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

Abstract

A pressure regulating valve (1) for controlling or regulating the pressure of a fluid is described, comprising a valve body (10) with at least one pressure-side inlet and at least one outlet, wherein a main valve chamber (50) and a control valve chamber (20) are arranged between the at least one inlet and the at least one outlet, and an electromagnetic actuating device (80) for actuating a control valve (40) arranged in the control valve chamber (20), wherein a main valve spool (60) movable in a longitudinal axis (L) is arranged in the main valve chamber (50), which can be arranged in an open position and a closed position, wherein in the closed position at least one sealing section (61, 64) of the main valve spool (60) interacts sealingly with at least one sealing section (71, 74) of a main valve seat (70), and wherein the main valve spool (60) and / or main valve seat (70) is located in at least one of the sealing sections (61, 64, 71,74) have or feature a surface structuring (25). Furthermore, a vibration damper with a pressure regulating valve (1) is described.

Description

[0001] The present invention relates to a pressure control valve for controlling or regulating the pressure of a fluid in a pilot pressure chamber, comprising the features of claim 1. Furthermore, the present invention relates to a vibration damper comprising such a pressure control valve, comprising the features of 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, where the damping characteristic of the pressure control valve depends on the volume flow rate of the fluid flowing through the proportional valve. Depending on the volume flow rate, a more comfort-oriented, softer damping or a more sporty, firmer damping can be set. In vibration dampers, an electrically actuated device is used with which several damping characteristics can be set by the driver or automatically by an on-board computer depending on the driving condition of the motor vehicle or the condition of the road surface over which the motor vehicle is currently traveling.

[0003] The fluid can be hydraulic or pneumatic, with hydraulic fluid or compressed air being the most common. Pilot pressure chambers in hydraulically or pneumatically operated devices serve to control or regulate pilot-operated valves, often designed as hydraulic or pneumatic spools. When pilot-operated valves are designed as proportional valves or proportional spools, the flow rates through the proportional valve or spool can be continuously adjusted within certain limits by varying the pressure in the pilot pressure chamber. The respective pressure control valve should have a defined characteristic curve that specifies the flow rate at a given overpressure in the pilot chamber.

[0004] DE 10 2023 112 797 teaches a pressure regulating valve with a main valve spool having an inner and an outer sealing section. The outer sealing section ensures a tight seal, with the outer sealing section of the main valve spool resting on an outer sealing section of the main valve seat.

[0005] A defined gap is formed between the inner sealing sections of the main valve spool and the main valve seat, created by axial and / or radial distances and / or chamfers. This gap restricts the flow. Consequently, the pressure is reduced before it acts on the outer sealing sections. This results in a smoother opening and closing behavior of the main valve spool, thus avoiding discontinuities in the hydraulic characteristic curve.

[0006] Pressure control valves of this type have proven reliable in the past, but they have a complex design. In particular, the geometric definition of the throttle cross-section at the inner sealing sections, and thus the throttling effect, is subject to significant tolerances. Therefore, considerable effort must be made to maintain these tolerances in order to achieve low characteristic curve variation. Specifically, known pressure control valves often exhibit undesirable behavior under rapidly increasing overpressure, with the flow rate initially rising or falling unpredictably.

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

[0008] The present invention is based on the objective of proposing a pressure control valve of the generic type that advantageously eliminates the disadvantages known from the prior art. The proposed pressure control valve should have a simplified design with simplified tolerances and / or improved flow guidance, resulting in, in particular, low characteristic curve variation, especially at low flow rates.

[0009] This problem is solved by a pressure regulating valve with the features of claim 1 and a vibration damper with the features of claim 17.

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

[0011] The pressure control valve with the features of claim 1, for controlling or regulating the pressure of a fluid in a pilot pressure chamber, has a valve body with at least one inlet and at least one outlet. The at least one inlet is fluidically connectable to the pilot pressure chamber.

[0012] Furthermore, the valve housing has a control valve chamber for a control valve and a main valve chamber for a main valve, arranged between the at least one inlet and the at least one outlet.

[0013] The pressure regulating valve also includes an electromagnetic actuator for operating the control valve. The actuator can open and / or close the control valve.

