Damping valve device for shock absorber of motor vehicle

Abstract

The invention relates to a damping valve device (54a, 54b, 54c) for a shock absorber (10) of a motor vehicle, comprising a main valve (68) having a main piston (76; 120) which connects the main control chamber (82; 118) and a pre-control chamber (84; 122) are separated from each other, and wherein the main control chamber (82; 118) and a pre-control chamber (84; the main piston (76, 120) and the main piston (76, 120) are fluidically connected to each other via a flow passage opening (86, 136), the main valve (68) has a main valve seat (90), a spring pack (77) is mounted on the main piston (76, 120), the spring pack (77) bears against the main valve seat (90) in the closed position of the main valve (68), and the spring pack (77) comprises at least two or more spring pads (106, 108).

Description

Technical Field

[0001] The invention relates to a damping valve device for a shock absorber of a motor vehicle, wherein the damping valve device has a main valve and a pilot valve. Background Art

[0002] DE 10 2020 215 480 A1 discloses a shock absorber having a damping valve arrangement, wherein the damping valve arrangement has a main valve and a pilot valve adjustable by a magnetic winding. In particular, during dynamic operation of the shock absorber, the behavior of the damping valve may be unstable when opening and closing the main valve. In addition, acoustic problems may occur during the switching of the main valve. Summary of the invention

[0003] It is therefore an object of the present invention to provide a damping valve device for a shock absorber which has particularly soft characteristics while having stable properties and which can be produced cost-effectively.

[0004] This object is achieved according to the invention by a damping valve arrangement having the features of the independent device claim 1. Advantageous developments are revealed in the dependent claims.

[0005] According to a first aspect, a damping valve device for a shock absorber of a motor vehicle comprises a main valve having a main piston, which separates a main control chamber and a pre-control chamber from each other. The main valve comprises a main valve seat, wherein a spring assembly is mounted on the main piston and, in the closed position of the main valve, rests on the main valve seat, wherein the spring assembly comprises at least two or more spring washers.

[0006] Arranging the spring assembly on the main piston provides damping when opening and closing the main piston, thereby minimizing the generation of noise. The spring assembly provides the advantage that, in particular in the case of dynamic loads, the main valve can already be opened in a soft manner, i.e., the fluid flow can flow between the main piston and the main valve seat without the main piston being displaced. In addition, the spring assembly provides compensation for unevenness on the end side of the main piston, which, without the spring assembly, would have to interact with the valve seat and form a fluid-tight closure.

[0007] The spring washer, in particular the radially outwardly directed region of the spring washer, is preferably elastically deformable. For example, the spring washers have different or identical stiffnesses. The spring washers are preferably arranged parallel to and coaxially with each other, and in particular abut against each other. The spring washer is in particular disc-shaped, and preferably abuts against the main piston with its radially inwardly directed end. The spring washer is preferably fixed to the main piston with its radially inwardly directed end, in particular in a fixed position. One of the spring washers preferably abuts against the valve seat in the closed position of the main valve. The spring washer is particularly used to compensate for uneven portions in the main valve seat and in the end face of the main piston, and to improve the dynamic response characteristics of the main valve, by allowing the fluid to flow through the main valve even in the case of soft characteristics.

[0008] The damping valve device is, for example, a pressure limiting valve, which can preferably be directly controlled or pre-controlled. The main valve with the main piston is preferably designed to close and open the damping valve device, in particular the pressure limiting valve. The main piston can preferably be moved axially by means of the magnetic core and / or the hydraulic pressure present in the pre-control chamber.

[0009] The damping valve device constructed as a pre-control pressure-limiting valve preferably includes, in addition to the main valve, a pilot valve and a connecting channel, wherein the pilot valve has a pilot working chamber and a slider arranged in the pilot working chamber, the slider being able to move axially with the aid of a magnetic core, and the connecting channel being arranged between the pre-control chamber and the pilot working chamber and connecting the two to each other in terms of fluid technology.

[0010] The damping valve device is arranged, for example, in a shock absorber for a motor vehicle. The shock absorber is, for example, a single-tube shock absorber or a multi-tube shock absorber, such as a twin-tube shock absorber. The shock absorber comprises, for example, an outer tube, which forms the outer surface of the shock absorber, in particular a housing. Inside the outer tube, an inner tube is arranged coaxially with the outer tube, which inner tube is also referred to as a damping tube. A compensation space is formed between the outer tube and the inner tube, which is preferably at least partially filled with a hydraulic fluid. For example, the compensation space is partially filled with a gas.

[0011] Inside the inner tube, a working piston connected to the piston rod is preferably arranged so that the working piston can move in the inner tube, wherein the inner tube is preferably configured as a guide for the working piston. For example, a damping valve device according to the present invention is arranged on the working piston. The working piston divides the inner chamber of the inner tube into a first working chamber on the piston rod side and a second working chamber away from the piston rod.

[0012] The damping valve device is, for example, at least partially arranged outside the outer tube of the shock absorber. When the damping valve device is arranged outside in this way, an intermediate tube can be optionally arranged inside the compensation space, which is coaxial with the inner tube and the outer tube and is arranged between the two. The damping valve device is, for example, mounted on the intermediate tube. The intermediate tube is preferably mounted on the inner tube in a fluid-tight manner, wherein an annular space is constructed between the intermediate tube and the inner tube. The intermediate tube preferably has a flange area for mounting the damping valve device on the intermediate tube, and the flange area is preferably constructed as a fluid inlet and / or fluid outlet of the damping valve device. The outer tube preferably has an opening aligned with the flange area, which is used to accommodate the damping valve device so that the damping valve device is connected to the compensation space in terms of fluid technology. For example, the shock absorber has another damping valve device, which is, for example, also arranged outside the outer tube. Preferably, the other damping valve device is connected to the inner tube, especially to the working chamber away from the piston rod, in terms of fluid technology by means of an adapter installed inside the inner tube. These damping valve devices are preferably constructed identically.

[0013] The shock absorber preferably has a closure assembly which seals the interior of the outer tube fluidically on the piston rod side. Opposite the closure assembly, the interior of the outer tube is fluidically sealed at the end remote from the piston rod, preferably by means of a bottom part. In particular, a bottom valve is arranged on the bottom part, which is mounted at the end of the inner tube remote from the piston rod.

