WO2024022924A1

WO2024022924A1 - Damping valve device for a vibration damper

Info

Publication number: WO2024022924A1
Application number: PCT/EP2023/070079
Authority: WO
Inventors: Freddy Woenarta; Klaus Schmidt; Ole Götz; Mirco Adam
Original assignee: Thyssenkrupp Bilstein Gmbh; Thyssenkrupp Ag
Priority date: 2022-07-27
Filing date: 2023-07-19
Publication date: 2024-02-01

Abstract

The invention relates to a damping valve device (1) for a hydraulic vibration damper (2) for a vehicle, comprising: a drive region (19), a valve region (9), and a damping valve housing (3) with a tube part (4) which encloses the drive region (19) and the valve region (9), wherein the drive region (19) has a coil (8) that is designed to produce a magnetic circuit within the damping valve device (1) and interact with an armature (11), which is installed within the coil (8) in an axially movable manner, in order to move the armature (11) in the axial direction, and the armature (11) is arranged within a pole tube (7), said pole tube (7) forming a guide for the armature (11). The valve region (9) has a fluid inlet (28) and a fluid outlet (29) for admitting and discharging a hydraulic fluid into and out of the valve region (9) and a valve block (27) with a plurality of flow passages (20) for conducting the hydraulic fluid, and the valve region (9) has a control slide (17) which is movably installed relative to the valve block (27) such that the control slide can be moved between a closed position, in which the flow passages (20) are closed by the control slide (17), and an open position, in which the flow passages (20) are released. An annular chamber (30) which is filled with hydraulic fluid is delimited by the control slide (17), the pole tube (7), and the valve block, and the annular chamber (30) has at least two different outer diameters.

Description

Damping valve device for a vibration damper

The invention relates to a damping valve device for a vibration damper, particularly for motor vehicles.

Vibration dampers, in particular shock absorbers, are commonly used in motor vehicles and are mounted between a wheel suspension, in particular an axle, and the body of the vehicle in order to dampen shocks while driving and reduce vibrations. To increase driving comfort and driving safety, the damping characteristics of the vibration damper are usually adjustable. For example, this is done via a solenoid valve, via which the flow of the hydraulic fluid within the vibration damper can be adjusted and thus makes the movement of the piston of the vibration damper easier or more difficult.

Solenoid valves are, for example, arranged on the outside of the vibration damper tube and thus represent a separate module from the vibration damper tube, which takes up additional space within the vehicle. In a solenoid valve, a control slide is usually moved via a magnetic device so that flow passages for a hydraulic fluid are opened or closed. This often creates hydraulic turbulence in the outflow area, which, for example, causes areas with lower pressure and thus creates a suction that acts on the control slide. This creates, for example, a closing force that acts on the control slide, making targeted control of the control slide very difficult.

From EP2685145A2 a damping valve device is known which is attached to the outside of the vibration damper.

Proceeding from this, it is the object of the present invention to optimize the control of the damping valve device and to reduce the manufacturing costs, in particular the number and complexity of the components, the assembly time and the weight of a damping valve device of a vibration damper. This object is achieved according to the invention by a damping valve device with the features of independent device claim 1. Advantageous further training results from the dependent requirements.