[0014] Furthermore, a main valve spool movable along the longitudinal axis and a main valve seat are arranged in the main valve chamber, the main valve spool being capable of being positioned in an open and a closed position. In the open position, the fluid can flow between the main valve spool and the main valve seat from the at least one inlet to the at least one outlet.

[0015] In the closed position, at least one sealing section of the main valve spool and at least one sealing section of the main valve seat act together to seal. This prevents fluid from flowing between the main valve spool and the main valve seat from the at least one inlet to the at least one outlet in the closed position.

[0016] According to the invention, the main valve spool and / or the main valve seat has or have a surface structuring in at least one of the sealing sections.

[0017] The present invention is based on the finding that, due to adhesive forces, the main valve spool adheres undesirably to the main valve seat, causing the flow rate to rise or fall unpredictably with increasing differential pressure. This results in an undefined characteristic curve, with the characteristic curve exhibiting significant scatter, particularly at low flow rates. For this reason, the at least one sealing section of the main valve spool and / or the at least one sealing section of the main valve seat features surface structuring. This surface structuring minimizes leakage between the two interacting sealing sections of the main valve spool and the main valve seat. Furthermore, it has been shown that the surface structuring delays the transition from laminar to turbulent flow, thereby further stabilizing the characteristic curve.

[0018] A further development of the present invention provides that the main valve spool and / or the main valve seat has at least one sealing collar. The sealing collar preferably projects along the longitudinal axis from the main valve spool and / or the main valve seat, with the at least one sealing section preferably being arranged at a free end of the at least one sealing collar. In the open position, the sealing collar reduces pressure losses by means of a short throttling gap, and in the closed position, a high surface pressure between the two interacting parts achieves a good sealing effect.

[0019] Furthermore, it has proven advantageous if the at least one sealing collar has a sealing surface at its free end that can interact with the main valve spool and / or the main valve seat to provide a surface seal. The sealing surface is preferably annular, and in particular, circular. It is especially preferred if the respective sealing surface is arranged in a plane perpendicular to the longitudinal axis. The respective sealing surface results in surface contact between the two interacting sealing sections, whereby stress concentrations can be avoided by a larger contact area. The corresponding sealing surfaces can also be manufactured precisely and easily.

[0020] A further development of the present invention provides that the surface structuring extends completely over the sealing surface of the at least one sealing section. Due to the formation of the surface structuring in the at least one sealing section of the main valve spool and / or the main valve seat, a leakage can occur between the at least one inlet and the at least one outlet between the main valve spool and the main valve seat. Preferably, the surface structure is larger than the preferably annular, more preferably circular, sealing surface of the main valve seat and / or the main valve spool.

[0021] A further development of the present invention provides that the main valve spool and / or the main valve seat has an inner sealing section and an outer sealing section. The two inner sealing sections of the main valve spool and the main valve seat act together to seal, and / or the two outer sealing sections of the main valve spool and the main valve seat act together to seal.

[0022] Preferably, the inner sealing section of the main valve spool and the inner sealing section of the main valve seat have the same or corresponding diameters. More preferably, the outer sealing section of the main valve spool and the outer sealing section of the main valve seat have the same or corresponding diameters. In other words, the inner sealing sections of the main valve spool and the main valve seat have a first diameter, and the outer sealing sections of the main valve spool and the main valve seat have a second diameter, wherein the first diameter is different from the second diameter. It is particularly preferred if the first diameter is smaller than the second diameter.

[0023] An intermediate chamber can be formed between the inner and outer sealing sections of the main valve spool and / or the main valve seat. This intermediate chamber creates a cross-sectional expansion in the flow path between the main valve spool and the main valve seat, particularly when the main valve spool is in the open position.

[0024] Preferably, the inner sealing sections of the main valve spool and the main valve seat and the outer sealing sections of the main valve spool and the main valve seat are coaxial, with the inner sealing section of the main valve spool and the main valve seat preferably being spaced apart and further preferably arranged within the outer sealing section. In other words, the inner sealing section has a smaller diameter than the outer sealing section. Accordingly, the inner sealing section is arranged on the side facing the at least one inlet, and the outer sealing section is located between the inner sealing section and the at least one outlet. Pressure surges from the pilot pressure chamber initially act directly on the inner sealing section, with the corresponding inner sealing sections and the corresponding outer sealing sections interacting in the manner of a labyrinth seal.