[0014] The damping valve device comprises a preferably cylindrical damping valve housing having a substantially tubular tube part and a housing upper part mounted on the tube part. The housing upper part has, for example, a connection area with one or more connection contacts for supplying current to the damping valve device. Preferably, the connection contacts for supplying current are connected to the drive unit. The housing upper part has, for example, a cylindrical cover section, to which a hollow cylindrical section is connected, which hollow cylindrical section has, for example, a smaller diameter.

[0015] The damping valve device preferably has a drive device configured as an electromagnet, in particular a winding having a plurality of coils made of an electrically conductive wire. The winding is preferably arranged inside the housing of the damping valve device and comprises, for example, a winding frame on which the coils of the winding are wound. Preferably, the winding at least partially or completely surrounds a magnetic core chamber, which extends centrally in the axial direction. A magnetic core is preferably supported axially movably inside the magnetic core chamber. The magnetic core is preferably slidably mounted inside the magnetic core chamber in the axial direction and, for example, comprises a central magnetic core rod, which is, for example, tubular and extends centrally in the axial direction through the magnetic core chamber. The magnetic core chamber is preferably delimited by an at least partially hollow cylindrical pole tube, which preferably serves as a guide for the magnetic core.

[0016] The damping valve arrangement preferably comprises a main valve and an optional pilot valve, and in particular a valve inlet for introducing hydraulic fluid into the damping valve arrangement, and a valve outlet for discharging hydraulic fluid from the damping valve arrangement. The pilot valve is preferably arranged downstream of the main valve. In particular, the damping valve arrangement allows hydraulic fluid to pass only in one direction.

[0017] The main valve preferably comprises a main piston, which is arranged axially movably inside the main working chamber. The main valve optionally comprises a housing part, which at least partially delimits the main working chamber and constitutes an axial guide for the main piston. The main piston is preferably arranged so that the main piston separates the main control chamber from the pre-control chamber, wherein the main piston optionally has a flow through hole, which extends through the main piston and constructs a fluid connection between the main control chamber and the pre-control chamber. Optionally, the pre-control chamber is fluidically connected to the first or second working chamber of the shock absorber via the flow through hole. For example, the main piston is constructed so that the end face of the main piston facing the main control chamber (the end face is applied with the hydraulic pressure of the main control chamber) is larger than the end face of the main piston facing the pre-control chamber (the end face is applied with the hydraulic pressure of the pre-control chamber).

[0018] During the operation of the damping valve device, in particular the pre-controlled or directly controlled pressure limiting valve, the hydraulic fluid flows into the main control chamber through the valve inlet, wherein the main piston is exerted with an opening force by the pressure in the main control chamber and moves axially in the opening direction. At this time, the main piston is lifted from the main valve seat and the hydraulic fluid flows to the valve outlet through the main flow channel. At the same time, the branch flow of the hydraulic fluid passes through the flow through hole in the main piston, flows to the pre-control chamber, and exerts a closing force on the main piston in the direction of the main valve seat. The opening width of the main valve, in particular the cross section of the main flow channel, is determined by the closing force, and the damping force of the damping valve device is determined by the cross section.

[0019] In a pilot-controlled pressure-limiting valve, the closing force is preferably determined by the pressure present in the pilot-control chamber. The pressure in the pilot-control chamber is regulated in particular by a pilot valve, wherein the hydraulic fluid flows from the pilot-control chamber via a connecting channel, which is released by the slide, into the pilot working chamber. The opening width of the connecting channel depends on the axial position of the slide, which is regulated, in particular preset, by means of a magnetic winding.

[0020] In a directly controlled pressure-limiting valve, the closing force of the main piston is preferably determined by the pressure present in the pilot control chamber and / or by means of a magnetic winding. For example, the main piston is directly connected to the magnetic core, so that the magnetic core exerts a force on the main piston that acts in the axial direction, in particular in the closing direction. A directly controlled pressure-limiting valve preferably has no pilot valve.

[0021] For an external damping valve device arranged outside the outer tube, the valve inlet is particularly configured in the flange area of ​​the damping valve device, wherein the flange area is preferably connected to the outer tube, the inner tube and / or the intermediate tube of the shock absorber. The main valve preferably has a main valve seat, which is configured, for example, on the flange area, and the main piston rests against the main valve seat in a fluid-tight manner in the closed position of the main valve. In the open position of the main valve, the main piston is lifted from the main valve seat in the axial direction, in which position a main flow channel is preferably configured between the main piston and the valve seat. The main flow channel preferably forms a fluid connection between the valve outlet and the valve inlet, in particular with the main control chamber.

[0022] On the side of the main piston away from the valve seat, a spring element is preferably mounted, which is arranged so that it exerts a spring force on the main piston in the direction of the main valve seat. The spring element is, for example, a preloaded spring having one or at least two spring washer assemblies, wherein the spring washer assembly is preferably configured in the shape of a disk, in particular as a disk spring.

[0023] The damping valve device, in particular the pilot-controlled pressure-limiting valve, preferably comprises a connecting channel for connecting the pilot-control chamber to the pilot working chamber of the pilot valve. The connecting channel is preferably configured in a housing component or in an area that is fixedly connected to the housing of the damping valve device and extends in particular centrally and in the axial direction. Preferably, the connecting channel forms a fluid inlet into the pilot valve.

[0024] The pilot valve preferably comprises a slide which is axially movable within the pilot working chamber. The slide preferably bears against the magnetic core with its end facing away from the main valve, so that the movement of the magnetic core and the slide is mechanically coupled at least in the pulling direction. The pilot valve is preferably movable into a closed position, in which the slide bears against the first valve seat of the pilot valve so that the connecting channel is completely closed by the slide, so that preferably no fluid flow can flow through the connecting channel into the pilot working chamber. The pilot valve is preferably movable into an open position, in which the slide is lifted from the first valve seat of the pilot valve, so that the connecting channel is released by the slide and a fluid flow is formed between the pilot control chamber of the main valve and the pilot working chamber.

[0025] Optionally, the pilot valve comprises a preload element, which is arranged and constructed in such a way that it exerts a preload force on the slider. The preload element is, for example, a disc spring or a helical spring, which is particularly arranged and constructed in such a way that the spring exerts a preload force on the slider in the direction of the magnetic core. Preferably, the preload element, which is constructed as a helical spring, a leaf spring and / or a disc spring, is arranged coaxially with the slider. Such a preload element increases operational safety and ensures that the slider reliably moves in the direction of the magnetic core, so that in a currentless operating state, the slider reaches a fail-safe position.

