Pressure 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

Abstract

The present invention relates to a pressure control valve (1) for controlling or regulating a pressure of a fluid in a pilot pressure chamber, comprising a valve housing (10) with at least one inlet, 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), an electromagnetic actuating device (70) by which a pilot valve (60) arranged in the pilot valve chamber (65) can be opened and / or closed, wherein a main valve (20) with a main valve seat (50) and a main valve slide (30) with a slide (32) movable along a longitudinal axis (L) is arranged in the main valve chamber (25), wherein the main valve slide (30) is prestressed into a closed position by a main valve spring (26),in which the main valve spool (30) cooperates sealingly with the main valve seat (50), wherein the main valve spool (30) comprises the spool (32) and at least one sealing element (41, 42) which is spring-supported on the spool (32), and wherein the at least one sealing element (41, 42) can cooperate sealingly with the main valve seat (50). Furthermore, the present invention relates to a vibration damper with a pressure control valve (1).

Description

[0001] The present invention relates to a pressure control valve for controlling or regulating a pressure of a fluid in a pilot pressure chamber having the features of patent claim 1. Furthermore, the present invention relates to a vibration damper having such a pressure control valve having the features of patent claim 17.

[0002] Pressure control valves are known in various designs from the prior art. For example, pressure control valves of this type are used in vibration dampers in motor vehicles, with the damping characteristics of the pressure control valve depending on the volume flow of the fluid flowing through the proportional valve. Depending on the volume flow, a softer, more comfortable damping or a harder, more sporty damping can be set. Vibration dampers use an energizable 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 state of the vehicle or the condition of the floor covering over which the vehicle is currently traveling.

[0003] 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. If pilot-operated valves are designed as proportional valves or proportional spools, the volumetric flows flowing through the proportional valve or proportional spool 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 flowing volumetric flow at an applied overpressure in the pilot chamber.

[0004] 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 2016 0 091 044 A1 and WO 2016 066 314 A1. The design becomes particularly complex because multiple slides must be used. Further vibration dampers are disclosed in US 2016 0 369 862 A1, JP 2009 115 319 A, US 5 147 018 A, WO 2011 023 351 A1, and US 2005 0 016 086 A1.

[0005] Such pressure control valves have proven themselves in the past, but they exhibit undesirable behavior, particularly at very low overpressures, in that the flow rate initially increases only slightly or initially does not increase at all as the overpressure increases. This behavior is referred to as 'zero point carryover'.

[0006] Another disadvantage of state-of-the-art pressure control valves has proven to be that in the lower characteristic curve range, i.e., at lower overpressures, the characteristic curves vary considerably due to component tolerances, which can result in significant variations in the damping behavior. Furthermore, there are only limited options for adapting the characteristic curves to specific applications.

[0007] This is where the present invention comes in.

[0008] The present invention is dedicated to the task of proposing a pressure control valve of this type that effectively eliminates the disadvantages known from the prior art. The proposed pressure control valve should be simple in design and allow the flow through the pressure control valve to be controlled in the lower characteristic curve range.

[0009] This object is achieved by a pressure control valve having the features of patent claim 1 and a vibration damper having the features of patent claim 17.

[0010] Further advantageous embodiments of the present invention are specified in the subclaims.

[0011] 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 which is fluidically connectable to the pilot pressure chamber.

[0012] Furthermore, 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 further comprises an electromagnetic actuating device by which the pilot valve arranged in the pilot valve chamber can be opened and / or closed.

[0013] 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 held in a closed position by a main valve spring, with the main valve slide sealingly interacting with the main valve seat in the closed position.

[0014] Preferably, the main valve slide comprises the slide and at least one sealing element which is spring-supported on the slide and wherein the at least one sealing element cooperates sealingly with the main valve seat.

[0015] The at least one sealing element can, for example, be a disc-shaped element that can be manufactured cost-effectively and can be easily replaced to adapt the characteristic curve of the pressure control valve.