[0025] A further development of the present invention provides that the main valve spool and / or the main valve seat have a surface structure in the inner sealing section. It is also advantageous if the main valve spool and / or the main valve seat do not have a surface structure in the outer sealing section. In other words, the outer sealing sections of the main valve spool and the main valve seat are preferably flat and, in the closed position, make essentially full-surface contact. The inner sealing sections can seal against each other in the closed position; however, the surface structure on the main valve spool and / or the main valve seat allows for leakage. This design prevents the main valve spool from sticking to the main valve seat in the closed position. It also provides a pressure regulating valve that is leak-free in the closed position.

[0026] Furthermore, it has proven advantageous if the surface structuring comprises a multitude of grooves. These grooves can preferably be introduced or machined into the sealing surface by laser or subtractive machining, forming small channels through which the medium can flow.

[0027] Furthermore, it has proven advantageous if adjacent grooves have a spacing between 0.025 mm and 0.5 mm, preferably 0.05 mm ± 0.025 mm. It has been shown that a close-meshed arrangement of the grooves prevents the main valve slide from sticking to itself.

[0028] Furthermore, a surface texturing with an Rz value of 0.04–0.06 has proven advantageous. Typically, the grooves are between 0.03 and 0.08 mm deep.

[0029] A further development of the present invention provides that the surface structuring is a laser texturing.

[0030] Furthermore, it has proven advantageous if the surface texturing comprises a stripe and / or cross pattern. For example, the surface texturing can be formed by a cross pattern, wherein adjacent stripes are spaced at the aforementioned interval of between 0.025 mm and 0.1 mm, preferably 0.05 mm ± 0.025 mm. The stripe pattern is preferably star-shaped, with at least two stripes meeting at an imaginary center point, which is preferably located on the longitudinal axis.

[0031] In a further development, it can be advantageous if the main valve spool is held resiliently in a closed position by at least one main valve spring. The at least one main valve spring presses the at least one sealing section of the main valve spool against the at least one sealing section of the main valve seat, with the spring rate determining the opening behavior of the main valve spool. It can be advantageous if the main valve spool is held resiliently in the closed position by two main valve springs connected in series, wherein, even more preferably, the springs have different spring rates.

[0032] According to a further development of the present invention, the control valve chamber is fluidically connected to the main valve chamber and to the at least one inlet via a first through-channel and to the at least one outlet via a second through-channel. The control valve can include a control valve seal arranged in the control valve chamber. The control valve seal can interact sealingly with a first and / or second control valve seat in the control valve chamber to close the first and / or the second through-channel.

[0033] According to a further development, the control valve can be actuated by means of a plunger via the actuating device. The plunger can be moved along its longitudinal axis between a first and a second position by the energized actuating device. The control valve is preferably arranged on the plunger, and the energized actuating device can move the plunger along its longitudinal axis from the first position to the second position against the force of a return spring. Preferably, the control valve includes a control valve seal that is disc-shaped, thus enabling a compact design.

[0034] In the unactuated state of the actuating device, the control valve seal is preferably arranged in the first position by means of a return spring. In the first position, the control valve seal can abut a first control valve seat and close the first through-channel.

[0035] When the actuating device is engaged, the plunger or control valve seal is in the second position, in which the control valve seal seals against the second control valve seat and closes the second passage. By appropriately actuating the device, the control valve can be used to adjust the pressure regulating valve, e.g., to selectively change the damping characteristics of the shock absorber.

[0036] Furthermore, it has proven advantageous if the actuating device is pressure-balanced. In particular, it is preferred if the actuating device includes a pressure equalization chamber that can communicate with the control valve chamber. For this purpose, it is advantageous if the plunger has a compensating bore through which fluid can flow along its longitudinal axis.

[0037] Another aspect of the present invention relates to a vibration damper with a previously described pressure regulating valve.

