Pressure control valve for controlling or regulating the pressure of a fluid in a pilot pressure chamber, and vibration damper having such a pressure control valve

Abstract

The invention relates to a pressure control valve (1) for controlling or regulating the pressure of a fluid in a pilot pressure chamber, having a valve housing (10) with at least one inlet, which can be fluidically connected to the pilot pressure chamber, and at least one outlet (O), wherein between the at least one inlet (I) and the at least one outlet (O) is a main valve chamber (25) and a pilot valve chamber (65), and having an electromagnetic actuation device (70), by means of which a pilot valve (60) located in the pilot valve chamber (65) can be opened and / or closed, wherein the main valve chamber (25) is equipped with a main valve (20) comprising a main valve seat (50) and a main valve slide (30) which can be moved in a longitudinal axis (L) and which comprises a slide (32), and the main valve slide (30) is pretensioned, by means of a main valve spring (26), into a closed position, in which the main valve slide (30) sealingly interacts with the main valve seat (50). The main valve slide (30) comprises the slide (32) and at least one seal element (41, 42) which is supported on the slide (32) in a spring-loaded manner, and the at least one seal element (41, 42) can sealingly interact with the main valve seat (50). The invention additionally relates to a vibration damper having a pressure control valve (1).

Description

[0001] BIN337 1Pressure control valve for controlling or regulating a pressure of a fluid in a pilot pressure chamber and vibration damper with such a pressure control valve The present invention relates to a pressure control valve for controlling or regulating a pressure of a fluid in a pilot pressure chamber with the features of patent claim 1. Furthermore, the present invention relates to a vibration damper with such a pressure control valve with the features of patent claim 17. Pressure control valves are already known from the prior art in various designs. For example, in the prior art, generic pressure control valves are used in vibration dampers in motor vehicles, wherein a damping characteristic of the pressure control valve depends on a volume flow of the fluid used flowing through the proportional valve. Depending on the volume flow, a more comfortable, softer damping or a more sporty, harder damping can be set.Vibration dampers use an energized actuation device with which several damping characteristics can be specified by the driver or automatically adjusted by an on-board computer depending on the driving condition of the vehicle or the condition of the road surface along which the vehicle is currently moving. The fluid can be hydraulic or pneumatic, with hydraulic fluid or compressed air typically being used. Pilot pressure chambers in hydraulically or pneumatically operated devices serve to control or regulate pilot-operated valves, often also designed as hydraulic or pneumatic spools. When pilot-operated valves. BIN337 2If the valves are designed as proportional valves or proportional slides, the volume flows flowing through the proportional valve or the proportional slide can be continuously adjusted within certain limits using the pressure in the pilot pressure chamber. The respective pressure control valve should have a defined characteristic curve that indicates the volume flow flowing through when there is an excess pressure in the pilot chamber. These requirements result in a relatively complex design of the device, in particular of the vibration damper, as can be seen, for example, in US 20160 091 044 A1 and WO 2016 066 314 A1. The design is complex primarily because multiple slides must be used. Further vibration dampers are disclosed in US 2016 0 369 862 A1, JP 2009115 319 A, US 5147 018 A, WO 2011023 351 A1 and US 20050 016 086 A1.Such pressure control valves have proven themselves in the past, but they exhibit undesirable behavior, particularly at very low overpressures, in that the volume flow initially increases only slightly or initially does not increase at all as the overpressure increases. This behavior is referred to as "zero point carryover." A further disadvantage of the pressure control valves known from the prior art is that in the lower characteristic curve range, i.e. at lower overpressures, the characteristics vary greatly due to component tolerances, which can cause the damping behavior to vary considerably. In addition, there are only limited options for adapting the characteristics to specific applications. This is where the present invention comes in. BIN337 3The present invention is dedicated to the task of proposing a generic pressure control valve that expediently eliminates the disadvantages known from the prior art. The proposed pressure control valve should be simple in design and make it possible to shape the flow through the pressure control valve in the lower characteristic curve range. This task is solved by a pressure control valve with the features of patent claim 1 and a vibration damper with the features of patent claim 17. Further advantageous embodiments of the present invention are specified in the subclaims. The fail-safe pressure control valve according to the invention with the features of patent claim 1 for controlling or regulating a pressure of a fluid in a pilot pressure chamber comprises a valve housing with at least one inlet that is fluidically connectable to the pilot pressure chamber.In addition, the valve housing has a pilot valve chamber with a pilot valve arranged between the at least one inlet and the at least one outlet, and a main valve chamber with a main valve. The pressure control valve also comprises an electromagnetic actuating device by which the pilot valve arranged in the pilot valve chamber can be opened and / or closed. Furthermore, a main valve seat and a main valve slide with a slide that is movable along the longitudinal axis are provided in the main valve chamber. The main valve slide is actuated by. BIN337 4a main valve spring is held resiliently in a closed position, wherein the main valve spool interacts sealingly with the main valve seat in the closed position. Preferably, the main valve spool comprises the spool and at least one sealing element which is spring-supported on the spool and wherein the at least one sealing element interacts