[0016] 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-supported relative to the spool can be set such that initially at low pressure the first sealing element slightly opens the main valve seat before the spool itself moves against the force of the main valve spring at higher pressures. In other words, the spring rate with which the at least one sealing element is held spring-supported relative to the spool 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 low overpressure, without a so-called carryover at the zero point occurring.

[0017] According 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 each specific application, thereby making it easy to adapt the proposed pressure control valve to different applications with different requirements for the characteristic curve.

[0018] A further development of the present invention provides for a stroke limiter to limit the displacement of the at least one sealing element along 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 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.

[0019] According to a preferred development of the present invention, the main valve seat has a first sealing collar and a second sealing collar.

[0020] Furthermore, it has 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.

[0021] It may also be advantageous if the first sealing collar and the second sealing collar are arranged at a distance 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.

[0022] 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 interacts sealingly 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 realize a multi-stage seal on the slide.

[0023] 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.

[0024] Preferably, 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.

[0025] According to a further 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 disc that rests against the main valve seat and determines the position of the slide in which the main valve element is arranged in the closed position.

[0026] 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 kept at a distance from each other in the longitudinal axis, in particular by a spacer disk, and can be moved together in the longitudinal axis relative to the slide. 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. When the pressure increases, the entire package can initially move in a spring-loaded manner relative to the slide, thus opening the main valve seat slightly. When the pressure increases, the slide moves together with the package and enables the flow of larger volume flows.

[0027] Furthermore, it has proven advantageous if the main slide has a pin protruding from the slide in the longitudinal axis. The first sealing element and / or the second sealing element can be arranged on or at 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.

[0028] It may 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 also be used to secure the second sealing element to the slide and / or to form a loss-prevention device 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.

[0029] 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 volume flow can flow through a bypass even with a very small pressure difference or overpressure. 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 the characteristic curve from being dragged out at the zero point.

[0030] A preferred embodiment 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 precisely adjusted in a simple manner.

[0031] The spring element can also include the aforementioned stroke limiter. For example, the spring element can have angled regions through which a stop can be formed to limit the stroke of the at least one spring element.

[0032] The sealing element spring can also comprise the second sealing element.

[0033] The sealing element spring may, 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.

[0034] 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 can 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, wherein corresponding openings are provided in the wall section for the at least one inlet and in the main housing part for the at least one outlet.

[0035] Furthermore, it has proven advantageous to provide at least one adjustment means by which the position of the main valve seat relative to the main housing part can be adjusted along the longitudinal axis. In the simplest case, the adjustment means can comprise a spacer ring inserted into the recess to specify a distance between the main housing part and the wall section.

[0036] 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 sealingly engage.

[0037] 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.

[0038] In 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 sealingly engage a first pilot valve seat and can close the first passage channel.

[0039] When the actuating device is actuated, the plunger 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 activated, allowing the damping characteristics to be specifically modified.

[0040] A further development of the present invention provides that the main slide is designed as a proportional slide.

[0041] Furthermore, it has proven advantageous if the actuating device is pressure-balanced. In particular, it is preferred if the actuating device comprises a pressure-balance chamber that can communicate with the pilot valve chamber. For this purpose, it is advantageous if the tappet has a compensating bore through which the tappet can be flowed along its longitudinal axis.

[0042] Another aspect of the present invention relates to a vibration damper with a pressure control valve as described above.

