alternatively or additionally, at least a portion of the compensating element can be arranged or formed on a sealing seat of the valve.

[0018] Furthermore, alternatively or additionally, at least a portion of the compensating element can be arranged or formed on the end stop.

[0019] The most suitable arrangement of the compensating element may be determined by the structure of the electromagnetic drive, preferably by the position and / or the size of its coil, to which the voltage may be applied.

[0020] In principle, it can be provided, alternatively or additionally, that in each case at least a part of the compensating element is designed as a preferably separate component.

[0021] Within the scope of the invention, preferably the compensating elements can preferably all be annular. Of course, in the case of an arrangement on one of the existing components, it is also conceivable that the compensating elements can also be formed by individual and therefore spaced apart elements, for example without a common shaped connection to each other.

[0022] Advantageously, the protruding portion of the damping element can be circumferentially unsupported. This means that, when a compressive force acts on the protruding portion of the damping element, it is possible for the protruding portion to deform radially freely in order to reduce the impact noise as much as possible by its elastic radial deformation capacity. This is not the case, for example, if the protruding portion of the damping element is too short so that its possible radial deformation capacity is blocked by the opening in the piston that accommodates the damping element. Particularly preferably, the protruding portion of the damping element can be completely unsupported.

[0023] In principle, it is regarded as advantageous within the scope of the invention if the damping element is arranged or formed in the piston, wherein its protruding part is located outside the piston.

[0024] The damping element can preferably be introduced into the channel of the piston as an initially unshaped material and then preferably elastically hardens there.

[0025] The compensating element can be at least partially formed of a metallic material or contain a metallic material. Particularly preferably, the compensating element can be at least partially formed of a ferromagnetic material or contain a ferromagnetic material. In any case, the maintenance of the strong magnetic field inside the valve can be significantly improved by appropriately selecting materials or material combinations.

[0026] In principle, the compensating element can be an integral part of the piston made of the same material. For example, the compensating element can be formed on the piston by machining.

[0027] Alternatively or additionally, the compensating element can be an integral component of the sealing seat made of the same material. For example, the compensating element can be formed on the sealing seat by machining.

[0028] Furthermore, alternatively or additionally, the compensating element may be an integral part of the end stop made of the same material. For example, the compensating element may be formed on the end stop by machining.

[0029] Preferably, the clamping force acting on the piston can be generated by a spring element, preferably a helical spring.

[0030] Particularly preferably, the piston can have a channel which extends through the piston between two end face regions of the piston, and in this case the damping element is arranged in the channel.

[0031] Advantageously, the piston can have an inlet which is connected to the channel, is arranged in particular on the circumference, and through which the damping element is introduced as an initially unshaped material. For this purpose, the inlet can preferably be positioned equidistantly from the two end face regions of the piston. Particularly preferably, the material can completely fill the channel. Due to the inlet, a uniform distribution of the initially unshaped material in the channel is achieved, which greatly simplifies the production of the damping element and also simplifies its fastening in the piston.

[0032] According to a particularly preferred development, the channel of the piston can widen towards at least one end face region, preferably both end face regions, of the piston. In other words, the channel can essentially have the shape of a bone. In this way, a good connection is formed between the piston or its channel and the damping element, especially after hardening of the material. Due to the resulting thickening towards both ends of the damping element, the damping element is firmly mounted in the piston, which makes an additionally required, usually adhesive connection between the damping element and the piston superfluous.

[0033] Preferably, the initially unshaped material can be injected into the passage of the piston and hardened there. Any shrinkage during the hardening of the damping element can help the damping element to convert a large amount of energy into, in particular radial deformation when impacting the sealing seat and / or the end stop, thereby further reducing the operating noise of the valve.

[0034] In principle, at least in some areas, the material of the damping element can consist of rubber or / and silicone, for example, or contain the above materials. In any case, the material is an elastic material, on which the damping properties of the damping element are based. The geometry of the damping element can be symmetrical or asymmetrical, in particular with respect to the longitudinal direction of the piston or / and perpendicular to the longitudinal direction of the piston.