sealingly with the main valve seat. The at least one sealing element can, for example, be a disc-shaped element which can be manufactured cost-effectively and can be easily replaced to adapt the characteristic curve of the pressure control valve. The present invention is based on the idea that the main valve spool is designed in several parts, wherein the at least one sealing element is spring-supported relative to the spool, thus realizing a series connection of the main valve spring and the springing of the sealing element.The spring rate with which the spring element is held spring-loaded relative to the slide can be set such that, initially at low pressure, the first sealing element slightly opens the main valve seat before, at higher pressures, the slide itself moves against the force of the main valve spring. In other words, the spring rate with which the at least one sealing element is held spring-loaded relative to the slide can preferably be smaller than a spring rate of the main valve spring. As a result, a volume flow can flow through the pressure control valve, particularly in the first characteristic curve range, even at a slight overpressure, without what is known as carryover at the zero point. BIN337 5According to the invention, it is preferred that a sealing element spring supports the at least one sealing element relative to the slide, and that the spring rate of the main valve spring is greater than the spring rate of the sealing element spring. The sealing element spring is preferably arranged in the longitudinal axis between the slide and the at least one sealing element and enables the at least one sealing element to undergo a displacement relative to the slide in the longitudinal axis. The sealing element spring can be a cost-effective and simple component, wherein the spring rate of the sealing element can be precisely adjusted. The simple components, such as the at least one sealing element or the sealing element spring, can be selected for specific applications, thereby making it easy to adapt the proposed pressure control valve to different applications with different characteristic curve requirements.A further development of the present invention provides for a stroke limiter to limit displacement of the at least one sealing element in the longitudinal axis relative to the slide. The stroke limiter can be formed, for example, by a spacer ring or at least one correspondingly shaped stop. When the pressure increases, the at least one sealing element can initially be lifted from the main valve seat against the spring force of the sealing element spring. At higher pressures, the slide is lifted together with the at least one sealing element. According to a preferred development of the present invention, the main valve seat has a first sealing collar and a second sealing collar. BIN337 6Furthermore, it has also proven advantageous if the first sealing collar and the second sealing collar are arranged around the longitudinal axis and if the first sealing collar and the second sealing collar are arranged radially spaced from one another. The two sealing collars are therefore arranged concentrically and have different diameters. It can also be advantageous if the first sealing collar and the second sealing collar are arranged spaced from one another along the longitudinal axis. The first sealing collar and the second sealing collar are arranged at a first distance along the longitudinal axis. A further development of the present invention provides that two sealing elements are arranged, wherein the first sealing element and the second sealing element are arranged on the slide. At least one of the two sealing elements is spring-supported on the slide and cooperates in a sealing manner with the main valve seat.The other of the two sealing elements can also be spring-supported on the slide or fixedly arranged on the slide and also interacts sealingly with the main valve seat. Preferably, the first sealing element interacts with the first sealing collar and the second sealing element interacts with the second sealing collar. The two sealing collars and the two sealing elements can thus create a multi-stage seal on the slide. The first sealing element and the second sealing element are arranged at a second distance along the longitudinal axis. According to one embodiment, the second distance can be adjusted by a spacer ring between the first sealing element and the second sealing element. BIN337 7Preferably, the first distance and the second distance are approximately equal. However, a preferred development can provide that the second distance is smaller than the first distance, whereby one of the two sealing elements is slightly raised from the main valve seat in the closed state. According to a development of the present invention, it is advantageous if the second sealing element is fixedly arranged on the slide. The second sealing element can, for example, be positively connected to the slide. The second sealing element can therefore form a stop disk which comes into contact with the main valve seat and predetermines the position of the slide in which the main valve element is arranged in the closed position. Alternatively, the second sealing element can be arranged so as to be movable relative to the slide and can be kept at a distance from the first sealing element in the longitudinal axis, for example by means of the spacer ring.In this alternative embodiment, the first sealing element and the second sealing element are held apart along the longitudinal axis, in particular by a spacer disk, and can be moved together along the longitudinal axis relative to the slide valve. In other words, the two sealing elements form a package, with one of the two sealing elements preferably having a bypass through which fluid can flow even when closed. As the pressure increases, the entire package can initially move in a spring-loaded manner relative to the slide valve, thus slightly opening the main valve seat. At higher pressures, the slide valve moves together with the package, allowing larger volume flows to pass through. BIN337 8Furthermore, it has proven advantageous if the main slide has a pin that projects from the slide in the longitudinal axis. The first sealing element and / or the second sealing element can be arranged on or on the pin. In particular, it is preferred if the first sealing element and / or the second