[0043] Three 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: Fig. 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, comprising a pilot valve actuatable 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 slide with a slide, a first sealing element, and a second sealing element, Fig. 2 an enlarged detailed view of the pressure control valve according to Fig. 1, Fig. 3 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 slide of the main valve slide, Fig. 4 a side view of the sealing element spring according to Fig. 3, Fig. 5 a detailed view of the second sealing element of the main valve slide according to Fig. 1 or Fig. 2, Fig. 6 a side view of the sealing element according to Fig. 5, Fig. 7 an enlarged and partial view of the pressure control valve according to a first development of the sealing element spring, Fig. 8 an enlarged view of the sealing element spring according to Fig. 7, Fig. 9 a side view of the sealing element spring according to Fig. 8, Fig. 10 an enlarged and partial view of the pressure control valve according to a second development of the sealing element spring, Fig. 11 an enlarged view of the sealing element spring according to Fig. 10, Fig. 12 a side view of the sealing element spring according to Fig. 11, Fig. 13 an enlarged detailed view of the pressure control valve according to a second embodiment, Fig. 14 an enlarged view of the sealing element spring according to Fig. 9, Fig. 15 an enlarged detailed view of the pressure control valve according to a third embodiment, Fig. 16 an enlarged view of the sealing element spring according to Fig. 15, Fig. 17 an enlarged view of the first sealing element according to Fig. 15, Fig. 18 an enlarged detailed view of the pressure control valve according to a fourth embodiment, Fig. 19 an enlarged view of the second sealing element with the sealing element spring according to Fig. 18, and Fig. 20 a side view of the second sealing element according to Fig. 19.

[0044] Identical or functionally equivalent parts or features are identified by the same reference numerals in the following detailed description of the figures. Likewise, not all identical or functionally equivalent parts or features are provided with a reference numeral in the figures.

[0045] First, a first exemplary embodiment is described in detail below using the Fig. 1-5. The further embodiments are then briefly described, focusing only on the differences from the previous embodiments. It should be noted at this point that the features of the embodiments and also of the further developments can be combined with one another.

[0046] Fig. 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.

[0047] Fig. 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.

[0048] The pressure control valve 1 comprises a valve housing 10 with at least one inlet I and at least one outlet O.

[0049] 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.

[0050] 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 areas in which the at least one inlet I and the at least one outlet O could be located.

[0051] The valve housing 10 at least partially encloses the main valve chamber 25 and the pilot valve chamber 65.

[0052] The pilot valve 60 includes a first pilot valve seat 63 and may further include a second pilot valve seat 64.

[0053] 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 can flow through the at least one inlet I, the main valve chamber 25 and the first passage 61 into the pilot valve chamber 65 and can flow out through the second passage 62 to the at least one outlet O.

[0054] In addition, the pressure control valve 1 has an energizable actuating device 70, wherein the energizable actuating device 70 is preferably actuated by a Fig. 1 concealed electromagnetic actuator can be formed.

[0055] 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 in a known manner when the excitation coil is energized, counter to the spring force of the return spring.

[0056] 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 material connection, in particular by pressing it into the receiving area.

[0057] 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 the force of a return spring (not shown). For this purpose, the plunger 75 is preferably connected to the armature and can furthermore - as in the Fig. 1 - are held movably mounted on the actuator housing 72 along the longitudinal axis L by means of bearing elements 74.

[0058] The tappet 75 protrudes from the actuator housing 72 into the valve housing 10. As can be seen, for example, in the detailed illustration in Fig. 2 can be removed, a first free end of the plunger 75 projects into the pilot valve chamber 65.

[0059] Furthermore, it can be seen from the accompanying figures that the tappet 75 has a pressure equalization bore through which the tappet 75 can be flowed along the longitudinal axis L. Consequently, the fluid can flow from the first free end through the tappet 75 into a pressure equalization chamber (not shown) opposite the armature, whereby pressure equalization can take place and the pressure control valve 1 can be designed to be pressure-balanced.

[0060] The plunger 75 further includes a pilot valve seal 66 disposed on the plunger 75, preferably adjacent to the free end. The pilot valve seal 66 may, for example, be secured to the plunger 75 by means of a retaining ring, as shown in the accompanying figures.

[0061] The pilot valve seal 66, according to the Fig. The embodiments shown in Figures 1 to 5 comprise a disc element which is preferably designed in the manner of a disc-shaped flat spring element.