[0038] Below, with reference to the accompanying drawings, three exemplary embodiments of a pressure control valve according to the invention and two further developments of an embodiment are described in detail. The drawings show: Fig. 1 a sectional view of a pressure regulating valve with an energizable actuating device for actuating a control valve in a control valve chamber and a main valve spool arranged in a main valve chamber, which seals against a main valve seat, Fig. 2 an enlarged and partially cutaway representation of the pressure regulating valve according to Fig. 1, Fig. 3 a detailed representation according to detail Z1 in Fig. 2, Fig. 4 a sectional view of a third wall section having the main valve seat according to Fig. 1 to 3, wherein the main valve seat has an inner and an outer sealing section, Fig. 5 a top view of the third wall section having the main valve seat according to Fig. 4, wherein the inner sealing section has a surface texture, Fig. 6 a detailed representation according to detail Z2 in Fig. 5, Fig. 7. Further development of the main valve seat according to Fig. 5 and Fig. 6, and Fig. 8 a detailed representation according to detail Z3 in Fig. 7.

[0039] Identical or functionally equivalent parts or features are identified by the same reference numerals in the detailed description of the figures below. Likewise, not all identical or functionally equivalent parts or features in the figures are assigned a reference number.

[0040] Fig. Figure 1 shows a first exemplary embodiment of a 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), particularly in a motor vehicle, to adjust the damping characteristics of the vibration damper.

[0041] The pressure regulating valve 1 comprises a valve body 10 with at least one inlet and at least one outlet. The at least one inlet can be connected to a pilot pressure chamber (not shown).

[0042] The valve housing 10 at least partially encloses a main valve chamber 50 and a control valve chamber 20 of a control valve 40, which are spaced apart from each other along the longitudinal axis L. A main valve seat 70 and a main valve spool 60 are formed in the main valve chamber 50.

[0043] The main valve chamber 50 is fluidically connected to the at least one inlet and the at least one outlet. Furthermore, the main valve chamber 50 is fluidically arranged between the at least one inlet and the control valve chamber 20. This means that the fluid from the at least one inlet must first flow through the main valve chamber 50 before it can enter the control valve chamber 20 through the second passage 12. For this purpose, the main valve spool 60 has a passage 68 that leads into the Fig. 1-3 is shown.

[0044] The main valve spool 60 is arranged in the main valve chamber 50 and is movably mounted along the longitudinal axis X between an open position (not shown in the figures) and a closed position (shown in the figures). The main valve spool 60 is held in the closed position by a main valve spring 55 against a main valve seat 70.

[0045] In the open position, the fluid can flow between the main valve spool 60 and the main valve seat 70 from the at least one inlet to the at least one outlet.

[0046] In the closed position, at least one sealing section 61, 64 of the main valve spool 60 and at least one sealing section 71, 74 of the main valve seat 70 act together to seal. This prevents fluid from flowing between the main valve spool 60 and the main valve seat 70 from the at least one inlet to the at least one outlet in the closed position.

[0047] The main valve slide 60 is cup-shaped with a bottom and an open side. The bottom faces the at least one inlet, and the open side of the cup-shaped main valve slide 60 at least partially accommodates the main valve spring 55 and faces the control valve chamber 20.

[0048] With reference to the accompanying Fig. 2 and Fig. Figure 3 shows that the main valve spool 60 has an inner sealing section 61 and an outer sealing section 64. The inner sealing section 61 and the outer sealing section 64 are arranged coaxially. The inner sealing section 61 lies on a first diameter D1 and the outer sealing section 64 lies on a second diameter D2, where D2 > D1.

[0049] The inner sealing section 61 and / or the outer sealing section 64 of the main valve slide 60 can be, as in particular, Fig. 3 can be seen, arranged on a sealing collar 62, 65, wherein preferably the respective sealing collar 62, 65 protrudes in the longitudinal axis L in the direction of the main valve seat 70, in particular from the bottom.

[0050] The inner sealing section 61 has a sealing surface 63 at its free end and / or the outer sealing section 61 has a sealing surface 66 at its free end. The respective sealing surfaces 63, 66 are preferably annular, in particular circular, and more preferably coaxial with the longitudinal axis. Preferably, the respective sealing surfaces 63, 66 are arranged in a plane perpendicular to the longitudinal axis L.

[0051] Also with reference to the accompanying Fig. 2 and Fig. Figure 3 shows that the main valve seat 70 has an inner sealing section 71 and an outer sealing section 74. The inner sealing section 71 and the outer sealing section 74 are arranged coaxially. The inner sealing section 71 lies on a first diameter D1' and the outer sealing section 74 lies on a second diameter D2', where D2' > D1'.