sealing element are arranged displaceably on the pin, wherein a running gap is formed between the pin and the first sealing element and / or the second sealing element, in particular by a clearance fit. A passage is preferably formed in the pin, through which the fluid can flow from the at least one inlet to the pilot chamber through the main valve chamber. It can also be advantageous if a rivet and / or a plug is inserted into the pin, wherein the rivet and / or the plug can form the passage.The rivet can additionally be used to fix the second sealing element to the slide and / or to form a loss protection for the first sealing element and / or the second sealing element. The slide can typically have a passage through which the fluid can flow from the at least one inlet to the pilot valve chamber. The aforementioned pin, the rivet and / or the plug can form the passage. Furthermore, it has proven advantageous if the first sealing element and / or the second sealing element and / or the first sealing collar and / or the second sealing collar form or form at least one bypass channel through which the fluid can flow when the first sealing element rests against the first sealing collar and / or the second sealing element rests against the second sealing collar. A bypass can already cause a very small pressure difference or overpressure. BIN337 9Volume flow. As the pressure increases, the resistance in the bypass channel increases and the at least one sealing element is raised in a spring-loaded manner relative to the slide. The bypass channel can in particular prevent any drift of the characteristic curve at the zero point. A preferred development of the present invention provides that the sealing element spring comprises a disc spring or a finger spring. Such spring elements can be manufactured cost-effectively and a defined spring rate can be set precisely in a simple manner. The spring element can also comprise the aforementioned stroke limiter. For example, the spring element can have angled regions by means of which a stop for limiting the stroke of the at least one spring element can be formed. The sealing element spring can also comprise the second sealing element.The sealing element spring can, for example, comprise one or more mutually adjacent annular sections, wherein one section forms the second sealing element and another section forms the sealing element spring, via which the first sealing element is held spring-loaded relative to the second sealing element and the slide. Furthermore, a preferred development of the present invention can provide that the valve housing comprises a main housing part and a wall section, wherein the wall section has the main valve seat. The main housing part. BIN337 10can have a corresponding recess into which the wall section with the main valve seat can be inserted into the main housing part. The main housing part and the wall section can jointly enclose the main valve chamber, with corresponding openings being provided in the wall section to the at least one inlet and in the main housing part to the at least one outlet. Furthermore, it has proven advantageous if at least one adjusting means is provided by means of which the position of the main valve seat relative to the main housing part can be adjusted in the longitudinal axis. In the simplest case, the adjusting means can grip a spacer ring which is inserted into the recess in order to specify a distance between the main housing part and the wall section.According to a further development of the present invention, the pilot valve chamber is fluidly connected to the main valve chamber and to the at least one inlet via a first passage channel and to the at least one outlet via a second passage channel. The pilot valve in the pilot valve chamber can have at least one pilot valve seat, against which a pilot valve seal actuated by the electromagnetic actuating device can bear in a sealing manner. According to a further development, a plunger and a pilot seal can be provided, wherein the plunger is movable along a longitudinal axis between a first and a second position by means of an energizable actuating device. The pilot seal is preferably arranged on the plunger, and the energizable actuating device can move the plunger along the longitudinal axis from the first position to the second position against the force of a return spring. BIN337 11In an unactuated state of the actuating device, the pilot seal is preferably arranged in the first position by means of a return spring. In the first position, the pilot seal can seal against a first pilot valve seat and can close the first passage. In the actuated state of the actuating device, the tappet is in the second position, in which the pilot seal seals against the second pilot valve seat and closes the second passage. By appropriately controlling the pilot valve seat, the pressure control valve can be controlled, whereby the damping characteristics can be specifically changed. A further development of the present invention provides that the main spool is designed as a proportional spool. Furthermore, it has proven advantageous if the actuating device is pressure-balanced.In particular, it is preferred if the actuating device comprises a pressure compensation chamber that can communicate with the pilot valve chamber. For this purpose, it is advantageous if the tappet has a compensation bore through which fluid can flow along the longitudinal axis of the tappet. A further aspect of the present invention relates to a vibration damper with a pressure control valve as described above. BIN337 12Three exemplary embodiments of a pressure control valve according to the invention and two further developments of an embodiment are described in detail below with reference to the accompanying drawings.They show: Figure 1 is a partially sectioned view of a pressure control valve for controlling or regulating a pressure of a fluid in a pilot pressure chamber with a pilot valve that can be actuated by an electromagnetic actuating unit and a main valve, wherein the main valve comprises a main valve spring, a main valve seat and a main valve spool with a spool, a first sealing element and a second sealing element, Figure 2 is an enlarged detailed view of the pressure control valve according to Figure 1, Figure 3 is a detailed view of a sealing element spring, by means of which the first sealing element is held