[0026] According to a first embodiment, at least one spring washer has a bypass opening. Preferably, the spring washer directly resting on the main valve seat has a bypass opening. In the following, the spring washer with at least one bypass opening is referred to as a bypass washer or a second spring washer. The bypass opening is preferably used to allow a fluid connection between the main control chamber and the valve outlet even in the closed position of the main valve. The bypass opening extends inwardly from an edge pointing radially outward in particular. The bypass opening preferably extends inwardly beyond the main valve seat in a radial direction. Preferably, the bypass opening extends over the entire axial width of the bypass washer. In the closed position of the main valve, the bypass washer rests on the main valve seat, wherein the hydraulic fluid flow flows from the main control chamber to the valve outlet through the bypass opening. For example, the bypass washer has a plurality of bypass openings, in particular identically constructed. The second spring washer, in particular the bypass washer, has, for example, 2, 4, 6, 8, 10 or more bypass openings. Preferably, the bypass openings are constructed evenly spaced apart from each other in the second spring washer. The bypass opening is in particular slit-shaped and extends in particular in the radial direction.

[0027] According to another embodiment, the spring washers each have at least one through-hole. The spring washers, in particular the bypass washers, which are directly in contact with the main valve seat, have a through-hole in addition to the bypass opening.

[0028] According to a further embodiment, the through holes are arranged aligned with one another.

[0029] According to another embodiment, the bypass opening forms a first bypass channel for the hydraulic fluid to flow through in the closed position of the main piston, wherein according to another embodiment, the through-holes together form a second bypass channel for the hydraulic fluid to flow through in the closed position of the main piston. These bypass channels allow a bypass flow of the hydraulic fluid in the closed position of the main valve. In the case of a faster flow rate change, the spring assembly is opened so that the bypass channel formed by the through-holes is closed.

[0030] Preferably, the number of through holes in the bypass washer corresponds to the number of bypass openings of the second spring washer. The through holes of the second spring washer are preferably circular. In particular, the through holes are identically constructed and are preferably arranged in alignment with the bypass openings in the radial direction.

[0031] According to another embodiment, the through-holes of the second spring washer are arranged radially offset relative to the bypass opening. The first spring washer has, for example, four through-holes, which are preferably configured as slits, in particular as elongated holes. In particular, the first spring washer comprises a plurality, in particular 2, 4, 6, 8, 10 or more through-holes.

[0032] According to another embodiment, the spring assembly has a first spring washer and a second spring washer, wherein in the closed position of the main valve, the second spring washer rests on the main valve seat and the second spring washer has a bypass opening and a through hole radially inward relative to the bypass opening. The through hole of the first spring washer is preferably arranged aligned with the through hole of the second spring washer, in particular arranged on the same radial length as the through hole of the second spring washer. The through hole of the first spring washer is preferably arranged radially offset relative to the bypass opening, in particular arranged radially inward.

[0033] According to another embodiment, the first spring washer is in contact with the second spring washer, and the through hole of the first spring washer is configured as a slit. This significantly simplifies the assembly of the first spring washer relative to the second spring washer. Preferably, the through hole of the first spring washer is configured as a partial circle slit, which extends in the circumferential direction of the first spring washer. Preferably, the through holes each extend on a partial circle of approximately 10° to 30°, in particular 20°.

[0034] According to another embodiment, a support washer is arranged between the spring assembly and the primary piston, the support washer spacing the spring assembly from the primary piston. The support washer preferably bears against the spring assembly and the primary piston and is used in particular to space the spring assembly from the primary piston in the axial direction. The support washer preferably defines an opening width of the spring assembly, wherein the opening width can be adjusted by correspondingly selecting the thickness of the support washer.

[0035] According to another embodiment, the support washer has a smaller diameter than the spring washer of the spring assembly. For example, the diameter of the support washer is 30% to 60% of the diameter of the spring washer. The support washer is preferably disc-shaped and arranged coaxially with the spring assembly. For example, the support washer is constructed of a material that cannot be elastically deformed. In particular, the support washer is fixed to the main piston in a fixed position. The support washer preferably has an axial thickness that is at least equal to or greater than the thickness of the spring assembly. The spring assembly and / or the support washer are preferably fixedly mounted on the main piston with their radially inner end regions, preferably by means of a material-fitting, form-fitting and / or force-fitting connection.

[0036] According to another embodiment, the spring assembly is fixed on the main piston in a stationary manner. Preferably, the spring assembly is fixed in the axial and radial directions.

[0037] According to another embodiment, the spring assembly is pressed against the primary piston, in particular fixedly pressed against the primary piston. According to another embodiment, the primary piston has a recess in which the spring assembly and / or the support washer are mounted. The recess preferably extends in the radial direction and has an axial extension that corresponds to the thickness of the support washer together with the spring assembly.

[0038] According to another embodiment, a fixing ring is mounted on the primary piston, which is designed and arranged in such a way that it fixes the spring assembly and, in particular, the support disk in the axial direction. The fixing ring is preferably arranged coaxially with the spring assembly and the support disk and preferably rests with its radially inwardly directed side on the primary piston, in particular on the rod region of the primary piston. The fixing ring preferably rests on the spring assembly, in particular the bypass disk.

[0039] Preferably, the primary piston has an axially protruding rod area, on which a recess is constructed. The recess is preferably constructed in an annular shape and preferably extends a full circle around the circumference of the rod area of ​​the primary piston. In particular, a fixing ring is mounted on the rod area. Preferably, the fixing ring is mounted on the rod area in a fixed position. For example, the spring washer has a directional member, in particular, a radially inwardly protruding tab that is arranged on the inner diameter of each washer. The rod area preferably has a groove that acts together with the tab to form a fixed connection, in particular a spring-groove connection. Preferably, the spring washer is connected to the rod area by means of a fixing member, such as a rivet or a screw. It is also conceivable that the spring washer has a groove that acts together with the tab on the rod area to form a groove-spring connection.

[0040] According to another embodiment, the damping valve device includes a winding; and an axially movable magnetic core, which is at least partially arranged inside the winding; a pilot valve, which has a pilot working chamber and a slider arranged in the pilot working chamber, which can move axially with the aid of the magnetic core; and a connecting channel, which is arranged between the pre-control chamber and the pilot working chamber, and connects the two to each other in terms of fluid technology.

[0041] According to another embodiment, the damping valve device comprises a winding and an axially movable magnet core which is arranged at least partially inside the winding, wherein the magnet core is connected to the main piston such that it exerts a closing force on the main piston.