According to a first aspect of the invention, a damping valve device for a hydraulic vibration damper for a vehicle, in particular a motor vehicle, comprises a drive area and a valve area. The damping valve device further comprises a damper valve housing, with a tubular part that encloses the drive region and the valve region, the drive region having a coil which is designed such that it generates a magnetic circuit within the damper valve device and with an axially movably mounted armature within the coil to move the armature in the axial direction. The anchor is arranged within a pole tube, the pole tube forming a guide for the anchor. In particular, the pole tube forms an axial guide for guiding the movement of the armature in the axial direction. The valve section has a fluid inlet and a fluid outlet for admitting and discharging a hydraulic fluid into the valve section, and a valve block having a plurality of flow passages for directing the hydraulic fluid. The valve area has a control slide which is mounted movably relative to the valve block in such a way that it can be moved between a closed position in which the flow passages are closed by the control slide and an open position in which the flow passages are free. The damping valve device has an annular space filled with hydraulic fluid, which is delimited by the control slide, the pole tube and the valve block and wherein the annular space has at least two different outer diameters. The annular space preferably has a first annular space region and a second annular space region, the first annular space region being delimited by the control slide and the second annular space region comprising flow channels formed between the valve block and the pole tube. The first and second annular spaces preferably adjoin one another directly, with the first annular space adjoining the damping valve device in the axial direction to the outside and the second annular space adjoining the axial direction inwards, in the direction of the cylinder tube of the vibration damper. The outer diameter of the annular space corresponds in particular to the inner diameter of the pole tube. The annular space is in particular designed in such a way that during operation of the damping valve device and when the damping fluid flows through the annular space, a turbulence is generated within the annular space, which applies a force to the control slide that is directed in the direction of the open position of the control slide. Optimally, the annular space is designed in such a way that during operation of the damping valve device, the hydraulic forces are balanced in the axial direction and therefore no hydraulic forces act on the control slide and it is moved exclusively or essentially by means of the coil.

According to a first embodiment, the annular space has a first annular space area with a first outer diameter and a second annular space area with a second outer diameter, the second outer diameter being larger than the first outer diameter. The second annular space area preferably adjoins the first annular space area in the direction of the fluid outlet. Preferably, the first annular space region with the first outer diameter extends at least partially or completely around the flow passages formed in the valve block. The first annular space area is in particular arranged coaxially to the area of the valve block that can be covered by the control slide.

According to a further embodiment, the first outer diameter is constant over the first annular space area and the second outer diameter is variable over the second annular space area. Preferably, the second annular space region extends over a length extending in the axial direction. Over this length, the outer diameter of the second annular space region is not constant and preferably changes continuously. The second annular space region preferably extends at least partially around the second region of the valve block in which the flow channels are formed. Preferably, the second annular space region is at least partially delimited by the flow channels, in particular formed by them.

According to a further embodiment, preferably in the open position of the control slide, the first annular space area is delimited by the control slide and the second annular space area comprises between the valve block and the pole tube trained flow channels. The maximum outside diameter of the second annular space region preferably corresponds to the outside diameter of the flow channels. In particular, the second annular space has a minimum outside diameter that is greater than or equal to the outside diameter of the first annular space region.

According to a further embodiment, the second annular space region has a maximum outside diameter that corresponds to the outside diameter of the flow channels.

According to a further embodiment, the second annular space region has a minimum outside diameter which corresponds to the first outside diameter of the first annular space region.

According to a further embodiment, the change in the outside diameter of the second annular space section between the minimum outside diameter and the maximum outside diameter corresponds to a mathematical function, preferably corresponding to a pitch circle section. In particular, the outer diameter changes continuously over the length of the second annular space section.

According to a further embodiment, the first annular space region has an inner diameter, the ratio of the outer diameter to the inner diameter being 0.7 to 0.95, in particular 0.8 to 0.9.

According to a further embodiment, the second annular space region (44) has an inner diameter, the ratio of the outer diameter to the inner diameter being 0.7 to 0.95, in particular 0.8 to 0.9.

According to a further embodiment, the ratio of the inside diameter corresponds to the maximum outside diameter of the second

Annulus area less or equal to 0.51. According to a further embodiment, the ratio of the inside diameter of the flow channels to the outside diameter of the flow channels is 0.6 to 1.1, preferably 0.7 to 1.02.

According to a further embodiment, a plurality of flow channels are formed between the pole tube and the valve block, which extend at least partially in the radial and axial directions.

The design of the annular space described above causes compensation for closing forces acting on the control slide during operation of the damping valve device, so that the control slide can be controlled precisely and easily by the magnetic forces of the coil.

The term axial direction is to be understood as meaning the direction running parallel to the axial center line of the damping valve device, in particular of the tubular part of the damping valve device. The term radial direction is understood to mean the direction orthogonal to the axial direction.