in a spring-loaded manner relative to the spool of the main valve spool, Figure 4 is a side view of the sealing element spring according to Figure 3, Figure 5 is a detailed view of the second sealing element of the main valve spool according to Figure 1 or 2, Figure 6 is a side view of the sealing element according to Figure 5. BIN337 13Figure 7 is an enlarged, partial view of the pressure control valve according to a first embodiment of the sealing element spring. Figure 8 is an enlarged, partial view of the sealing element spring according to Figure 7. Figure 9 is a side view of the sealing element spring according to Figure 8. Figure 10 is an enlarged, partial view of the pressure control valve according to a second embodiment of the sealing element spring. Figure 11 is an enlarged, partial view of the sealing element spring according to Figure 10. Figure 12 is a side view of the sealing element spring according to Figure 11. Figure 13 is an enlarged, detailed view of the pressure control valve according to a second embodiment. Figure 14 is an enlarged, detailed view of the sealing element spring according to Figure 9. Figure 15 is an enlarged, detailed view of the pressure control valve according to a third embodiment. Figure 16 is an enlarged, detailed view of the sealing element spring according to Figure 15. BIN337 14Figure 17 is an enlarged view of the first sealing element according to Figure 15, Figure 18 is an enlarged detailed view of the pressure control valve according to a fourth exemplary embodiment, Figure 19 is an enlarged view of the second sealing element with the sealing element spring according to Figure 18, and Figure 20 is a side view of the second sealing element according to Figure 19. Identical or functionally identical parts or features are identified by the same reference numerals in the following detailed description of the figures. Likewise, not all identical or functionally identical parts or features are provided with a reference numeral in the figures. First, a first exemplary embodiment is described in detail below with reference to Figures 1-5. The other exemplary embodiments are then described in brief, with only the differences from the previous exemplary embodiments being discussed.At this point, it should be noted that the features of the exemplary embodiments and also of the further developments can be combined with one another. Figure 1 shows a first exemplary embodiment of a fail-safe pressure control valve 1 for controlling or regulating the pressure of a fluid. The pressure control valve 1 can be used, for example, in a vibration damper (not shown), in particular of a motor vehicle, to adjust a damping characteristic of the vibration damper. BIN337 15Figure 1 shows a first exemplary embodiment of a fail-safe pressure control valve 1 for controlling or regulating the pressure of a fluid. The pressure control valve 1 can be used, for example, in a vibration damper (not shown), in particular of a motor vehicle, to adjust a damping characteristic of the vibration damper. The pressure control valve 1 comprises a valve housing 10 with at least one inlet I and at least one outlet O. The pressure control valve 1 comprises a main valve 20 and a controllable pilot valve 60, wherein the main valve 20 is arranged in a main valve chamber 25 and the pilot valve 60 in a pilot valve chamber 65. The at least one inlet I can be connected to a pilot pressure chamber. In the accompanying figures, the reference symbols "I" and "O" indicate the regions in which the at least one inlet I and the at least one outlet O could be located.The valve housing 10 at least partially encloses the main valve chamber 25 and the pilot valve chamber 65. The pilot valve 60 comprises a first pilot valve seat 63 and can furthermore comprise a second pilot valve seat 64. The pilot valve chamber 65 is connected to the at least one inlet I via a first passage 61 and the main valve chamber 25. Furthermore, the pilot valve chamber 65 is connected to the at least one outlet O by means of a second passage 62, whereby the fluid flows through the at least one inlet I. BIN337 16an inlet I, the main valve chamber 25 and the first passage 61 into the pilot valve chamber 65 and can flow through the second passage 62 to the at least one outlet O. In addition, the pressure control valve 1 has an energizable actuating device 70, wherein the one energizable actuating device 70 can preferably be formed by an electromagnetic actuator hidden in Figure 1. The actuating device 70 can be accommodated in an actuator housing 72, wherein the actuating device 70 further comprises an excitation coil, an armature and a return spring. The armature can be moved along a longitudinal axis L when the excitation coil is energized against a spring force of the return spring in a known manner. The actuator housing 72 has a receiving area formed by a recess, into which the valve housing 10 can be at least partially inserted.The valve housing 10 can be fixedly arranged in the receiving area of ​​the actuator housing 72, for example by a positive, non-positive and / or materially bonded connection, in particular by being pressed into the receiving area. Furthermore, the pressure control valve 1 has a plunger 75, wherein the plunger 75 can be moved by the actuating device 70 along the longitudinal axis L against a force of a return spring (not shown). For this purpose, the plunger 75 is preferably connected to the armature and can furthermore - as shown in Figure 1 - be held movably mounted on the actuator housing 72 along the longitudinal axis L by means of bearing elements 74. BIN337 17The plunger 75 protrudes from the actuator housing 72 into the valve housing 10. As can be seen, for example, from the detailed illustration in Figure 2, a first free end of the plunger 75 protrudes into the pilot valve chamber 65. Furthermore, it can be seen from the accompanying figures that the plunger 75 has a pressure equalization bore through which the plunger 75 can flow along the longitudinal axis L. Consequently, the fluid can flow from the first free end through the plunger 75 into a pressure equalization chamber (not shown) opposite the armature, whereby pressure equalization can occur and the pressure control valve 1 can be designed to be pressure-balanced. The plunger 75 further has a pilot valve seal 66, which is arranged on the plunger 75, preferably adjacent to the