[0042] The invention also includes a shock absorber having an aforementioned damping valve arrangement, wherein the damping valve arrangement is arranged, for example, on the working piston and / or at least partially outside the outer tube. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] The invention is explained in more detail below with reference to a number of exemplary embodiments and with reference to the accompanying drawings.

[0044] Figure 1 A schematic illustration of a vibration damper according to an exemplary embodiment is shown in a longitudinal section.

[0045] Figure 2 A schematic illustration of a damping valve arrangement according to a further exemplary embodiment is shown in a longitudinal section.

[0046] Figure 3 A longitudinal sectional view is shown according to another embodiment Figure 2 A partial schematic diagram of the main valve seat of the medium damping valve device.

[0047] Figures 4a to 4d The schematic diagrams of the spring disk of a damping valve arrangement according to one embodiment are each shown in a top view.

[0048] Figure 5 A schematic illustration of a vibration damper according to an exemplary embodiment is shown in a longitudinal section.

[0049] Figure 6 A schematic illustration of a damping valve arrangement according to a further exemplary embodiment is shown in a longitudinal section.

[0050] Figure 7 A longitudinal sectional view is shown according to another embodiment Figure 6 A partial schematic diagram of the main valve seat of the medium damping valve device.

[0051] Figure 8a and Figure 8b The schematic diagrams of the spring disk of a damping valve arrangement according to one embodiment are each shown in a top view. DETAILED DESCRIPTION

[0052] Figure 1 A shock absorber 10 is shown, wherein the shock absorber 10 is a multi-tube shock absorber, for example a twin-tube shock absorber. The shock absorber 10 has an outer tube 12, which forms the outer surface of the shock absorber 10, in particular the housing. An inner tube 14 is arranged coaxially with the outer tube inside the outer tube 12, which inner tube can also be referred to as a damping tube. A compensation space 16 is formed between the outer tube 12 and the inner tube 14, which is preferably at least partially filled with a hydraulic fluid. For example, the compensation space 16 is partially filled with a gas.

[0053] The working piston 18 connected to the piston rod 20 is arranged inside the inner tube 14 so that the working piston can move inside the inner tube 14, wherein the inner tube is preferably configured as a guide for the working piston 18. The working piston 18 has, for example, a valve device not shown. The working piston 18 divides the inner cavity of the inner tube 14 into a first working chamber 22 arranged on the piston rod side and a second working chamber 24 arranged away from the piston rod. Inside the compensation space 16, the intermediate tube 26 is arranged coaxially between the inner tube 14 and the outer tube 12.

[0054] The inner chamber of the outer tube 12 is fluidically sealed on the piston rod side by means of a closure assembly 34. Opposite the closure assembly 34, the inner chamber of the outer tube 12 is fluidically sealed on the end remote from the piston rod by means of a bottom part 36. A bottom valve 38 is arranged, for example, on the bottom part 36, which is particularly mounted on the end of the inner tube 14 remote from the piston rod. The bottom valve 38 is, for example, a non-return valve which can allow fluid to pass through in both directions or only in one direction. The second working chamber 24 is preferably fluidically connected to the compensation space 16 via the bottom valve 38. The ends of the inner tube 14 and the outer tube 12 on the piston rod side are preferably fixed to the closure assembly 34.

[0055] The central tube 26 is preferably mounted in a fluid-tight manner on the inner tube 14. An annular space 28 is formed between the central tube and the inner tube 14. At least one through-hole 30 is formed in the inner tube 14, which connects the first working chamber 22 to the annular space 28 in a fluid-tight manner.

[0056] The intermediate tube 26 has, by way of example, a flange region 32 for mounting the damping valve device 54a on the intermediate tube 26. The flange region 32 forms a receptacle for the damping valve device 54a, in particular forming a fluid inlet and / or a fluid outlet of the damping valve device 54a. The flange region 32 connects the annular space 28 to the damping valve device 54a, for example. The outer tube 12 preferably has an opening aligned with the flange region 32 for accommodating the damping valve device 54a, so that the damping valve device 54a is fluidically connected to the compensation space 16.

[0057] The shock absorber 10 comprises, for example, another damping valve device 54b, which is fluidically connected to the inner tube 14, in particular to the working chamber 24 remote from the piston rod, by means of an adapter 40 mounted inside the inner tube 14. Preferably, the outer tube 12 and the intermediate tube 26 have openings aligned with the adapter, which are used to accommodate the damping valve device 54a. The damping valve devices 54a, 54b are, for example, identically configured. For example, the damping valve devices 54a, 54b are configured as directly controlled or pre-controlled pressure limiting valves.

[0058] The piston rod 20 has, for example, an optional tension stop which, during a movement of the piston rod in the tension direction Z, is acted upon by a spring force via a spring element 42 .

[0059] Figure 2 1 and 2. An exemplary damping valve arrangement 54a, 54b is shown, which is preferably arranged as an external valve at least partially outside the outer tube 12 of the shock absorber 10. The damping valve arrangement 54a, 54b is designed, for example, as a pilot-controlled pressure-limiting valve and comprises a preferably cylindrical damping valve housing having a Figure 14 and 5. The substantially tubular tube part 45 shown in the figure and the housing upper part 44 mounted on the tube part 45. The housing upper part 44 has, for example, a connection area 46, which has one or more connection contacts for supplying current to the damping valve device 54a, 54b. Preferably, the connection contacts for power supply are connected to the drive unit. The housing upper part 44 has, for example, a cylindrical cover section 56, to which a hollow cylindrical section 58 is connected, which hollow cylindrical section has, for example, a smaller diameter.

[0060] The damping valve device 54a, 54b has, for example, a drive region 48 and a valve region 50. The drive region 48 is, for example, arranged in the upper region of the damping valve device 54a, 54b, facing the housing upper part 44, and is preferably arranged substantially above the valve region 50. The drive region 48 preferably includes a drive device configured as an electromagnetic device. The electromagnetic device includes a winding 52, which has a plurality of coils made of conductive wire. The winding 52 is preferably inside the tube part 45 and is arranged concentrically with the tube part. The winding 52 is, for example, arranged inside the hollow cylindrical section 58 of the housing upper part 44, and is particularly close to the inner wall of the housing upper part 44. The housing upper part 44 is, for example, constructed of plastic, in particular of a non-magnetic or only very small magnetic material, preferably a magnetic insulator or a material with high magnetic resistance. The winding 52, for example, includes a winding frame, on which the coils of the winding are wound. The winding 52 at least partially or completely surrounds a core chamber 60, which extends in the central axial direction. The core 62 is supported in the core chamber 60 so that it can move axially. The core 62 is preferably cylindrical and has a diameter slightly smaller than the diameter of the core chamber 60, so that the core 62 is preferably mounted slidably in the axial direction. For example, the core 62 comprises a central core rod 65, which is, for example, tubular and extends through the core chamber 60 in the central axial direction. The core chamber 60 is preferably delimited by an at least partially hollow cylindrical pole tube 64. The pole tube 64 preferably has a bottom and is, in particular, configured to be open in the direction of the valve area 50. The pole tube 64 is preferably constructed of a magnetizable or magnetic material and, for example, has a magnetic barrier that is not shown.