[0035] The valve according to the invention, preferably a solenoid valve, makes it possible to maintain a magnetic field that is as strong as possible in the valve despite the arrangement of at least one damping element on the piston and the resulting quasi-shortening of the piston.

[0036] Furthermore, the present invention is directed to a seat comfort system, preferably a car seat comfort system, and a seat, preferably a car seat, having such a comfort system, comprising at least one fluid actuator and at least one valve according to the invention as described in more detail above.

[0037] The resulting advantages have already been explained in more detail in conjunction with the introduction of the valve according to the invention, so that at this point reference is made to the previous explanations in this regard in order to avoid repetitions. BRIEF DESCRIPTION OF THE DRAWINGS

[0038] The invention is explained in more detail below with reference to several exemplary embodiments schematically shown in the accompanying drawings. In the drawings:

[0039] Figure 1 An exploded view of a valve according to the invention is shown in a side view,

[0040] Figure 2 Show Figure 1 A longitudinal section of a part of the valve,

[0041] Figure 3A Show Figure 1 A longitudinal section of the valve in the assembled state in the first switching position,

[0042] Figure 3B Show Figure 1 A longitudinal section of the valve in the second switching position in the assembled state,

[0043] Figure 4 The same representation is used to show the first alternative embodiment. Figure 2 Components in

[0044] Figure 5 The same representation is used to show the second alternative embodiment. Figure 2 Parts in. DETAILED DESCRIPTION

[0045] Figure 1 An exploded view of a valve 1 according to the invention is shown in a side view. The valve 1 comprises a base body 2 which, in the present case, has, by way of example only, a first opening 2a and a second opening 2b. The two openings 2a, 2b can each be connected to a fluid line, not shown in detail here. Thus, for example, a fluid pressure can be applied to the first opening 2a. In the open state of the valve 1, a fluid can flow through a portion of the base body 2 and out via the second opening 2b. In a manner not shown in detail, the second opening 2b can be connected to a fluid actuator in order to control the fluid actuator.

[0046] The valve 1 is opened and closed by a piston 3, which is shown here outside a base body 2. The valve 1 further comprises a coil 4, which is arranged around a part of the base body 2, and an end stop 5. The base body 2 can also be referred to as a coil carrier. In the assembled state, the end stop 5 is connected to the base body 2 by a C-shaped clamp 7 and is thus fixed in its position, as shown in FIG. 3 , which is described in more detail below.

[0047] As shown, the base body 2 has a cylindrical channel 2c, through which there is a fluid-conducting connection between the two openings 2a, 2b. Therefore, in the open state of the valve 1, the fluid pressure P1 applied to the first opening 2a can be transmitted and applied to the second opening 2b as a fluid pressure P2. The piston 3 can be pushed into the channel 2c until it rests on the sealing seat 2d of the base body 2. In the context of the present invention, this position of the piston 3 is referred to as its closed position S1. In order to seal the channel 2c to prevent the fluid from escaping uncontrolled, the end stop 5 has a circumferential annular seal 5a, for example in the form of a sealing rope.

[0048] When observing the piston 3, it is obvious that it is equipped with a damping element 6. The damping element 6 is at least partially made of a material that is softer than the piston 3, so as to effectively dampen the impact of the movable piston 3 on the end stop 5 and the sealing seat. As a result, the typical rattling noises of such a valve 1 during operation and caused by the movement of the piston 3 can be reduced to a minimum. The spring element 8 is arranged between the piston 3 and the end stop 5 and is designed in this case merely as an example as a helical spring, for providing a clamping force for loading the piston 3. The structure of the damping element 6 is shown in FIG. Figure 2 , and are described in more detail below.