free end. The pilot valve seal 66 may, for example, be secured to the tappet 75 by means of a retaining ring, as shown in the accompanying figures.The pilot valve seal 66, according to the embodiments shown in Figures 1 to 5, comprises a disk element, which is preferably designed in the manner of a disk-shaped flat spring element. In the accompanying figures, the electromagnetic actuating device is not energized and is in a first position. If, as shown in the accompanying figures, the pilot valve 60 has a second pilot valve seat 64, the pilot valve seal 66 rests sealingly against the second pilot valve seat 64 in the first position. BIN337 18In an actuated state (not shown) of the actuating device 70, the excitation coil of the actuating device 70 is energized and the pilot valve seal 66 is moved towards the first pilot valve seat 63. In this position, the pilot valve seal 66 lies sealingly against the first pilot valve seat 63 and closes the first passage 61. In this position, the fluid cannot flow from the at least one inlet into the pilot valve chamber 65. Furthermore, it can be seen from the accompanying figures that the valve housing 10 comprises a main housing part 12 and a wall section 14, wherein the main housing part 12 and the wall section 14 enclose the main valve chamber 54. The wall section 14 can be inserted into a receptacle of the wall section 14 in the manner of a plug.On the side facing the main valve chamber 25, the wall section 14 has the main valve seat 50, designated as a whole, which is formed around a housing inlet opening. In order to determine the position of the main valve seat 50 along the longitudinal axis L with respect to the valve housing 10, or more precisely, the main housing part 12, an adjusting means 16, e.g. a spacer ring, can be arranged in the receptacle between the wall section 14 and the main housing part 12. With reference to Figures 2, 7, 10, 13, 15 and 18, it can be seen that the main valve seat 50 has a first sealing collar 51 and a second sealing collar 52, which protrude into the main valve chamber 25 along the longitudinal axis L. BIN337 19The first sealing collar 51 and the second sealing collar 52 are arranged concentrically around the longitudinal axis L and have different diameters. Furthermore, the first sealing collar 51 and the second sealing collar 52 are arranged at a first distance from one another along the longitudinal axis L. The main valve chamber 25 is fluidically connected on the one hand to the at least one inlet I and on the other hand to the at least one outlet O. A main valve spool 30, referred to as a whole, a main valve spring 26 and a main valve seat 50 are arranged in the main valve chamber 25. The main valve spool 30 is movable along the longitudinal axis L in the main valve chamber 25 and is preloaded by the main valve spring 26 into a closed position shown in the figures, in which the main valve spool 30 cooperates sealingly with the main valve seat 50. The main valve spring 26 has a spring rate K1.The main valve chamber 25 is fluidically arranged between the at least one inlet and the pilot valve chamber 65. This means that the fluid from the at least one inlet must first flow through the main valve chamber 25 before it can enter the pilot valve chamber 65 through the first passage 61. For this purpose, the main valve spool 30 has a passage 58, which is shown, for example, in Figures 2, 7, 10, 15, and 18. According to the first embodiment, the main valve spool 30 comprises Figures 1-6 and the further developments. BIN337 20according to Figures 7-12, a slide 32, a first sealing element 41, a second sealing element 42, and a sealing element spring 40. The slide 32 is essentially cup-shaped and can also be referred to as the main valve slide body. Depending on the position of the slide 32 in the longitudinal axis L, outlet openings 15 in the valve housing 10 can be more or less open or completely or only partially closed. The slide accommodates the main valve spring 26 in its interior. On the side of the slide 32 facing the inlet I, a pin 34 is arranged, which projects from an end wall of the slide 32. The passage 58 can be formed in the pin 34. The sealing element spring 40, shown by way of example in Figures 3 and 4, can be an essentially disk-shaped element and can have a plurality of spring fingers, preferably arranged symmetrically around the circumference.The spring fingers protrude from an area designated as the contact section 43 and form a spring section 44. The contact section 43 is essentially ring-shaped with a central opening. At the free end of the spring fingers is the so-called support section 45, wherein the support section 45 can be displaced relative to the contact section 43 along the longitudinal axis L, counter to the spring force of the spring section 44. The sealing element spring 40 has a spring rate K2. BIN337 21The first sealing element 41 can also be referred to as a sealing disk and is preferably a circular disk with a central opening. The second sealing element 42 is shown in detail in Figures 5 and 6 and can also be referred to as a stop disk. The second sealing element 42 is a circular disk and has a central opening. The second sealing element 42 has a plurality of recesses around its circumference, forming a bypass channel 46 through which the fluid can flow through the second sealing element 42. The sealing element spring 40 is arranged along the longitudinal axis L between the slide 32 and the first sealing element 41. The first sealing element 41 is spring-loaded on the slide 32 by means of the sealing element spring 40 and can bear sealingly against the main valve seat 50, in particular against the first sealing collar 51 of the main valve seat 50.For this purpose, the first sealing element 41 and the sealing element spring 40 are placed on the slide 32 via the pin 34, with the sealing element spring 40 being arranged between the end face of the slide and the first sealing element 41. Furthermore, a spacer ring 47 for stroke limitation 48 can be arranged between the first sealing element 41 and the sealing element spring 40, which spacer ring specifies a minimum distance between the contact section 43 and the first sealing element 41. The spacer ring is arranged within the spring fingers. The opening in the sealing element spring 40 and / or the opening in the first sealing element 41 are / is designed to form a running