[0061] The winding 52 is preferably constructed and arranged in such a way that, when an electric current is applied to it, it forms a magnetic field having magnetic field lines which preferably run substantially in the axial direction in the magnetic core chamber 60. The magnetic core 62 is preferably constructed of a magnetizable or magnetic material and can be moved in the axial direction corresponding to the polarity of the magnetic field formed by means of the winding 52.

[0062] Pole tube elements are connected to the hollow cylindrical region of the pole tube 64 in the axial direction and coaxially to the hollow cylindrical region, which together form the pole tube 64, wherein the pole tube 64 is in particular designed in multiple parts, in one piece or in one piece. The pole tube 64 has an upper tubular region with an in particular constant inner diameter, which is preferably designed as a hollow cylinder and extends from the housing upper part 44 in the axial direction to beyond the magnetic core 62. The upper hollow cylindrical region is connected in the axial direction by a lower region with an enlarged diameter, wherein the outer surface of the pole tube 64 preferably extends to Figure 1 4 and at least partially bears against the tube part 45 and is fluid-tight relative to the tube part 45 via a sealing element 66. The pole tube 64 at least partially surrounds a valve region 50, which will be explained in more detail in the following description.

[0063] The valve area 50 comprises, for example, a main valve 68 and a pilot valve 70, as well as a valve inlet 72 for introducing hydraulic fluid into the damping valve devices 54a, 54b, and a valve outlet 74 for discharging hydraulic fluid from the damping valve devices 54a, 54b. During operation of the damping valve, the hydraulic fluid, in particular the pilot flow, preferably flows from the valve inlet 72 into the main valve 68, then into the pilot valve 70, and subsequently into the valve outlet 74. The main valve 68 comprises a main piston 76, which is arranged in an axially movable manner inside a main working chamber 78. The main valve 68 further comprises, for example, a housing component 80, which at least partially defines the main working chamber 78 and is configured for axially guiding the main piston 76. The main piston 76 is preferably inside the housing component 80 and is arranged concentrically with the housing component 80. The main piston 76 preferably divides the main working chamber 78 into a main control chamber 82 and a pilot control chamber 84 , wherein the main piston 76 has in particular a flow through-opening 86 which extends through the main piston 76 and forms a fluid connection between the main control chamber 82 and the pilot control chamber 84 .

[0064] The valve inlet 72 is formed in particular in a flange region 88 of the damping valve device 54a, 54b, wherein the flange region 88 can preferably be connected to the outer tube 12, the inner tube 14 and / or the intermediate tube 26 of the shock absorber 10. A main valve seat 90 is formed on the flange region 88. A spring assembly 77 is mounted on the main piston 76, which rests on the main valve seat 90 in the closed position of the main valve 68.

[0065] In the open position of the main valve 68, the main piston moves away from the main valve seat 90 in the axial direction, and the main piston 76 and the spring assembly 77 are lifted from the main valve seat 90, so that a main flow channel 92 is formed between the main piston 76 and the main valve seat 90. The main flow channel 92 forms a fluid connection between the valve inlet 72, in particular the main control chamber 82, and the valve outlet 74.

[0066] The main piston 76 has, on its surface pointing in the direction of the drive region 48, a central recess, in particular, so that the main piston 76 has a hollow cylindrical region. The recess of the main piston 76, in particular the interior of the hollow cylindrical region, preferably at least partially delimits the pilot control chamber 84. A spring element 94 is mounted on the side of the main piston 76 that faces away from the main valve seat 90, and the spring element is arranged in such a way that the spring element exerts a spring force on the main piston 76 in the direction of the main valve seat 90. The spring element 94 is, for example, a preloaded spring having at least one or two spring washer groups, wherein the spring washer group is preferably configured in the shape of a disk, in particular as a disk spring. The spring element 94 preferably extends over the entire diameter of the pilot control chamber 84, in particular to the inner wall of the housing component 80.

[0067] The spring element 94 preferably rests on a central block 96 that is fixedly connected to the housing part 80. The central block 96 is, for example, arranged in the pilot control chamber 84 and supported on the housing part 80 or fixedly connected to the housing part. In the central block 96, a connecting channel 98 is preferably configured, which is used to connect the pilot control chamber 84 with the pilot working chamber 100 of the pilot valve 70. The connecting channel 98 preferably extends through the central block 96 in the center and in the axial direction. Preferably, the connecting channel 98 forms a fluid inlet that is connected to the pilot valve 70.

[0068] The pilot valve 70 comprises, for example, a slide 102, which is arranged axially movably inside the pilot working chamber 100. The slide 102 preferably bears against the magnetic core 62 with its end remote from the main valve 68, so that the movement of the magnetic core 62 and the slide 102 is coupled at least in the movement of the magnetic core 62 toward the slide 102. The slide 102 preferably bears against the central block 96 in the closed position of the pilot valve 70 so that the connecting channel 98 is completely closed by the slide 102. In the open position of the pilot valve 70, the slide 102 is lifted from the central block 96, so that the connecting channel 98 is released by the slide 102, and a fluid flow is formed between the pilot control chamber 84 of the main valve 68 and the pilot working chamber 100. The pilot valve 70 preferably has a pilot housing part 104, which is arranged in a fixed position and, for example, bears against the housing part 80 or is fixedly connected thereto. The pilot working chamber 100 is constructed inside the pilot housing component 104, wherein the inner wall of the pilot housing component is constructed as a contact surface preferably fluid-tight with the slider 102. The pilot housing component 104 is preferably constructed as an axial guide for the slider 102. The slider 102 has, for example, a T-shaped longitudinal section, wherein the slider 102 has a first region facing the connecting channel 98, the first region having a larger cross section than the cross section of the connecting channel 98, and also has a second region 105 facing the magnetic core 62, the second region having a larger cross section than the cross section of the first region. The second region preferably extends over the entire cross section of the pilot working chamber 100.