[0049] Figure 2 A side view of a piston 3 separated from the other components of the valve 1 is shown. By way of example only, the piston has a continuous channel 3a through which a damping element 6 extends. Preferably, a damping element 6 made of a preferably elastically hardened and initially non-shaped material can be introduced into the channel 3a of the piston 3. As shown by way of example only in FIG. 3 , for this purpose, the piston 3 can have an inlet 3b which is connected to the channel 3a and through which the initially non-shaped material can be introduced until it fills the entire channel 3a. It can be seen that at both ends of the piston 3 opposite to each other in the longitudinal direction X of the piston 3, a portion 6a, 6b of the damping element 6 protrudes beyond the corresponding end surface area 3c, 3d, respectively. This ensures that the linearly movable piston 3 does not come into contact with the sealing seat 2d and the end stop 5, which would generate a rattling noise, but is always spaced from them by the corresponding protruding portions 6a, 6b of the damping element 6. The length a, ie the distance between the end face areas 3 c , 3 d of the piston 3 and the free surface of the corresponding part 6 a , 6 b of the damping element 6 , may be the same towards both ends of the piston 3 .

[0050] It can be seen that the two protruding parts 6a, 6b of the damping element are not supported on the circumference, preferably completely unsupported. This allows the corresponding parts 6a, 6b of the damping element to deform radially freely when a compressive force acts on them, so as to reduce the impact noise as much as possible through their elastic radial deformation ability.

[0051] Figure 3A Show Figure 1 2 shows a longitudinal section of the valve 1 in its assembled state and therefore in the operating state. As shown, the piston 3 is arranged linearly displaceably in the cylindrical channel 2c of the base body 2. In its closed position S1, shown here, the piston 3 is firmly pressed against the sealing seat 2c of the base body 2. As a result, the two openings 2a, 2b are separated from each other so that no fluid can flow; the valve 1 is in its closed state. The clamping force required to press the piston 3 is generated by a spring element 8, which is arranged in the recess 5b of the end stop 5 for this purpose and is therefore supported on the one hand on the bottom 5c of this recess 5b and on the other hand on the end of the piston 3 or on the damping element 6 facing the end stop 5. In this arrangement, the damping element 6 is designed to generate a clamping force acting on the piston 3. The displacement of the piston 3 is achieved by applying a voltage to the coil 4, which is part of the electromagnetic drive.

[0052] Figure 3B Show again Figure 3A Valve 1 in which the position of piston 3 changes. Figure 3A and Figure 3B As shown in FIG. 1 , the piston 3 is now displaced to the right into the open position S2. The displacement of the piston 3 is the result of the application of a voltage to the coil 4. The current flowing through the coil 4 generates a magnetic field which is strongest in the coil 4 and causes the preferably ferromagnetic piston 3 to overcome the clamping force of the spring element 8 from its closed position S1 (see FIG. 1 ). Figure 3A ) is moved into the open position S2 shown here, thereby connecting the two openings 2a, 2b to one another in a fluid-conducting manner.

[0053] Figure 4 A basic embodiment of a valve 1 according to the invention is shown by means of a representation of its longitudinal section, which is reduced to only the piston 3 and its damping element 6 and the end stop 5 and its spring element 8. In the exemplary embodiment shown here, the end stop 5 has a compensation element 9. The compensation element 9 is located at the end of the end stop 5 facing the piston 3. As shown in the figure, the compensation element 9 protrudes with its width b relative to the end of the end stop 5. The width b refers to the distance between the frontmost surface 9a of the compensation element 9 and the surface area 5d of the end stop 5 that protrudes the farthest in the direction of the piston 3. In the present case, the surface area 5d is in the form of a projection around the entrance of the recess 5b of the end stop 5, in which the spring element 8 is arranged.

[0054] The advantage of the compensation element 9 is that it at least partially bridges the annular gap 10 generated between the end surface area 3d of the piston 3 and the end stop 5. In this case, in the open position S2, due to the protruding portion 6b of the damping element 6, the piston 3 is inevitably spaced apart from the surface area 5d of the end stop 5 without contact, so that the annular gap 10 is generated.