gap between the pin 34 and themselves, preferably with a clearance fit. BIN337 22The second sealing element 42 is arranged on the side of the first sealing element 41 facing away from the sealing element spring 40, at a distance from the first sealing element 41. The second sealing element 42 is fixedly connected to the slide 32 and is sealingly applied to the main valve seat 50, in particular to the second sealing collar 52 of the main valve seat 50, by the main valve spring 26. It can be seen from Figures 2, 7 and 10 that the bypass channels 46 are arranged such that they project beyond the second valve collar 52, which is why fluid can flow through the second sealing element 42 when the second sealing element 42 bears against the second sealing collar 52 of the main valve seat 50. The second sealing element 42 can be attached to the pin 34 in any desired manner, for example by form-fitting, force-fitting and / or material-fitting. In the illustrated embodiment, the second sealing element 42 is held by a rivet 35 inserted into the pin 34.The rivet 35 can, as shown, also form the passage 58. When the pressure in the (not shown) pilot pressure chamber increases, a pressure force initially acts through the bypass channel(s) 46 on the first sealing element 41 and lifts it against the restoring force of the weak sealing element spring 40 until the first sealing element 41 comes to a stop against the stroke limiter 48. If the pressure increases further, the main valve spool 30 is raised. Due to the weak sealing element spring 40, the main valve 20 opens even at low pressures, whereby a defined characteristic curve can be realized without carryover at the zero point even at low pressures. BIN337 23The further developments shown in Figures 7-9 and 10-12 differ from the previously described embodiment in the design of the sealing element spring 40. The first further development according to Figures 7-9 provides that the stroke limiter 48 is formed by the sealing element spring 40. For this purpose, a plurality of stops are provided around the circumference, which stops are preferably arranged between the spring arms around the circumference. The stroke limiter 48 can be introduced into the essentially disc-shaped element, for example, by punching, which results in particularly simple production and eliminates the need for an additional spacer ring to take over the function of the limiter 48. The second further development of the first embodiment according to Figures 10-12 also provides that the stroke limiter 48 is formed by the sealing element spring 40.For this purpose, a plurality of tabs protrude into the opening in the sealing element spring 40, which tabs are angled in order to each form a shoulder forming the stroke limiter 48. According to this second development, the stroke limiter 48 can also be introduced into the essentially disc-shaped element by punching and bending, which results in particularly simple production and no additional spacer ring has to be provided which takes over the function of the stroke limiter 48. Figures 13 and 14 show a second embodiment of the pressure regulating valve 1, wherein the pressure regulating valve 1 differs from the first embodiment in that the second sealing element 42 is not... BIN337 24a rivet, but rather by caulking on the pin 34, in particular at the free end of the pin 34. Furthermore, this exemplary embodiment differs in the design of the stroke limiter 48 of the first sealing element 41 and in the design of the sealing element spring 40. It should be noted that the differences listed above are not exhaustive. According to the second exemplary embodiment according to Figures 13 and 14, the main valve spool 30 comprises a spool 32 and, in sequence along the longitudinal axis L, a sealing element spring 40, a first spacer ring 47, a first sealing element 41, and a second sealing element 42. Furthermore, the main valve spool 30 can have a second spacer ring 47', which is arranged between the first sealing element 41 and the second sealing element 42.In this exemplary embodiment, as can be seen from Figure 14, the sealing element spring 40 is designed as a flat disc spring and has an annular contact section 43 and an annular support section 45. Between the annular contact section 43 and an annular support section 45, two spring sections 44 are formed which connect the contact section 43 and the support section 45 and enable an elastic displacement of the support section 45 relative to the contact section 43. The contact section 43 is arranged radially outside the support section 45 and the opening is inside the support section 45. The first sealing element 41 is held at a distance from the sealing element spring 40 by means of a spacer ring 47, or more precisely. BIN337 25expressed by means of the spacer ring 47, it is held at a distance from the support section 45 of the sealing element spring 40. The spacer ring 47 specifies the maximum displacement, i.e. the stroke limit 48 of the first sealing element 41, before it comes to bear against the sealing element spring 40. On the end face of the slide 32, as shown in Figure 13, a projection 49 is formed on the end face, by means of which the sealing element spring 41 is arranged at a distance from the end face of the slide 32. The projection 49 enables unhindered deformation of the sealing element spring 41 in the direction of the end face of the slide 32; however, the projection 49 can also be dimensioned such that it forms a stroke limit 48, by means of which the maximum displacement of the support section 45 relative to the contact section 43 can be specified.The second sealing element 42 is fixedly arranged on the slide 32 in the region of the free end of the pin 34, wherein a second spacer ring 47' can be arranged between the first sealing element 41 and the second sealing element 42. A line cross-section of the passage 58 can, as shown in Figure 13, be adjusted, for example, by a plug forming an orifice. The plug can be used for a specific application, wherein an adapted plug with a corresponding orifice can be provided for each different application. The functioning of the second embodiment is identical to the functioning of the first embodiment and the associated developments. BIN337 26The third exemplary embodiment is shown in Figures 15, 16 and 17. It should already be noted here that the second sealing element 42 is designed