[0069] Preferably, the slide 102 in the closed position abuts against a first valve seat, which is formed in the central block 96. The slide 102 of the pilot valve 70 preferably has at least one or more through-holes 112, which extend through the slide 102 in the axial direction and are formed to allow the hydraulic fluid to pass through the flow channel of the slide 102.

[0070] During operation of the damping valve device 54a, 54b, the hydraulic fluid flows through the valve inlet 72 into the main control chamber 82, wherein the pressure in the main control chamber 82 exerts an opening force on the main piston 76 and causes the main piston to move axially upward. At this time, the main piston 76 is lifted from the main valve seat 90, and the hydraulic fluid flows to the valve outlet 74 through the main flow channel 92. At the same time, the hydraulic fluid flows to the pilot control chamber 84 through the flow through hole 86 in the main piston 76, and exerts a closing force on the main piston in the direction of the main valve seat 90. The opening width of the main valve 68, in particular the cross section of the main flow channel 92, is determined by the closing force, and the cross section determines the damping force of the damping valve device 54a, 54b. The pressure in the pilot control chamber 84 is adjusted by the pilot valve 70, wherein the hydraulic fluid flows from the pilot control chamber 84 through the connecting channel 98 into the pilot working chamber 100, and the connecting channel is released by the slide 102. The opening width of the connecting channel 98 depends on the axial position of the slide 102, which is adjusted, in particular preset, by means of the magnetic winding 54. In the closed position of the pilot valve 70, the slide 102 preferably completely closes the connecting channel 98, so that the hydraulic pressure in the pilot control chamber 84 increases to a maximum value and closes the main valve 68, in which the main piston 76 is pressed against the main valve seat 90. In the open position of the pilot valve 70, the connecting channel 98 is at least partially released from the slide 102, so that the hydraulic flow flows through the through-opening 112 in the slide 102 and flows to the valve outlet 74 via the flow channel arranged downstream of the through-opening 112.

[0071] Figure 3 Show according to Figure 2 Detailed view of the damping valve arrangement 54a, 54b, showing the main valve seat 90. The main valve seat 90 is preferably a component which is statically mounted inside the damping valve arrangement 54a, 54b. Preferably, the main valve seat 90 is mounted on the flange area 88 or is constructed integrally with the flange area. Figure 3 , the closed position of the main valve 68 is shown, wherein the spring assembly 77 rests on the main valve seat 90. The spring assembly 77 exemplarily comprises two spring washers 106, 108, namely a first spring washer 106 and a second spring washer 108. For example, the spring washers 106, 108 are configured in a disc shape and are particularly mounted on the main piston 76 coaxially.

[0072] The second spring washer 108 is preferably arranged so that in the closed position of the main valve 68, it abuts against the main valve seat 90. The spring washers 106 and 108 are preferably mounted parallel to each other and directly against each other. The spring washers 106 and 108 are preferably constructed of elastically deformable materials. In particular, the second spring washer 108 below has a bypass opening 152. The bypass opening 152 preferably extends from the outside to the inside in a radial direction, in particular from the radially outwardly directed edge to the inside. The bypass opening 152 preferably extends inwardly beyond the main valve seat 90 in a radial direction. Preferably, the bypass opening 152 extends over the entire axial width of the second spring washer 108.

[0073] In the closed position of the main valve 68, the second spring washer 108, which is also referred to as the bypass washer 108, bears against the valve seat 90, wherein the hydraulic fluid flows through the bypass opening 152 from the main control chamber 82 to the valve outlet 74. For example, the second spring washer 108 has a plurality of bypass openings 152, which are in particular designed identically.

[0074] For example, the spring washers 106, 108 have through holes 154, 156, respectively. The second spring washer 108 has a through hole 156 in addition to the bypass opening. The through holes 154, 156 are preferably arranged aligned with each other. Preferably, the bypass opening 152 forms a first bypass channel for the hydraulic fluid to flow through in the closed position of the main piston 76, wherein the through holes 154, 156 together form a second bypass channel for the hydraulic fluid to flow through in the closed position of the main piston 76.

[0075] A support washer 110 is preferably arranged between the spring group 77 and the primary piston 76. The support washer 110 preferably rests on the first spring washer 106 and the primary piston 76. For example, the support washer 110 has a smaller diameter than the spring washers 106, 108 of the spring group 77. The support washer 110 is arranged in particular coaxially with the spring group 77 and is preferably fixed on the primary piston 76 in a fixed position. The support washer 110 preferably has a diameter that corresponds to 30% to 60% of the diameter of the spring group 77 and / or the primary piston 76. The support washer 110 preferably has an axial thickness that is at least equal to the thickness of the spring group 77 or greater than the thickness of the spring group 77. The support washer 110 preferably spaces the spring group 77 from the primary piston 76, in particular from the end side of the primary piston 76.

[0076] The spring group 77 and in particular the support washer 110 are preferably fixedly mounted with their radially inner end regions on the main piston 76, preferably by means of a material-fitting, form-fitting and / or force-fitting connection. In particular, the spring group 77 and the support washer 110 are pressed against the main piston 76. The main piston 76 preferably has a rod region 114, which forms a central axial projection relative to the end side of the main piston 76. In the rod region 114 there is a radial recess 113, in which the radial end regions of the spring group 77 and / or the support washer 110 are mounted, in particular fixed, preferably fixedly clamped. The spring group 77 and the support washer 110 are preferably fixed in the radial and axial direction inside the recess 113 in the main piston 76.

[0077] Figure 4a and Figure 4b The spring washers 106, 108 are shown in a top view. For example, the second spring washer 108 has four bypass openings 152. It is also conceivable that the second spring washer comprises a plurality, in particular 2, 4, 6, 8, 10 or more bypass openings 152, which are preferably configured to be evenly spaced apart from one another in the second spring washer 108. These bypass openings 152 are configured, for example, in the form of slits and extend in particular in the radial direction.

[0078] For example, the number of through holes 156 of the second spring washer 108 corresponds to the number of bypass openings 152. The through holes 156 of the second spring washer 108 are preferably circular. In particular, the through holes 156 are identically configured and are preferably arranged in radial alignment with the bypass openings 152. For example, the through holes 156 of the second spring washer 108 are arranged radially offset relative to the bypass openings 152.