[0055] Figure 5 An alternative embodiment of the compensating element 9 is shown. Figure 4 As shown, for the sake of clarity, the valve 1 is also shown here in a longitudinal section, which is reduced to only the piston 3 and its damping element 6 as well as the end stop 5 and the spring element 8. It can be seen that the compensation element 9 is now arranged on the piston 3, preferably on its end face area 3d. The width b of the compensation element 9 refers to the distance between the frontmost surface 9a of the compensation element 9 and the surface area 3e of the piston 3 that protrudes the farthest in the direction of the end stop 5. In the present case, purely by way of example, the surface area 3e is identical to the end face area 3d of the piston 3.

[0056] With respect to the longitudinal direction X of the piston 3, the specific length a of the parts 6a, 6b of the damping element 6 protruding relative to the respective end face area 3c, 3d of the piston 3 is in all embodiments smaller than the width b of the respective, preferably associated compensation element 9. This ensures that the piston 3 always contacts the end stop 5 and the sealing seat 2d via its damping element 6 and that no relatively hard materials thus collide with each other. Due to the compensation element 9, a magnetic field that is as strong as possible can be maintained in the valve 1 despite the protruding damping element 6.

[0057] It is also conceivable that the compensation element 9 is arranged in a manner not shown in detail on the end of the piston 3 facing the sealing seat 2d or on the sealing seat 2d itself. The compensation element 9 can also be at least partially a separate component. Of course, the above combinations are also possible.

[0058] Preferably, the specific compensating element 9 can be annular in order to reduce the annular gap 10 as uniformly as possible and without any interruptions.

[0059] Advantageously, the compensating element 9 can be formed at least partially from or comprise a metallic and / or magnetic and / or ferromagnetic material.

[0060] Particularly preferably, Figure 4 and Figure 5 As shown, the compensating element 9 can be an integral part of the piston 3 or / and the end stop 5 made of the same material. Alternatively or additionally, the compensating element 9 can of course also be an integral part of the sealing seat 2d made of the same material (not shown in detail here).

[0061] List of reference numerals:

[0062] 1 - Valve

[0063] 2-1 matrix

[0064] 2a - First opening of 2

[0065] 2b - Second opening of 2

[0066] 2c - Channels in 2

[0067] 2d-2 seal seat

[0068] 3-1 Piston

[0069] 3a - Channel 3

[0070] 3b-3 entrance

[0071] 3c - 3 end face area

[0072] 3d - 3 end area

[0073] Surface area of ​​3e - 3

[0074] 4-1 Coil

[0075] 5-1 End Stops

[0076] 5a-5 annular seal

[0077] 5b – The recess in 5

[0078] 5c - Bottom of 5b

[0079] 5e - 5 surface area

[0080] 6-1 Damping element

[0081] 6a - The protrusion of 6

[0082] 6b - The protruding part of 6

[0083] 7-1 Fixture

[0084] 8-1 Spring element

[0085] 9-1 Compensation Components

[0086] 9a - 9 surface

[0087] 10 - 1 annular gap

[0088] a - length of 6a and / or 6b

[0089] b - width of 9

[0090] P1 - Fluid Pressure

[0091] P2 - Fluid Pressure

[0092] S1 - 3 closed position

[0093] S2 - 3 open position

[0094] X-3 vertical

Claims

1. A valve (1) for a seat comfort system or / and a seat, preferably a solenoid valve, the seat comfort system is preferably a car seat comfort system and in particular comprises at least one fluid actuator, the seat is preferably a car seat and is equipped with such a comfort system, the valve (1) comprising a base body (2) having a linearly movable piston (3), the piston (3) being reversibly displaceable in the direction of a sealing seat (2d) and in the direction of an end stop (5), wherein the piston (3) has at least one damping element (6) for reducing the impact of the piston (3) on the end stop (5) and / or the sealing seat (2d), Features The piston (3) has a channel (3a) extending through it between its two end face areas (3c, 3d), wherein the damping element (6) is arranged in the channel (3a).