analogously to the second sealing element 42 according to Figures 5 and 6, but the centrally formed opening is larger for receiving on the pin 34. The main valve slide 30 comprises, according to the third exemplary embodiment according to Figure 15, a slide 32 and, along the longitudinal axis L, in sequence, a sealing element spring 40, a first spacer ring 47, a first sealing element 41, a second spacer ring 47' and a second sealing element 42. The sealing element spring 40 according to Figure 16 is designed analogously to the sealing element spring 40 according to Figure 14. The third exemplary embodiment differs from the second exemplary embodiment in the arrangement of the second sealing element 42 and the resulting mode of operation.The second sealing element 42, together with the first sealing element 41, is spring-supported relative to the slide 32. The first sealing element 41 and the second sealing element 42 are therefore loosely arranged relative to the slide 32 on the slide 32. More precisely, the first sealing element 41 and the second sealing element 42 are loosely arranged on the pin 34—like the first sealing element 41—with the pin 34 having a loss-prevention feature at its free end. Furthermore, a spacer ring 47' is arranged between the first sealing element 41 and the second sealing element 42, and a spacer ring 47 is arranged between the first sealing element 41 and the sealing element spring 40. BIN337 27The spacer ring 47' between the first sealing element 41 and the second sealing element 42 preferably has a thickness that approximately corresponds to the first distance between the first and second sealing collars 52, 52 along the longitudinal axis L. Both the first sealing element 41 and the second sealing element 42 are jointly pressed against the respective sealing collar 51, 52 by the sealing element spring 40 and thus cooperate with it. The first sealing element 41 is an annular disk, similar to the previously described embodiments. With increasing pressure, the fluid can also flow through the bypass channels 46 in this embodiment. However, in this embodiment, the first sealing element 41 and the second sealing element 42 can be lifted together against the force of the sealing element spring 40, wherein the stroke limiter 48 is designed analogously to the second embodiment according to Figures 13 and 14.A fourth embodiment is shown in Figures 18-20 and, compared to the previously described embodiments, has a particularly short overall length, measured along the longitudinal axis L. According to the fourth embodiment shown in Figure 18, the main valve slide 30 comprises a slide 32 and, along the longitudinal axis L, in sequence, the sealing element spring 40, the first spacer ring 47, and the first sealing element 41. BIN337 28On the end face of the slide 32, a projection 49 is formed, by means of which the sealing element spring 40 is arranged at a distance from the end face of the slide 32. The sealing element spring 40 is designed as a flat disc spring, analogous to the sealing element spring 40 described with reference to Figures 14 or 16, and has an annular contact section 43 and an annular support section 45. Between the annular contact section 43 and an annular support section 45, two spring sections 44 are formed which connect the contact section 43 and the support section 45 and enable an elastic displacement of the support section 45 relative to the contact section 43.The first sealing element 41 is arranged by means of a spacer ring 47 at a distance from the sealing element spring 40 along the longitudinal axis L and is held spring-loaded on the slide 32 by means of the sealing element spring 40 - as in the previous embodiments - and lies sealingly against the second sealing collar 52 of the main valve seat. The second sealing element 42 is formed by the sealing element spring 40 or by the contact section 43 of the sealing element spring 40. The contact section 43 has a first side and a second side opposite the first side, wherein the first side lies against the slide 32 or the projection 49 and the second side interacts with the first sealing collar 51 of the main valve seat 50. As can be seen in Figure 18, it is not absolutely necessary for the second sealing element 42 to rest on the first sealing collar 51, but there can also be a slight gap between the. BIN337 29second sealing collar 52 and the second sealing element 42. The width of the gap can be adjusted by a suitable selection of the spacer ring 47 and the adjusting means 16. The sealing element spring 40, the spacer ring 47, and the first sealing element 41 can be arranged movably relative to the pin 34 on the slide 32 in the manner described above, wherein a loss protection device can also be provided at the free end of the pin 34 in this exemplary embodiment. The weak sealing element spring 40 and the main valve spring 26 are connected in series in this exemplary embodiment, wherein the weak sealing element spring 40 preloads the main valve spring 26.As the pressure increases, the fluid can lift the first sealing element 41 together with the spacer ring 47 against the force of the sealing element spring 40, whereby the stroke limiter 48 of the first sealing element 41 can be designed analogously to the second or third embodiment according to Figures 13-17. As the pressure continues to rise, the slide valve would then also be lifted against the force of the main valve spring 26 together with the first sealing element 41, the spacer ring 47, and the sealing element spring 40 encompassing the second sealing element 42. BIN337 30 List of reference symbols 1 Pressure control valve 10 Valve housing 12 Main housing part 14 Wall section 15 Outlet openings 16 Adjustment means 20 Main valve 25 Main valve chamber 26 Main valve spring 30 Main valve spool 32 Spool 34 Zapfen 35 Niet40 Sealing element spring 41 First sealing element 42 Second sealing element 43 Contact section 44 Spring section 45 Support section 46 Bypass channel 47 Spacer ring 48 Stroke limiter 49 Projection 50 Main valve seat 51 First sealing collar 52 Second sealing collar 58 Passage 60 Pilot valve 61 First passage channel BIN337 31 62 second passage channel 63 first pilot valve seat 64 second pilot valve seat 65 pilot valve chamber 66 pilot valve seal 70 actuating device 72 actuator housing 74 bearing elements 75 Stößel K1 spring rate of 26K2 spring rate of 40longitudinal axis