[0052] The inner sealing section 71 and / or the outer sealing section 74 of the main valve seat 70 can be, as in particular, Fig. 3 can be seen, arranged on a sealing collar 72, 75, wherein preferably the respective sealing collar 72, 75 protrudes in the longitudinal axis L in the direction of the main valve slide 60.

[0053] The inner sealing section 71 has a sealing surface 73 at its free end and / or the outer sealing section 71 has a sealing surface 76 at its free end. The respective sealing surfaces 73, 76 are preferably annular, in particular circular, and more preferably coaxial with the longitudinal axis. Preferably, the respective sealing surfaces 73, 76 are arranged in a plane perpendicular to the longitudinal axis L.

[0054] The inner sealing section 61 of the main valve spool 60 and the inner sealing section 71 of the main valve seat 70, as well as the outer sealing section 64 of the main valve spool 60 and the outer sealing section 74 of the main valve seat 70, act together to seal. Thus, the first diameters D1, D1' and the second diameters D2, D2' correspond to each other, i.e., D1 ≈ D1' and D2 ≈ D2', see [reference]. Fig. 2.

[0055] The corresponding inner sealing sections 61, 71 and the corresponding outer sealing sections 64, 74 therefore act together in the manner of a labyrinth seal, wherein the inner sealing sections 61, 71 are located on the pressure side or towards the at least one inlet and the corresponding outer sealing sections 64, 74 are located towards the at least one outlet.

[0056] Preferably, the inner sealing section 61 of the main valve slide 60 rests on the inner sealing section 71 of the main valve seat 70 in the closed position.

[0057] Preferably, the outer sealing section 64 of the main valve slide 60 rests on the outer sealing section 74 of the main valve seat 70 in a sealing position.

[0058] An intermediate chamber is formed between the inner sealing sections 61, 71 and the outer sealing sections 64, 74. The intermediate chamber can be formed by a recess in the main valve spool 60 and / or by a recess in the valve housing 10.

[0059] To prevent the main valve spool 60 from sticking to the main valve seat 70, the at least one sealing section 61, 64 of the main valve spool and / or the at least one sealing section 71, 74 of the main valve seat 70 have a surface structuring 25.

[0060] The surface structuring 25 includes, according to the Fig. 5 and Fig. 7 a multitude of grooves 26. The grooves 26 form small channels through which the fluid can flow.

[0061] Adjacent grooves 26 preferably have a spacing between 0.025 mm and 0.1 mm, more preferably a spacing of 0.05 mm ± 0.025 mm. Furthermore, it has proven advantageous if the grooves have a depth and / or width between 0.025 mm and 0.1 mm, preferably 0.05 mm ± 0.025 mm.

[0062] Furthermore, it is advantageous if the surface structuring 25 has an RZ value of 0.04-0.06.

[0063] In the exemplary embodiment according to the accompanying Fig. 5 to 7 only the inner sealing section 71 of the main valve seat 70 has the surface structuring 25.

[0064] In the embodiment according to the Fig. 5 and Fig. The surface structuring 25 comprises a radial pattern, with the grooves 26 extending radially. The grooves 26 are arranged in the sealing section 71 at a distance of approximately 0.05 mm.

[0065] The difference between the one in the Fig. 5 and Fig. 6 illustrated embodiment and the further training according to the Fig. 7 and Fig. 8 lies in the design of the surface structuring 25.

[0066] Surface structuring 25 is covered in the further training according to Fig. 8 formed by grooves 26 arranged in a cross-line pattern, wherein immediately adjacent grooves 26 are arranged at a distance of approximately 0.05 mm and have a depth and width of approximately 0.05 mm.

[0067] Again, with reference to the Fig. Figure 3 shows that the inner sealing sections 61, 71 can interact to seal in the closed position. The surface structuring 25 allows leakage between the inner sealing sections 61, 71.

[0068] The sealing sections 61, 71 thus act as a throttle, thereby relieving the outer sealing sections 64, 74 and preventing the main valve spool 60 from sticking to the main valve seat 70. The surface structuring 25 also ensures that the flow in the inner sealing section 61, 71 remains laminar for a longer period, which promotes a smooth characteristic curve.