2. The valve (1) according to claim 1, Features At least one end side portion (6a, 6b) or both end side portions (6a, 6b) of the damping element (6) protrudes relative to the preferably respectively associated end surface area (3c, 3d) of the piston (3) to preferably form an annular gap (10), which preferably spaces the piston (3) from the sealing seat (2d) in the closed position (S1) of the piston (3) or / and preferably spaces the piston (3) from the end stop (5) in the open position (S2) of the piston (3).

3. The valve (1) according to claim 1 or 2, Features The piston (3) can be reversibly displaced in the direction of the end stop (5) to reach an open position (S2) by a preferably electromagnetic drive, overcoming a clamping force, and can preferably be reversibly displaced in the direction of the sealing seat (2d) by the clamping force to reach a closed position (S1).

4. The valve (1) according to claim 2 or 3, Features At least one compensating element (9) is designed to partially bridge the annular gap (10) so that, with respect to the longitudinal direction (X) of the piston (3), the length (a) of the portion (6a, 6b) of the damping element (6) protruding relative to a specifically associated end surface area (3c, 3d) of the piston (3) is smaller than the width (b) of the specifically associated compensating element (9).

5. A valve for a seat comfort system or / and a seat, preferably a solenoid valve (1), wherein the seat comfort system is preferably a car seat comfort system and preferably comprises at least one fluid actuator, wherein the seat is preferably a car seat and is equipped with such a comfort system, wherein the valve (1) comprises a base body (2) having a linearly movable piston (3), wherein the piston (3) can be reversibly displaced to a closed position (S1) by a clamping force, the piston (3) being pressed against a sealing seat (2d), and in order to reach an open position (S2), the clamping force can be overcome by an electromagnetic drive at an end stop The piston (3) is reversibly displaceable in the direction of the end stop (5), wherein the piston (3) has at least one damping element (6) for reducing the impact of the piston (3) on the end stop (5) and / or the sealing seat (2d), the damping element protruding relative to the end surface area (3c, 3d) of the piston (3) to form an annular gap (10), the annular gap (10) separating the piston (3) in its closed position (S1) from the sealing seat (2d) and / or separating the piston (3) in its open position (S2) from the end stop (5), Features At least one compensating element (9) is designed to partially bridge the annular gap (10) so that, with respect to the longitudinal direction (X) of the piston (3), the length (a) of the part (6a, 6b) of the damping element (6) protruding relative to the preferably associated end surface area (3c, 3d) of the piston (3) is smaller than the width (b) of the preferably associated compensating element (9).

6. Valve (1) according to claim 4 or 5, Features At least a part of the compensating element (9) is arranged or formed on the piston (3), or / and - on the sealing seat (2d) or / and - on said end stop (5).

7. Valve (1) according to claim 5 or 6, Features The damping element (6) is arranged or formed inside the piston (3), wherein the protruding parts (6a, 6b) of the damping element (6) are located outside the piston (3).

8. Valve (1) according to any one of the preceding claims, Features The damping element (6), which is made of a preferably elastically hardened and initially shapeless material, is introduced into the channel (3a) of the piston (3).

9. The valve (1) according to any one of claims 4 to 8, Features The compensation element (9) - at least partially formed of or containing metal and / or magnetic and / or ferromagnetic materials, or / and - is an integral part of the piston (3) made of the same material, or / and - is an integral part of the sealing seat (2d) made of the same material, or / and - is an integral part of said end stop (5) made of the same material.

10. The valve (1) according to any one of claims 3 to 9, Features The clamping force acting on the piston (3) is generated by a spring element, preferably a helical spring.

11. The valve (1) according to any one of claims 5 to 10, Features The piston (3) - has a channel (3a) extending through it between its two end face regions (3c, 3d), wherein the damping element (6) is arranged in the channel (3a), or There is an inlet (3b) connected to the channel (3a), in particular arranged circumferentially, and through which the damping element (6) is introduced as an initially unformed material, preferably completely filling the channel (3a).

12. Valve (1) according to any one of claims 1 to 4 or 8 to 11, Features The channel (3a) widens towards at least one, preferably both, end face regions (3c, 3d) of the piston (3).

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