[0062] In the accompanying figures, the electromagnetic actuator 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 sealingly abuts the second pilot valve seat 64 in the first position.

[0063] In 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 in the direction of the first pilot valve seat 63.

[0064] In this position, the pilot valve seal 66 lies sealingly against the first pilot valve seat 63 and closes the first passage channel 61. In this position, the fluid cannot flow from the at least one inlet into the pilot valve chamber 65.

[0065] 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.

[0066] 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.

[0067] In order to determine the position of the main valve seat 50 in 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.

[0068] With reference to the Fig. 2, Fig. 7, Fig. 10, Fig. 13, Fig. 15 and Fig. 18 it can be seen that the main valve seat 50 has a first sealing collar 51 and a second sealing collar 52 which project into the main valve chamber 25 in the longitudinal axis L.

[0069] The 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.

[0070] 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.

[0071] 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.

[0072] The main valve spring 26 has a spring rate K1.

[0073] 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, for example, Fig. 2, Fig. 7, Fig. 10, Fig. 15 and Fig. 18 is shown.

[0074] The main valve spool 30 comprises according to the first embodiment according to the Fig. 1-6 and the further training according to the Fig. 7-12 a slider 32, a first sealing element 41, a second sealing element 42 and a sealing element spring 40.

[0075] 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 along the longitudinal axis L, outlet openings 15 in the valve housing 10 can be opened to a greater or lesser extent, or closed completely or only partially. The slide accommodates the main valve spring 26 within its interior.

[0076] 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.

[0077] The passage 58 may be formed in the pin 34.

[0078] The sealing element spring 40, shown as an example in the Fig. 3 and Fig. 4, can be a substantially disc-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 substantially annular 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 against the spring force of the spring section 44. The sealing element spring 40 has a spring rate K2.

[0079] The first sealing element 41 can also be referred to as a sealing disc and is preferably a circular disc with a central opening.

[0080] The second sealing element 42 is shown in detail in the Fig. 5 and Fig. 6 and can also be referred to as a stop disc. The second sealing element 42 is a circular disc 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.

[0081] 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 sealingly bear 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.

[0082] 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.

[0083] The opening of the sealing element spring 40 and / or the opening of the first sealing element 41 are or are designed to form a running gap between the pin 34 and themselves, preferably with a clearance fit.

[0084] The second sealing element 42 is arranged on the side of the first sealing element 41 facing away from the sealing element spring 40, spaced apart 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.

[0085] The Fig. 2, Fig. 7 and Fig. 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 abuts the second sealing collar 52 of the main valve seat 50.

[0086] The second sealing element 42 can be attached to the pin 34 in any desired manner, for example, by positive, non-positive, and / or material connection. 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.

[0087] When the pressure in the pilot pressure chamber (not shown) increases, a pressure force initially acts on the first sealing element 41 through the bypass channel(s) 46, lifting 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 continues to increase, the main valve spool 30 is raised. Due to the weak sealing element spring 40, the main valve 20 opens even at low pressures, allowing a defined characteristic curve to be realized without carryover at the zero point even at low pressures.

[0088] The further training courses presented in the Fig. 7-9 and 10-12 differ from the previously described embodiment in the design of the sealing element spring 40.

[0089] The first further training according to the Fig. 7-9 provides that the stroke limiter 48 is formed by the sealing element spring 40. For this purpose, several stops are provided around the circumference, which are preferably arranged between the spring arms. 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 perform the function of the limiter 48.

[0090] The second development of the first embodiment according to the Fig. 10-12 also provides that the stroke limiter 48 is formed by the sealing element spring 40. For this purpose, several tabs protrude into the opening of the sealing element spring 40, which are angled to form a shoulder each forming the stroke limiter 48.

[0091] 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 to take over the function of the stroke limiter 48.