[0069] The outer sealing sections 64, 74 of the main valve slide 60 and the main valve seat 70 are in essentially full-surface sealing contact in the closed position, see Fig. 2.

[0070] Fig. It can also be seen from Figure 1 that the valve housing 10 comprises a first wall section 31, a second wall section 32 and a third wall section 33.

[0071] In the control valve chamber 20 of the control valve 40, a first control valve seat 21 and a second control valve seat 22 are arranged. The first control valve seat 21 and the second control valve seat 22 are arranged on opposite sides in the valve housing 10, or more precisely in the control valve chamber 20, along the longitudinal axis L.

[0072] How in particular Fig. Figure 1 shows that the first control valve seat 21 is arranged in a first wall section 31 and the second control valve seat 22 is arranged in a second wall section 32.

[0073] Furthermore, the third wall section 33 can be provided, wherein the second wall section 32 is arranged in the longitudinal axis L between the first wall section 31 and the third wall section 33.

[0074] The first wall section 31 and the second wall section 32 define the control valve chamber 20 in the longitudinal axis L.

[0075] The second wall section 32 and the third wall section 33 define the main valve chamber 50 in the longitudinal axis L.

[0076] The third wall section 33 can be, as in the Fig. As shown in Figure 5, the third wall section 33 is formed by a housing base part 18, which can be pressed in. Adjustment devices or spacers can be provided to define the position of the third wall section 33 in the longitudinal axis L, as indicated in the figures.

[0077] The valve housing 10 – or more precisely, the third wall section 33 – can have an opening, preferably arranged coaxially with the main valve spool 60, which can form the at least one inlet of the pressure regulating valve 1. Furthermore, the third wall section 33 can have the main valve seat 70 described above, with the at least one sealing section 71, 74.

[0078] The control valve chamber 20 is connected to the at least one inlet by means of a first through-channel 11. Furthermore, the control valve chamber 20 is connected to the at least one outlet by means of a second through-channel 12, allowing the fluid to flow into the control valve chamber 20 through the at least one inlet and the first through-channel 11, and to flow out through the second through-channel 12 to the at least one outlet.

[0079] The first wall section 31 comprises the second passage channel 12, the first control valve seat 21 and preferably a passage bore 15 which will be described in detail later.

[0080] The first control valve seat 21 - see also Fig. 1 - has a first control valve seat collar 23. The first control valve seat collar 23 can be V-shaped and projects into the control valve chamber 20.

[0081] The second wall section 32 comprises the first passage channel 11 and the second control valve seat 22. The second wall section 32 can include an insertion sleeve 34, wherein preferably the second wall section 32 has a dome designed as a sleeve section into which the insertion sleeve 34 is inserted or pressed.

[0082] The insertion sleeve 34 preferably has the first through-channel 11 and the second control valve seat 22. When pressing in the insertion sleeve 34, the position of the second control valve seat 22 in the valve housing 10 can be precisely adjusted along the longitudinal axis L.

[0083] The second control valve seat 22 - see also Fig. 2 - has a second control valve seat collar 24. The second control valve seat collar 24 can be V-shaped and projects into the control valve chamber 20.

[0084] Furthermore, the pressure regulating valve 1 has an energizable actuating device 80 for actuating the control valve 40, wherein the energizable actuating device 80 - as in the illustrated embodiment - can preferably be formed by an electromagnetic actuator.

[0085] The actuating device 80 can be housed in an actuator housing 81, wherein the actuating device 80 further comprises an excitation coil 82, an armature 83 and a return spring 85. The armature 83 can be moved along a longitudinal axis L against a spring force of the return spring 85 in a known manner when the excitation coil 82 is energized.

[0086] The actuator housing 81 has a receiving area 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 81, for example by a positive, force-fit and / or material-fit connection.

[0087] Furthermore, the pressure regulating valve 1 has a plunger 90, wherein the plunger 90 can be moved along the longitudinal axis L by the actuating device 80. For this purpose, the plunger 90 is preferably connected to the armature 83 and can also be – as in the Fig. 1 is shown - held movably mounted on the actuator housing 81 along the longitudinal axis L by means of bearing elements 87.