The hydraulic vibration damper preferably comprises an inner cylinder tube and an outer cylinder tube arranged coaxially therewith, which in particular forms the outer wall of the vibration damper. Within the inner cylinder tube, a piston is preferably attached to a piston rod in an axially movable manner and divides the inner cylinder tube into two working spaces. In particular, the piston has at least two fluid passages through which one working space is connected to the other working space. An annular space is preferably formed between the inner and outer cylinder tubes, with a central tube, which divides the annular space, preferably being mounted within the annular space and coaxially between the inner and outer cylinder tubes. The damping valve device is preferably fluidly connected to at least one of the working spaces of the inner cylinder tube and is preferably attached to the center tube and the outer cylinder tube of the vibration damper. The vibration damper is preferably completely or partially filled with a hydraulic fluid. The tube part is preferably designed such that it can be connected to the outer cylinder tube and in particular has a substantially constant, circular cross section. The tubular part preferably forms the outer housing wall of the damping valve device. In particular, the drive area and the valve area are arranged completely within the tube part, so that the tube part preferably extends in the axial direction beyond the drive area and/or the valve area. The valve area is preferably arranged in an area of the tube part facing the outer cylinder tube of the vibration damper, the drive area being arranged in the opposite area of the tube part facing away from the outer cylinder tube of the vibration damper. The tube part is preferably made of a magnetic or magnetizable material.

The drive area preferably comprises an electromagnet, the electromagnet having, for example, a coil with a plurality of windings which are arranged on a coil support. The coil carrier is preferably made of a plastic and in particular is essentially hollow cylindrical and arranged coaxially to the tubular part.

The coil is preferably firmly, in particular cohesively, positively and/or non-positively connected to the tubular part. For example, a clearance fit is formed between the pole tube and the coil. The coil is preferably designed and arranged such that it generates a magnetic circuit within the damping valve device. Preferably, the coil to which an electrical current is applied generates a magnetic flux which runs in a closed path within the damping valve device. The magnetic circuit includes the elements of the damping valve device through which the magnetic flux generated by the coil runs in a closed path.

The armature is arranged within the coil, preferably coaxially therewith. The armature is preferably made of a magnetic or magnetizable material and is in particular part of the magnetic circuit. The anchor preferably has a first cylindrical region, which is adjoined in the axial direction by a second cylindrical region with a smaller diameter relative to the first region. In particular, the pole tube is arranged between the armature and the coil, which is at least partially hollow cylindrical and extends coaxially to the coil, the tube part and the armature. The pole tube is preferably made of a magnetic or magnetizable material and is in particular part of the magnetic circuit. For example, the anchor is at least partially or completely wrapped with a sliding film, such as a PTFE film, which facilitates the axial movement of the anchor within the pole tube. The pole tube preferably has a hollow cylindrical region which rests at least partially on the coil, in particular the coil support, and preferably has a substantially constant cross section. In particular, the hollow cylindrical region has a substantially constant inner and/or outer diameter, in particular a constant wall thickness.

The hollow cylindrical region preferably forms the guide, in particular axial guide, of the armature, so that the armature is mounted within the pole tube so that it can move in the axial direction. The hollow cylindrical region of the pole tube preferably extends in the axial direction, preferably in the direction of the upper part of the housing, over the coil and, in particular, has a base at its end, which completely closes the end of the pole tube. A cylindrical armature space is preferably formed within the hollow cylindrical region, in which the armature and hydraulic fluid are arranged. Adjoining the hollow cylindrical region of the pole tube in the axial direction towards the valve region is a valve-side region which has at least one or a plurality of expansions of the inner diameter and/or the outer diameter. The valve-side region of the pole tube is preferably funnel-shaped, with the funnel expanding in the direction of the valve. The pole tube, in particular the valve-side region of the pole tube, is preferably firmly connected to the tube part, in particular in a form-fitting, non-positive and/or material-locking manner. The pole tube extends, for example, in the axial direction at least partially or completely along the coil, the valve slide and the valve block.