[0092] The Fig. 13 and Fig. 14 shows a second embodiment of the pressure control valve 1, wherein the pressure control valve 1 differs from the first embodiment in that the second sealing element 42 is held on the pin 34, in particular at the free end of the pin 34, not by a rivet, but by caulking. Furthermore, this 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.

[0093] The main valve slide 30 comprises according to the second embodiment according to the Fig. 13 and Fig. 14 a slide 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 slide 30 can have a second spacer ring 47' which is arranged between the first sealing element 41 and the second sealing element 42.

[0094] The sealing element spring 40 is in this embodiment, like the Fig. 14, 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.

[0095] The contact section 43 is arranged radially outside the support section 45 and the opening is inside the support section 45.

[0096] 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, spaced from the support section 45 of the sealing element spring 40 by means of the spacer ring 47. The spacer ring 47 specifies the maximum displacement, i.e., the stroke limit 48, of the first sealing element 41 before it comes into contact with the sealing element spring 40.

[0097] On the front side of the slide 32, according to Fig. 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.

[0098] The projection 49 allows unhindered deformation of the sealing element spring 41 in the direction of the end face of the slide 32, but the projection 49 can also be dimensioned such that it forms a stroke limiter 48, by which the maximum displacement of the support section 45 relative to the contact section 43 can be predetermined.

[0099] The second sealing element 42 is arranged fixedly 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.

[0100] A line cross-section of the passage 58 can, as in Fig. 13, for example, by means of a plug forming an orifice. The plug can be used for specific applications, with a customized plug with a corresponding orifice being provided for each different application.

[0101] The functioning of the second embodiment is identical to the functioning of the first embodiment and the associated further developments.

[0102] The third embodiment is shown in the Fig. 15, Fig. 16 and Fig. 17. It should be noted here that the second sealing element 42 is analogous to the second sealing element 42 according to Fig. 5 and Fig. 6, but the central opening is larger to accommodate the pin 34.

[0103] The main valve slide 30 comprises according to the third embodiment according to Fig. 15 a slider 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.

[0104] The sealing element spring 40 according to Fig. 16 is analogous to the sealing element spring 40 according to Fig. 14 trained.

[0105] The third embodiment differs from the second 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-loaded against the slide 32.

[0106] The first sealing element 41 and the second sealing element 42 are therefore arranged loosely on the slide 32 opposite the slide 32. More precisely, the first sealing element 41 and the second sealing element 42 are arranged loosely on the pin 34—like the first sealing element 41—wherein the pin 34 may have a captive locking device at its free end.

[0107] 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.

[0108] The 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 in 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 interact with it.

[0109] The first sealing element 41 is an annular disc, analogous to the previously described embodiments.

[0110] 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 analogous to the second embodiment according to the Fig. 13 and Fig. 14 is trained.

[0111] A fourth embodiment is shown in the Fig. 18-20 and has a particularly short overall length, measured along the longitudinal axis L, compared to the previously described embodiments.

[0112] The main valve slide 30 comprises according to the fourth embodiment according to Fig. 18 a slide 32 and along the longitudinal axis L in sequence the sealing element spring 40, the first spacer ring 47, the first sealing element 41.

[0113] On 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.

[0114] The sealing element spring 40 is analogous to that described with reference to the Fig. 14 or Fig. 16, 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 elastic displacement of the support section 45 relative to the contact section 43.

[0115] The first sealing element 41 is arranged by means of a spacer ring 47 in the longitudinal axis L at a distance from the sealing element spring 40 and is held supported 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.

[0116] 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 bears against the slide 32 or the projection 49 and the second side cooperates with the first sealing collar 51 of the main valve seat 50. As shown in Fig. 18, it is not absolutely necessary for the second sealing element 42 to rest on the first sealing collar 51, but rather a slight gap may also be formed between the second 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.

[0117] 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 prevention device can also be provided at the free end of the pin 34 in this exemplary embodiment.