[0088] The plunger 90 protrudes from the actuator housing 81 into the valve housing 10. In particular, how Fig. 1 can be removed, a first free end 91 of the plunger 90 protrudes into the control valve chamber 20.

[0089] Furthermore, in particular the Fig. It can be deduced from Figure 1 that the plunger 90 has a pressure equalization bore 95 through which fluid can flow along the longitudinal axis L of the plunger 90. Consequently, the fluid can flow from the first free end 91 through the plunger 90 into a pressure equalization chamber 86 opposite the armature 83, thereby enabling pressure equalization and allowing the pressure control valve 1 to be pressure-balanced.

[0090] The plunger 90 also has a control valve seal 43 on the control valve 40.

[0091] The control valve seal 43 is arranged on the plunger 90, preferably adjacent to the free end 91, and can, for example, be configured as shown in Fig. As shown in Figure 1, the control valve seal 43 is attached to the plunger 90 by means of a retaining ring 98. Preferably, the control valve seal 43 is attached to the plunger 90 in a fluid-tight manner.

[0092] The control valve seal 43 is disc-shaped and can, for example, comprise or be a metal disc.

[0093] The control valve seal 43 comprises a first sealing surface 41 and a second sealing surface 42, which are arranged on opposite sides of the control valve seal 43 in the longitudinal axis L.

[0094] In an unactuated state of the actuating device 80 according to the Fig. 1 The control valve seal 43 is arranged in a first position by means of the return spring 85.

[0095] In this first position of the control valve seal 43, the fluid from the control valve chamber 20 cannot flow through the second passage 12 towards the at least one outlet. In other words, the control valve chamber 20 is closed on the outlet side in this first position.

[0096] In the actuating state of the actuator 80, the excitation coil 82 of the actuator is energized, and the control valve seal 43 is moved from the first control valve seat 21 towards the second control valve seat 22. In the second position, the control valve seal 43 comes into contact with the second control valve seat 22, and the second sealing surface 42 acts as a seal against the second control valve seat 22 to close the first passage 11. This prevents the fluid from flowing from the at least one inlet into the control valve chamber 20.

[0097] Again, with reference to Fig. 1 can be seen that on the side of the first wall section 31 facing away from the control valve chamber 20 a failsafe seal 35 is arranged, which is held under preload against the first wall section 31 and thereby seals against a failsafe seat 36 of the through bore 15.

[0098] The failsafe seal 35 can be designed as a disc-shaped flat spring element and can furthermore be arranged between the first wall section 31 and the actuator housing 81.

[0099] The preload of the failsafe seal 35 can be achieved by a failsafe spring 37.

[0100] Furthermore, the Fig. As can be seen from Figure 1, the failsafe seat 36 can be formed by at least one annular projection. In the illustrated embodiment, the failsafe seat 36 is formed by two projections that are coaxial around the longitudinal axis L.

[0101] The through-bore 15 is arranged in the first wall section 31 such that the control valve seal 43 cannot seal against the through-bore 15. In the event of a power failure or when the actuating device 80 is de-energized, the fluid can flow from the control valve chamber 20 through the through-bore 15 to the at least one outlet, contrary to the sealing effect of the failsafe seal 35. This ensures that, for example, the vehicle can continue to operate with a specific damping characteristic even in the event of a power failure. Reference symbol list 1 pressure regulating valve 10 Valve housings 11 first passage channel 12 second passage channel 15 through-hole 18 Housing base part 20 Control valve room 21 first control valve seat 22 second control valve seat 23 first control valve seat collar 24 second control valve seat collar 25 Surface texturing 26 groove 31 first wall section 32 second wall section 33 third wall section 34 Insert socket 35 Failsafe seal 36 failsafe seats 37 Failsafe spring 40 Control valve 41 first sealing surface 42 second sealing surface 43 Control valve seal 50 Main valve room 55 Main valve spring 60 main valve slides 61 inner sealing section 62 Sealing collars 63 sealing surface of 61 64 outer sealing section 65 Sealing collar 66 sealing surface of 64 68 Passage 70 Main valve seat 71 inner sealing section 72 sealing collars 73 sealing surface of 71 74 outer sealing section 75 Sealing collar 76 sealing surface of 74 80 Actuating device 81 actuator housings 82 Excitation coil 83 anchors 85 Return spring 86 Pressure equalization chamber 87 Bearing element 90 pestles 91 Free End 95 Pressure equalization bore 98 retaining ring D1 first diameter of 61 D2 first diameter of 71 D1' second diameter of 64 D2' second diameter of 74 L Longitudinal axis QUOTES INCLUDED IN THE DESCRIPTION