The pole tube, in particular the valve-side area, preferably encloses the valve block and/or the control slide, in particular circumferentially. Preferably there is a with between the valve block and/or the control slide and the pole tube Hydraulic fluid-filled annular space is formed. The control slide is preferably mounted so that it can move in the axial direction relative to the valve block and the pole tube and is arranged coaxially with the tube part and the pole tube. The control slide is preferably in operative connection with the armature, so that the movement of the armature is at least partially or completely coupled to the control slide. The control slide preferably has an axial end face which points in the direction of the armature and against which the armature rests, so that a movement of the armature is transmitted to the control slide.

The valve block is preferably arranged coaxially with the pole tube and in particular has a cavity which is fluidly connected to the fluid inlet/fluid outlet, so that hydraulic fluid flows into the valve block. A fluid space is preferably formed between the valve block and the pole tube, in which the hydraulic fluid can flow. The valve block is, for example, funnel-shaped and has, for example, a cylindrical region facing the drive unit, which is preferably arranged coaxially to the control slide and has a substantially constant cross section. The control slide preferably surrounds the valve block circumferentially and is mounted so that it can move in the axial direction relative to the valve block. At the area facing away from the drive unit, the valve block has, for example, a funnel-shaped, radial expansion. The valve block is in particular stationary relative to the axially movable control slide and, for example, firmly connected to the pole tube. Preferably, the valve block is at least partially or completely enclosed circumferentially and in the axial direction by the pole tube element, with the control slide being arranged between the drive-side region of the valve block and the pole tube element.

Flow passages, in particular passage openings, are preferably formed within the valve block, through which the hydraulic fluid can flow, in particular from the fluid inlet to the fluid outlet. The flow passages are preferably arranged in the cylindrical area of the valve block enclosed by the control slide. The control slide is mounted so that it can move axially in such a way that it completely opens the flow passages in an open position of the damping valve device and in a closed position of the damping valve device the flow passages are completely closed. The control slide is mounted in such a way that it can preferably be moved into a variety of intermediate positions in which the flow passages are partially closed. The control slide is preferably biased towards the open position by means of a spring. The spring is preferably arranged between the control slide and the valve block and preferably acts on the control slide with a force acting axially in the direction of the drive region.

For example, the valve block has a first cylindrical region and an adjoining second cylindrical region, the second region having a larger diameter than the first region and the flow channels being formed in the second region. The flow passages are arranged in particular in the first area. The pole tube preferably rests on the second region of the valve block. For example, the pole tube rests exclusively on the second region of the valve block and is in particular spaced from the first region. The second region has, for example, a circumferential surface pointing radially outwards and a shoulder surface pointing axially in the direction of the first region. The shoulder surface preferably rests on the pole tube. The first region of the valve block is in particular arranged coaxially to the control slide. The first area can preferably be completely or partially enclosed by the control slide. The flow passages are preferably circular bores in the valve block, in particular the wall of the first region of the valve block.

The flow channels are preferably formed in the second region of the valve block and are in particular designed to be open in the direction of the pole tube, so that the flow channels are each formed between the inner surface of the pole tube and the radially outward-facing surface of the valve block. The flow channels preferably extend from the shoulder surface to the peripheral surface and in particular represent recesses, preferably bulges, in the shoulder surface and the peripheral surface. The direction of extension of the flow channels preferably has an axial and a radial component. This enables optimal flow of the damping fluid. For example, the flow channels preferably extend continuously at an angle of 10° to 80°, in particular 20° to 60°, preferably 30° to 50° to the axial. For example, the number of flow channels corresponds to the number of flow passages. It is also conceivable that more flow channels are provided as flow passages or more flow passages than flow channels. For example, at least one flow channel is arranged in alignment with one of the flow passages. Preferably, each flow channel is arranged in alignment with a respective flow passage. For example, at least two flow passages are arranged at different height levels. The arrangement of the flow passages at different height levels causes the flow passages to be opened/closed by the control slide in a predetermined order. This enables optimal distribution of the transverse force acting on the control slide during the switching process.