Claims

BIN337 32 Patent claims 1 . Druckregelventil (1) zum Steuern oder Regeln eines Pressure of a fluid in a pilot pressure chamber, comprising ^ ein Ventilgehäuse (10) mit mindestens einem Einlass, which is fluidically connectable to the pilot pressure chamber, and with at least one outlet (O), wherein a main valve chamber (25) and a pilot valve chamber (65) are arranged between the at least one inlet (I) and the at least one outlet (O), ^ eine elektromagnetische Betätigungseinrichtung (70), by means of which a pilot valve (60) arranged in the pilot valve chamber (65) can be opened and / or closed, ^ wobei in dem Hauptventilraum (25) ein Hauptventil (20) with a main valve seat (50) and a main valve slide (30) movable in a longitudinal axis (L) with a slide (32), ^ wobei der Hauptventilschieber (30) durch eine Haupt-valve spring (26) is pretensioned into a closed position in which the main valve slide (30) cooperates sealingly with the main valve seat (50), characterized in that the main valve slide (30) comprises the slide (32) and at least one sealing element (41, 42) which is spring-supported on the slide (32) and that the at least one sealing element (41, 42) can cooperate sealingly with the main valve seat (50). 2 . Druckregelventil (1) nach einem der vorgenannten An- sayings, characterized in that BIN337 33 a sealing element spring (40) which supports at least one sealing element (41, 42) relative to the slide (32), and that a spring rate (K1) of the main valve spring (26) is greater than a spring rate (K2) of the sealing element spring (40).

3. Druckregelventil (1) nach einem der vorgenannten An- claims, characterized in that the at least one sealing element (41) is movable in the longitudinal axis (L) relative to the slide (32).

4. Druckregelventil (1) nach einem der vorgenannten An-claims, characterized in that a stroke limiter (48) is provided, by which a displacement of the at least one sealing element (41, 42) in the longitudinal axis (L) relative to the slide (32) is limited.

5. Druckregelventil (1) nach einem der vorgenannten An- claims, characterized in that the main valve seat (50) has a first sealing collar (51) and a second sealing collar (52).

6. Druckregelventil (1) nach einem der vorgenannten An- claims, characterized in that the first sealing collar (51) and a second sealing collar (52) are arranged around the longitudinal axis (L) and are radially spaced from one another. BIN337 34 7. Druckregelventil (1) nach einem der vorgenannten An- claims, characterized in that two sealing elements (41, 42) are arranged, wherein the first sealing element (41) and the second sealing element (42) are arranged on the slide (32), and that the first sealing element (41) can cooperate with the first sealing collar (51) and the second sealing element (42) can cooperate with the second sealing collar (52).

8. Druckregelventil (1) nach einem der vorgenannten An- Claims, characterized in that the second sealing element (42) is fixedly arranged on the slide (32) or that the second sealing element (42) is arranged movably on the slide (32) relative to the slide (32) and is held at a distance from the first sealing element (41) in the longitudinal axis (L).

9. Druckregelventil (1) nach einem der vorgenannten An- claims, characterized in that the main valve slide (30) has a pin (34) projecting from the slide (32) in the longitudinal axis (L) and that the first sealing element (41) and / or the second sealing element (42) are arranged on the pin (34).

10. Druckregelventil (1) nach einem der vorgenannten An- sayings, characterized in that BIN337 35 the first sealing element (41) and / or the second sealing element (42) and / or the first sealing collar (51) and / or the second sealing collar (52) have or have at least one bypass channel (46) through which the fluid can flow.

11. Druckregelventil (1) nach einem der vorgenannten An-claims, characterized in that the sealing element spring (40) comprises a disc spring or a finger spring.

12. Druckregelventil (1) nach einem der vorgenannten An- claims, characterized in that the valve housing (10) comprises a main housing part (12) and a wall section (14) with the main valve seat (50).

13. Druckregelventil (1) nach einem der vorgenannten An- claims, characterized in that the wall section (14) can be positioned relative to the main housing part (12) in the longitudinal axis (L) via adjusting means (16).

14. Druckregelventil (1) nach einem der vorgenannten An- claims, characterized in that the pilot valve chamber (60) is connected via a first passage channel (61) to the main valve chamber (25) and the at least BIN337 36 an inlet (I) and is fluidically connected to the outlet (O) via a second passage channel (62).

15. Druckregelventil (1) nach einem der vorgenannten An-Claims, characterized in that a tappet (75) can move a pilot valve seal (66) along the longitudinal axis (L) between a first position and a second position by means of the energizable actuating device (70), and in that the pilot valve seal (66) bears sealingly against a pilot valve seat (63, 64) in the first position and / or a second position.

16. Druckregelventil (1) nach einem der vorgenannten An- claims, characterized in that the actuating device (70) is pressure-balanced.

17. Schwingungsdämpfer mit einem Druckregelventil (1) nach one of the aforementioned claims.

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