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

[0000] DE 10 2023 112 797

[0004]

Claims

[1] Pressure regulating valve (1) for controlling or regulating the pressure of a fluid, comprising - a valve housing (10) with at least one pressure-side inlet and with at least one outlet, wherein a main valve chamber (50) and a control valve chamber (20) are arranged between the at least one inlet and the at least one outlet, and - an electromagnetic actuating device (80) for actuating a control valve (40) arranged in the control valve chamber (20), - wherein a main valve slide (60) movable in a longitudinal axis (L) is arranged in the main valve chamber (50), which can be arranged in an open position and a closed position, - wherein in the closed position at least one sealing section (61, 64) of the main valve slide (60) interacts sealingly with at least one sealing section (71, 74) of a main valve seat (70), characterized bythat the main valve spool (60) and / or main valve seat (70) has or has a surface structuring (25) in at least one of the sealing sections (61, 64, 71, 74). [2] Pressure regulating valve (1) according to one of the preceding claims, characterized by that the sealing section(s) (61, 64, 71, 74) is or are arranged on at least one sealing collar (62, 65, 72, 75). [3] Pressure regulating valve (1) according to one of the preceding claims, characterized by , that the sealing collar (62, 65, 72, 75) has a sealing surface (63, 66, 73, 76) at its free end which can act in a sealing manner with the main valve slide (60) and / or the main valve seat (70). [4] Pressure regulating valve (1) according to one of the preceding claims, characterized by , that surface structuring (25) extends completely over the sealing surface (63, 66, 73, 76). [5] Pressure regulating valve (1) according to one of the preceding claims, characterized by, that the main valve spool (60) and the main valve seat (70) have an inner sealing section (61, 71) and an outer sealing section (64, 74). [6] Pressure regulating valve (1) according to one of the preceding claims, characterized by , that in the closed position in the inner sealing section (61, 71) the surface structuring (25) is arranged to provide a leakage path on the main valve slide (60) and / or the main valve seat (70). [7] Pressure regulating valve (1) according to one of the preceding claims, characterized by , that in the closed position in the outer sealing section (64, 74) the main valve slide (60) and the main valve seat (70) lie on top of each other in a surface sealing manner. [8] Pressure regulating valve (1) according to one of the preceding claims, characterized by , that the surface structuring (25) comprises a multitude of grooves (26). [9] Pressure regulating valve (1) according to one of the preceding claims, characterized by, that adjacent grooves (26) have a distance between 0.025 and 0.1mm, preferably 0.05±0.025mm. [10] Pressure regulating valve (1) according to one of the preceding claims, characterized by , that a surface structuring has an RZ value of 0.04 - 0.

06. [11] Pressure regulating valve (1) according to any of the preceding claims, characterized by , that the surface texturing (25) is a laser texturing. [12] Pressure regulating valve (1) according to one of the preceding claims, characterized by , that the surface structuring (25) includes a stripe and / or a cross pattern. [13] Pressure regulating valve (1) according to one of the preceding claims, characterized by , that the main valve slide (60) is biased into the closed position by a main valve spring (55). [14] Pressure regulating valve (1) according to one of the preceding claims, characterized by, that the control valve chamber (20) is fluidically connected to the main valve chamber (50) and the at least one inlet via a first passage channel (11) and to the outlet via a second passage channel (12). [15] Pressure regulating valve (1) according to any of the preceding claims, characterized by , that a plunger (90) can move a control valve seal (43) of the control valve (40) along the longitudinal axis (L) between a first position and a second position by means of the energizable actuating device (80), and the control valve seal (43) in the first position and / or a second position is in sealing contact with a control valve seat (21, 22). [16] Pressure regulating valve (1) according to one of the preceding claims, characterized by , that the actuating device (80) is pressure balanced. [17] Vibration damper with a pressure control valve (1) according to one of the preceding claims.

Images