Preferably, the flow passages are arranged evenly spaced apart from one another in the circumferential direction of the first region of the valve block. For example, at least two flow passages directly adjacent to one another are arranged at different height levels. In particular, all flow passages are arranged at different height levels. The height level is preferably understood to mean the distance between the center of the respective flow passage and a specific cross-sectional plane of the damping valve device. In particular, this is to be understood as the axial distance of the center of the respective flow passage to the shoulder surface of the second region of the valve block.

In particular, at least two flow passages are arranged at the same height level. This achieves a simultaneous opening of the flow passages by means of the control slide and optimizes the distribution of the forces acting on the control slide during the switching process of the damping valve. For example, circumferentially opposite flow passages are arranged on the valve block at the same height level. The valve block preferably has four, six, eight or ten flow passages which are arranged circumferentially around the first region of the valve block and in particular adjacent ones Flow passages are arranged offset from one another at an angle of 90°, 60°, 45° or 36° around the central axis of the valve block. Opposite flow passages are arranged 180° offset from each other. Simultaneous opening/closing of opposite flow passages optimizes the distribution of the forces acting on the control slide during the switching process of the damping valve. Alternatively, opposite flow passages are arranged circumferentially on the valve block at different height levels.

For example, circumferentially opposite flow passages on the valve block have a height difference that is less than the height difference to the directly adjacent flow passages. This causes opposing flow passages to open/close immediately one after the other. For example, at least two flow passages have different diameters. According to a further embodiment, at least two flow passages have different geometries. All flow passages preferably have different diameters and/or geometries. This enables optimal adjustment of the forces acting on the control slide during the switching process of the damping valve.

The pole tube is preferably formed in one piece. “One-piece” is preferably understood to be formed from one piece, in particular a solid block, whereby “one-piece” includes a firm connection between several parts, for example by means of positive connection, frictional connection and/or material connection. A pole tube designed in one piece or in one piece considerably simplifies the assembly of the damping valve device. Complex assembly of the pole tube is no longer necessary. In addition, fasteners for assembling a multi-part pole tube are dispensed with, which leads to weight savings. A further weight saving is achieved in that the tubular part is part of the magnetic circuit, since in this way at least part of the coil carrier, in particular the outer jacket, can be dispensed with. For example, the pole tube is produced by a machining process, in particular turning or milling. In particular, the pole tube is manufactured by casting or cold forming. The damping valve device has, for example, a sealing element which is arranged in a chamber, the chamber being formed between the pole tube and the tube part and additionally the coil and/or a support. The chamber is preferably closed by the pole tube and the tube part, as well as the coil and/or the support element. The chamber is preferably designed to accommodate a sealing element, in particular a sealing ring. The chamber is preferably designed in the shape of a circular ring and in particular has a rectangular cross section. The chamber is in particular completely closed and delimited by the pole tube, the tube part and the coil and/or the support ring. A sealing element, which is preferably a sealing ring, is mounted in the chamber. The sealing element preferably rests at least on the pole tube and the tube part and serves in particular for sealing, so that no hydraulic fluid passes from the valve area into the coil. In particular, the sealing element also rests on a shoulder of the pole tube.

A chamber for receiving the sealing element formed between the pole tube and the tube part and in addition to the coil and/or a support ring enables the sealing element to be easily mounted on the pole tube. In particular, damage to a sealing element designed as a sealing ring is avoided, since this can largely be mounted in an unstressed state.

For example, the sealing element is designed as an O-ring. The sealing element is preferably made of a plastic, in particular an elastomer. The sealing element is in particular annular and preferably has a round, in particular circular, cross section. Preferably, the cross-sectional diameter of the sealing ring is larger than the cross-sectional width of the chamber, so that it preferably rests on at least three inner surfaces of the chamber.

In particular, the pole tube has a radial shoulder that adjoins the chamber. Preferably, the radial shoulder represents a radial extension of the pole tube relative to a region of the pole tube directly adjacent in the direction of the upper housing part. Preferably, the pole tube has a plurality of different ones Outer diameters, the outer diameter of the pole tube reducing in particular from the chamber towards the upper part of the housing. The outside diameter of the pole tube within the chamber is preferably greater than or equal to the outside diameter of the region of the pole tube extending from the chamber towards the upper part of the housing. This makes it easier to slide the sealing ring onto the pole tube.