[0079] The first spring washer 106 is Figure 4b , and it has four through holes 154 by way of example, which are preferably configured as slits, in particular as elongated holes. It is also conceivable that the first spring washer has a plurality of through holes 156, in particular 2, 4, 6, 8, 10 or more. For example, the through holes 154 of the first spring washer 106 are configured as partial circle slits, which extend in the circumferential direction of the first spring washer 106. Preferably, the through holes 154 extend on a partial circle of approximately 10° to 30°, in particular 20°. The through holes 154 of the first spring washer 106 are preferably arranged aligned with the through holes 156 of the second spring washer 108, in particular arranged on the same radial length. The through holes 154 of the first spring washer 106 are preferably arranged radially offset relative to the bypass opening 152, in particular arranged radially inwardly.

[0080] Figure 4c and Figure 4dFurther embodiments of spring washers 106 and 108 are shown, wherein the spring washers correspond largely to Figure 4a and Figure 4b The spring washers 106, 108 in the embodiment of the present invention are different in that the through hole 156 of the spring washer 108 is arranged offset relative to the bypass opening 152. For example, the through hole 156 is arranged offset by about 40° to 60°, for example, 45°, relative to the bypass opening 152. Figure 4a and Figure 4b In contrast, the spring washers 106 and 108 each have a groove which is formed on an edge pointing radially inwards. The rod region 114 of the main piston 76 preferably has a projection which interacts with the groove of the respective spring washer 106, 108 to form a groove-spring connection.

[0081] Figure 5 A vibration damper 10 is shown, which is substantially similar to Figure 1 The damping valve device 54c is arranged on the working piston 18. Figure 1 different, Figure 5 The shock absorber 10 does not have an intermediate pipe and external damping valve devices 54 a , 54 b .

[0082] Figure 6 The damping valve device 54c also comprises a drive region 48 having a winding 52 and a magnetic core 62 which is axially movable in the winding, as shown in FIG. Figure 2 The damping valve device 54c also has a valve region 50, which has a main valve 68 and a pilot valve 70. For example, the damping valve device 54c has two main valves 68a, 68b, which are each arranged on one side of the working piston 18, so that the main valve 68a or 69b is respectively effective in the pulling phase or the pushing phase of the shock absorber 10.

[0083] The working piston 18 has a fluid through-hole 116, which leads into the main control chamber 118 of the main valve 68. The main piston 120 separates the main control chamber 118 from the pre-control chamber 122 in terms of fluid technology. A main valve seat 124 is constructed on the working piston 18 or on a component fixedly connected to the working piston, against which the main piston 120 rests in the closed position of the corresponding main valve 68. The closing force acting on the main piston 120 in the direction of the main valve seat 124 is determined by the hydraulic pressure present in the pre-control chamber 122. For example, the pre-control chambers 122 of the two main valves 68a, 68b are connected to each other via a flow channel, so that preferably the same pressure exists in the pre-control chambers 122 of the main valves 68a, 68b. The pressure present in the two pre-control chambers 122 can preferably be adjusted by the pilot valve 70. The pilot valve 70 has a slide 126 which is mounted axially movable and which, in the closed position of the pilot valve 70, abuts against a first valve seat of the pilot valve 70. The pilot control chambers 122 are hydraulically connected to a pilot working chamber 132, for example, via a connecting channel 130. The flow cross section of the connecting channel 130 can be at least partially or completely closed by means of the slide 126, wherein the slide 126 abuts against a first valve seat 128 of the pilot valve 70. The movement of the slide 126 is preferably coupled to the magnetic core 62 at least in one direction of movement, and as described with reference to Figures 1 to 3 As described, the slide is moved axially by the winding 52 .

[0084] The primary piston 120 is preferably arranged movably relative to a fixed flange area 134. A flow through hole 136 is formed in the flange area 134, which connects the pilot control chamber 122 to the corresponding working chamber 22, 24 of the shock absorber 10. The flow through holes 136 are preferably connected to a check valve in each case, so that the hydraulic flow can only flow from the corresponding working chamber 22, 24 into the corresponding pilot control chamber 122, but not in the opposite direction.

[0085] When the working piston 18 moves in the thrust direction D, the hydraulic fluid flows, for example, from the working chamber 24 remote from the piston rod via the flow through hole 136 of the main valve 68b into one of the pilot control chambers 122, so that the same pressure is present in the two pilot control chambers through the hydraulic connection of the pilot control chambers 122. The discharge of the hydraulic fluid is determined by the position of the slide 126 relative to the first valve seat 128 via the pilot valve 70 and thus the set pressure in the pilot control chamber 122. Figure 5 The pilot working chamber 132 of the exemplary embodiment of is preferably fluidically connected to an outflow channel 148 , through which the hydraulic fluid can flow from the pilot working chamber 132 into the first or second working chamber 22 , 24 .

[0086] Figure 7A detailed view of the main valve seat 124 is shown, wherein a spring assembly 77 is mounted on the main piston 120, and the spring assembly 77 is connected to the main valve seat 124. Figure 3 The spring assembly 77 of FIG. 1 corresponds substantially to that of FIG. 1 , and identical elements are provided with the same reference numerals. Figure 7 The main piston 120 also has a rod region 114. A fixing ring 150 is mounted on the rod region 114, which is arranged coaxially with the spring group 77 and the support washer 110 and rests with its radially inwardly directed side against the rod region 114 of the main piston 120. The fixing ring 150 preferably rests on the spring group 77, in particular on the second spring washer 108. Preferably, the fixing ring 150 is arranged and constructed in such a way that the fixing ring fixes the spring group 77 and the support ring 110 in the axial direction.

[0087] Figure 8a and Figure 8b Show Figure 7 The spring washers 106 and 108 are substantially corresponding to Figure 4a and Figure 4b The second spring washer 108 resting against the main valve seat 124 also has a plurality of (e.g., four) bypass openings 152 and a through hole 156. The first spring washer 106 also has a plurality of through holes 154, wherein the construction and arrangement of the through holes 154, 156 and the bypass opening 152 substantially correspond to Figure 4a and Figure 4b .