[0118] The weak sealing element spring 40 and the main valve spring 26 are connected in series in this embodiment, with the weak sealing element spring 40 preloading the main valve spring 26.

[0119] When 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, wherein the stroke limiter 48 of the first sealing element 41 is analogous to the second or third embodiment according to the Fig.13-17. If the pressure continues to rise, the slide would then also be raised 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 surrounding the second sealing element 42. List of reference symbols 1 pressure control valve 10 valve housings 12 Main housing part 14 Wall section 15 outlet openings 16 adjustment tools 20 Main valve 25 Main valve chamber 26 Main valve spring 30 main valve spool 32 sliders 34 cones 35 rivets 40 sealing element spring 41 first sealing element 42 second sealing element 43 Annex section 44 spring section 45 support section 46 Bypass channel 47 spacer ring 48 Stroke limitation 49 lead 50 Main valve seat 51 first sealing collar 52 second sealing collar 58 passage 60 pilot valve 61 first passage channel 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 housings 74 bearing elements 75 tappets K1 spring rate of 26 K2 spring rate of 40 L Longitudinal axis QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] US 2016 0 091 044 A1

[0004] WO 2016 066 314 A1

[0004] US 2016 0 369 862 A1

[0004] JP 2009 115 319 A

[0004] US 5 147 018 A

[0004] WO 2011 023 351 A1

[0004] US 2005 0 016 086 A1

[0004]

Claims

[1] Pressure control valve (1) for controlling or regulating a pressure of a fluid in a pilot pressure chamber, comprising - a valve housing (10) with at least one inlet 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), - an electromagnetic actuating device (70) by which a pilot valve (60) arranged in the pilot valve chamber (65) can be opened and / or closed, - wherein a main valve (20) with a main valve seat (50) and a main valve slide (30) with a slide (32) movable in a longitudinal axis (L) is arranged in the main valve chamber (25), - wherein the main valve slide (30) is biased by a main valve spring (26) into a closed position in which the main valve slide (30) cooperates sealingly with the main valve seat (50), characterized by 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] Pressure control valve (1) according to one of the preceding claims, characterized by that a sealing element spring (40) supports the at least one sealing element (41, 42) against 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] Pressure control valve (1) according to one of the preceding claims, characterized by that the at least one sealing element (41) is movable in the longitudinal axis (L) relative to the slide (32). [4] Pressure control valve (1) according to one of the preceding claims, characterized by 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] Pressure control valve (1) according to one of the preceding claims, characterized by that the main valve seat (50) has a first sealing collar (51) and a second sealing collar (52). [6] Pressure control valve (1) according to one of the preceding claims, characterized by 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. [7] Pressure control valve (1) according to one of the preceding claims, characterized bythat 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] Pressure control valve (1) according to one of the preceding claims, characterized by 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] Pressure control valve (1) according to one of the preceding claims, characterized by 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] Pressure control valve (1) according to one of the preceding claims, characterized by that 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] Pressure control valve (1) according to one of the preceding claims, characterized by that the sealing element spring (40) comprises a disc spring or a finger spring. [12] Pressure control valve (1) according to one of the preceding claims, characterized by that the valve housing (10) comprises a main housing part (12) and a wall section (14) with the main valve seat (50). [13] Pressure control valve (1) according to one of the preceding claims, characterized by that the wall section (14) can be positioned in the longitudinal axis (L) relative to the main housing part (12) via adjusting means (16). [14] Pressure control valve (1) according to one of the preceding claims, characterized by that the pilot valve chamber (60) is fluidically connected to the main valve chamber (25) and the at least one inlet (I) via a first passage channel (61) and to the outlet (O) via a second passage channel (62). [15] Pressure control valve (1) according to one of the preceding claims, characterized by 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 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] Pressure control valve (1) according to one of the preceding claims, characterized by that the actuating device (70) is pressure balanced. [17] Vibration damper with a pressure control valve (1) according to one of the preceding claims.

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