In the axial direction from the drive region towards the valve region, the pole tube preferably has a first outer diameter which is arranged within the coil. This is followed, for example, by a second outer diameter which is larger than the first outer diameter, so that a shoulder, in particular an axial end face, is formed which points in the direction of the upper housing part and against which the coil preferably rests at least partially. The second outside diameter is preferably spaced from the inside diameter of the tube part in such a way that the chamber is formed between the pole tube and the tube part. The second outside diameter is preferably followed by a third outside diameter of the pole tube, which is larger than the first and the second outside diameter and preferably essentially corresponds to the inside diameter of the tube part, so that the pole tube with the third outside diameter rests on the tube part. An axial end face is preferably formed between the second and the third outer diameter, which faces in the direction of the upper housing part and delimits the chamber.

For example, the coil has an axially extending projection which adjoins the chamber. The coil preferably has a receptacle to which the windings and the coil support are firmly connected. In particular, the receptacle is made of a plastic, which is preferably applied at least partially or completely around the windings and the coil support by means of injection molding. The plastic material is preferably sprayed onto the windings and the coil support. The receptacle preferably forms the lateral surface of the coil pointing in the direction of the tubular part and lies in particular against the tubular part. The receptacle is, for example, formed in one piece or in one piece with the upper housing part. Preferably the recording has a clearance fit or is fixed with the Pipe part connected, in particular non-positively, cohesively and / or positively. The coil preferably has a projection which runs in the axial direction, in particular along the inner wall of the tube part, which extends between the tube part and the pole part and adjoins the chamber. The projection is preferably made of a plastic. The projection is preferably formed in the receptacle or the bobbin of the coil. The end face of the projection pointing in the valve direction preferably forms a boundary of the chamber. The pole tube and the tube part are preferably connected to one another via a positive connection, in particular via a bayonet lock. The positive connection has, for example, at least one axial recess formed in the pole tube, which opens into the chamber. The positive connection is in particular a bayonet connection. For example, the pole tube has a plurality of recesses, which are particularly hook-shaped. Each recess includes, for example, an area that extends in particular in the axial direction and an area that adjoins this area and extends in the radial direction. A radial constriction of the tubular part preferably engages in the recess. The recesses are preferably radial depressions which are formed in the outer surface of the pole tube which lies against the tube part. The recesses preferably extend into the chamber and in particular form interruptions in the support surface of the sealing element. In this case, the sealing element 13 preferably has depressions and projections, the projections engaging in the recesses of the pole tube 7 and, for example, forming a positive connection.

The damping valve device has, for example, a support ring arranged separately from the coil. Preferably, the support ring rests at least partially on the coil with an outer surface. The support ring is preferably designed in the shape of a circular ring and, for example, has a rectangular cross section. In particular, the support ring 15 rests with its outer surface on the inside of the tube part and with its inner surface on the outer surface of the pole tube. The end face of the support ring pointing in the direction of the valve borders in particular on the chamber. The support ring is preferably firmly connected to the coil, the pole tube and/or the tube part. The support ring preferably forms a contact surface for the sealing element. The projection of the coil is provided, for example, as an alternative to or together with the support ring.

For example, the pole tube has a hollow cylindrical region which is arranged within the coil and the hollow cylindrical region has a recess running in the circumferential direction. The recess is preferably formed between the coil and the armature in the pole tube and is, for example, circular. Preferably, the recess extends in the circumferential direction of the pole tube completely in a closed ring around the pole tube or has interruptions. In particular, the recess extends in the radial direction from outside to inside into the pole tube. The depth of the recess is preferably less than the wall thickness of the pole tube, so that the recess does not form an opening. The recess is in particular completely or partially filled with a material, in particular a magnetically insulating material, such as plastic. For example, the recess is completely or partially filled with ambient air. The recess preferably has a cross section with a valve-side region that widens in the radial direction from the inside to the outside in the direction of the valve region. The pole tube preferably has a conical area in the area of the recess, which serves to introduce the magnetic flux into the armature. In the direction of the upper housing part, the valve-side area of the recess is adjoined by, for example, an area with a rectangular, in particular square, cross-section.