[0088] Description of Reference Numerals

[0089] 10. Shock absorber

[0090] 12 outer tube

[0091] 14 Inner tube

[0092] 16 Compensation space

[0093] 18 Working piston

[0094] 20 piston rod

[0095] 22 First / piston rod side working chamber

[0096] 24 Second / working chamber away from the piston rod

[0097] 26 Intermediate pipe

[0098] 28 Ring Space

[0099] 30 through holes

[0100] 32 Flange area

[0101] 34 closed components

[0102] 36 bottom parts

[0103] 38 foot valve

[0104] 40 Adapter

[0105] 42 Spring element

[0106] 44 Shell upper part

[0107] 45 pipe parts

[0108] 46 Wiring area

[0109] 48 drive area

[0110] 50 valve area

[0111] 52 Winding

[0112] 54a, 54b, 54c Damping valve device

[0113] 56 Top cover section

[0114] 58 hollow cylindrical section

[0115] 60 core chamber

[0116] 62 core

[0117] 64 diodes

[0118] 65 magnetic core rod

[0119] 66 Sealing element

[0120] 68 Main valve

[0121] 70 pilot valve

[0122] 72 valve inlet

[0123] 74 valve outlet

[0124] 76 / 120 main piston

[0125] 77 Spring Set

[0126] 78 Main working chamber

[0127] 80 Shell parts

[0128] 82 / 118 Main control chamber

[0129] 84 / 122 Pre-control chamber

[0130] 86 / 136 Flow Through Hole

[0131] 88 / 134 flange area

[0132] 90 / 124 main valve seat

[0133] 92 Main flow channel

[0134] 94 Spring element

[0135] 96 center block

[0136] 98 / 130 connection channel

[0137] 100 / 132 pilot working chamber

[0138] 102 / 126 Slide

[0139] 104 pilot housing parts

[0140] 106 first spring washer

[0141] 108 Second spring washer / bypass washer

[0142] 110 support gasket

[0143] 112 Through hole

[0144] 113 recess

[0145] 114 Rod area of ​​main piston 76

[0146] 116 Fluid passage opening in working piston 18

[0147] 118 Main control chamber

[0148] 128 first valve seat

[0149] 136 Flow Through Holes

[0150] 138 preload element

[0151] 148 Outflow channel

[0152] 150 fixing ring

[0153] 152 bypass opening

[0154] 154 through hole of first spring washer

[0155] 156Through hole of the second spring washer

Claims

1. A damping valve device (54a, 54b, 54c) for a shock absorber (10) of a motor vehicle, comprising: A main valve (68) having a main piston (76; 120) which separates a main control chamber (82; 118) and a pilot control chamber (84; 122) from one another, in, The main control chamber (82; 118) and the pilot control chamber (84; 122) are fluidically connected to each other via a flow through-hole (86; 136). The main valve (68) has a main valve seat (90). It is characterized in that A spring assembly (77) is mounted on the main piston (76, 120) and abuts against a main valve seat (90) in a closed position of the main valve (68), wherein the spring assembly (77) includes at least two or more spring washers (106, 108).

2. The damping valve device (54a, 54b, 54c) according to claim 1, characterized in that At least one spring washer (106, 108) has a bypass opening (152).

3. The damping valve device (54a, 54b, 54c) according to any one of the preceding claims, characterized in that The spring washers (106, 108) have through holes (154, 156), respectively.

4. The damping valve device (54a, 54b, 54c) according to claim 3, characterized in that The through holes (154, 156) are arranged in alignment with each other.

5. The damping valve device (54a, 54b, 54c) according to any one of claims 2 to 4, characterized in that: The bypass opening (152) forms a first bypass channel for the hydraulic fluid to flow through in the closed position of the main piston (76; 120).

6. The damping valve device (54a, 54b, 54c) according to any one of claims 2 to 5, characterized in that The through holes (154, 156) together form a second bypass channel for allowing hydraulic fluid to flow through when the main piston (76; 120) is in the closed position.

7. The damping valve device (54c) according to any one of claims 2 to 6, characterized in that The bypass opening (152) and the through holes (154, 156) are arranged offset from each other in the radial direction.

8. The damping valve device (54a, 54b, 54c) according to any one of the preceding claims, characterized in that The spring assembly (77) has a first spring washer (106) and a second spring washer (108), wherein the second spring washer (108) abuts against the main valve seat (90) in the closed position of the main valve (68), and the second spring washer has a bypass opening (152) and a through hole (156) radially inward relative to the bypass opening.

9. The damping valve device (54a, 54b, 54c) according to claim 8, characterized in that The first spring washer (106) abuts against the second spring washer (108), and the through hole (156) of the first spring washer (106) is configured in a slit shape.

10. The damping valve arrangement (54a, 54b, 54c) according to any one of the preceding claims, characterized in that A support washer (110) is installed between the spring group (77) and the main piston (76, 120), and the support washer spaces the spring group (77) and the main piston (76, 120).

11. The damping valve device (54a, 54b, 54c) according to claim 10, characterized in that The support washer (110) has a smaller diameter than the spring washers (106, 108) of the spring assembly (77).

12. The damping valve device (54a, 54b, 54c) according to any one of the preceding claims, characterized in that The spring assembly (77) is fixed to the main piston (76, 120) in a stationary manner, in particular in the axial direction.

13. The damping valve device (54a, 54b, 54c) according to any one of the preceding claims, characterized in that The spring assembly (77) and the main piston (76, 120) are compressed.

14. The damping valve device (54a, 54b, 54c) according to any one of claims 10 to 13, characterized in that The main piston (76, 120) has a recess (113) in which a spring assembly (77) and / or a support washer (110) is mounted.

15. The damping valve device (54a, 54b, 54c) according to any one of the preceding claims, characterized in that A fixing ring (150) is mounted on the main piston (120) and is designed and arranged in such a way that it fixes the spring assembly (77) in the axial direction.

16. The damping valve arrangement (54a, 54b, 54c) according to any one of the preceding claims, comprising: Winding (52), an axially movable magnetic core (62) at least partially arranged inside the winding (52), A pilot valve (70) having a pilot working chamber (100, 132) and a slider (102; 126) arranged in the pilot working chamber (100; 132), the slider being axially movable by means of a magnetic core (62), and A connecting channel (98; 130) is arranged between the pilot control chamber (84; 122) and the pilot working chamber (100; 132) and connects the two to each other in terms of fluid technology.

17. The damping valve device (54a, 54b, 54c) according to any one of claims 1 to 15, comprising: Winding (52), An axially movable magnetic core (62) is arranged at least partially inside the winding (52), wherein: The magnetic core (62) is connected to the main piston (76, 120) so that the magnetic core applies a closing force to the main piston.

18. A shock absorber (10) for a motor vehicle, comprising: An outer tube (12), an inner tube (14) arranged coaxially with the outer tube, and a working piston (18) arranged axially movable inside the inner tube (14), the working piston dividing the inner cavity of the inner tube (14) into a working cavity (22) on the piston rod side and a working cavity (24) away from the piston rod, It is characterized in that The shock absorber has a damping valve arrangement (54a, 54b, 54c) according to any of the preceding claims.

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