The coil is preferably fixed in the axial direction via the recess. The receptacle of the coil preferably has a projection pointing radially inwards, which engages in the recess of the pole tube and in particular has a shape that corresponds to the cross section of the recess, so that a positive connection is formed between the receptacle and the pole tube.

In particular, the tubular part is designed in one piece or in one piece. The pipe part is preferably formed in one piece, for example cast and in particular machined using machining processes such as turning, lasering or milling. For example, the pipe part is produced by cold forming. Preferably, the tubular part extends in the axial direction beyond the coil and the valve block. The tube part preferably forms the outer wall of the damping valve device together with the upper housing part. The damping valve housing preferably consists of the upper housing part and the tube part. The tubular part is preferably directly connected to the upper housing part and the outer cylinder tube of the vibration damper.

For example, the tube part is connected to the pole tube in a form-fitting, non-positive and/or material-locking manner. Preferably, the pole tube, in particular in the valve-side region, has a circumferential recess which interacts with a constriction of the tube part to form a positive connection.

For example, the pole tube is designed in one piece and/or in one piece and surrounds the armature and the control slide. According to a further embodiment, the pole tube extends in the axial direction beyond the valve block. The valve block and the control slide are preferably completely enclosed circumferentially and in the axial direction by the pole tube.

The damping valve device preferably has a flow plate made of a magnetic or magnetizable material, the flow plate resting on the coil, the pole tube and/or the tube part. The flow plate is preferably attached to the end face of the coil facing away from the valve area and extends in particular around the armature.

In particular, the magnetic circuit is formed from the coil, the pole tube, the tube part, the armature and the flux plate. The elements of the magnetic circuit are preferably made entirely or partially from a magnetic or magnetizable material. In particular, adjacent elements of the magnetic circuit lie directly against one another in order to ensure that the magnetic flux is as resistance-free as possible. For example, the flow plate is designed in the shape of an annular disk and has, for example, at least one radial recess. For example, the flow plate has a plurality of recesses pointing radially from the outside inwards, which are in particular evenly spaced from one another. Preferably, the recesses extend radially into the flow plate over about a third to half of the radius of the flow plate.

According to a further embodiment, the damping valve housing has an upper housing part which is attached to the front at one end of the tube part, the pole tube extending from the upper housing part to the valve block. A plug contact for a power connection of the coil and in particular electrical lines leading from the plug contact to the coil, such as conductor tracks, sheet metal strips or copper strips, are preferably arranged in the upper housing part. The upper housing part preferably forms a cover of the tube part.

The pole tube is connected, for example, to the valve block by means of a mechanical joining connection. A mechanical joining connection is preferably understood to mean a connection between two components by means of forming, with at least one of the components being mechanically formed. A connection of the pole tube to the valve block by reshaping the pole tube and/or the valve block enables the pole tube to be easily pre-assembled on the valve block, so that it can be inserted into the tube part together with the valve lock and connected to it. This significantly reduces assembly time and assembly costs.

The mechanical joining connection includes, for example, a plastic deformation of the pole tube, such as crimping and/or rolling of the pole tube. The end region of the pole tube is preferably mechanically formed in order to form the mechanical joint connection between the pole tube and the valve block. In particular, a biasing element, for example a spring washer or a plate spring, is arranged between the pole tube and the valve block. The biasing element is in particular designed in such a way that it applies an axial spring force to the pole tube and preferably braces this against the valve block. For example, the pole tube has a forming edge which is produced by plastic deformation of the pole tube, whereby the prestressing element lies against it. Preferably, the biasing element rests on the valve block, in particular the comfort valve body.

The invention also includes a vibration damper for a vehicle with a damping valve device as described above, the vibration damper having an outer cylinder tube and the tube part of the damping valve device being connected to the cylinder tube, in particular directly. Preferably, the cylinder tube is connected to the tube part in a form-fitting, non-positive and/or material-locking manner. In particular, the cylinder tube is connected to the tube part via a fastening means. A comfort valve is preferably arranged in the pipe part, which is in particular hydraulically connected in series to the damping valve device described above.

Description of the drawings

The invention is explained in more detail below using several exemplary embodiments with reference to the accompanying figures.

Fig. 1 shows a schematic representation of a vibration damper with a damping valve device in a side view according to an exemplary embodiment.

Fig. 2 shows a schematic representation of a damping valve device in a sectional view according to an exemplary embodiment.

Fig. 3 shows three schematic representations of an annular space in a sectional view according to an exemplary embodiment.

Fig. 1 shows a vibration damper 2 for a vehicle chassis, the vibration damper 2 comprising a damping valve device 1. The vibration damper 2 of FIG. 1 is only shown in an external view. The vibration damper 2 preferably comprises a cylinder tube which has a hydraulic fluid sealed therein, a piston which is axially movable within the cylinder tube along a cylinder tube axis and which divides the cylinder tube into two Working spaces divided, a piston rod that is aligned parallel to the cylinder tube axis and connected to the piston. In particular, the piston has at least two fluid passages through which one working space is connected to the other working space. The vibration damper 2 is, for example, a multi-tube vibration damper. In particular, the vibration damper 2 has an inner cylinder tube in which the piston is guided. For example, the outer cylinder tube 21 is attached coaxially around the inner cylinder tube, with an annular space being formed between the inner and outer cylinder tubes 21. Between the inner and outer cylinder tubes 21 and coaxially therewith, a center tube is preferably attached, which divides the annular space. To dampen the piston movement in at least one, preferably both, actuation direction(s), a damping valve device 1 is connected to at least one of the working spaces. The damping valve device 1 is preferably attached to the center tube and the outer cylinder tube 21 of the vibration damper 2.

Fig. 2 shows a damping valve device 1 with a preferably cylindrical damping valve housing 3, which comprises a substantially tubular tube part 4 and an upper housing part 5 attached to the tube part 4. The tube part 4 is connected at one end to the cylinder tube 21 of the vibration damper 2, not shown in FIG. 2. At the other end of the tube part 4, opposite the cylinder tube 21, the upper housing part 5 is attached, so that the upper housing part 5 preferably closes the tube part 4 at the end. The upper housing part 5 has, for example, a circular cylindrical cover section 22, which has a larger diameter than the tube part 4 and protrudes radially beyond the tube part 4. The cover section 22 is adjoined by a hollow cylinder section 23, which has a smaller diameter than the tube part 4, in particular than the inner diameter of the tube part 4, and is arranged within the tube part 4 coaxially therewith. The upper housing part 5, in particular the hollow cylinder section 23, preferably rests on the inner wall of the tube part 4. By way of example, the cover section has an annular recess on the side pointing in the direction of the tube part 4, in which the end of the tube part 4 is received. The pipe part 4 is connected, for example, to the upper housing part 5 via a positive connection 24. The positive connection 24 is, for example, a radial recess formed in the upper housing part 5, into which a radial narrowing of the tube part 4 engages. The positive connection 24 is preferably formed on the end of the tubular part 4 facing the upper housing part 5. The upper housing part 5, in particular the cover section 22, has a connection area 25 which has one or more connection contacts for an electrical power supply to the damping valve device 1. The connection contacts for an electrical power supply are preferably connected to a drive unit 19.

The damping valve device 1 has, for example, a drive area 19 and a valve area 9. The drive area 19 is, for example, arranged in the upper area of the damping valve device 1 facing the upper housing part 5 and preferably essentially above the valve area 9. The drive area 19 preferably comprises a drive designed as an electromagnet. The electromagnet comprises a coil 8 with a plurality of windings made of a current-conducting wire. The coil 8 is preferably arranged within the tube part 4 and concentric to it. By way of example, the coil 8 is arranged within the hollow cylinder section 23 of the upper housing part 5 and rests in particular on the inner wall of the upper housing part 5. In particular, the coil 8 is cast into the upper housing part 5, the upper housing part 5 being formed, for example, from a plastic, in particular a non-magnetic or only very slightly magnetic material, preferably a magnetic insulator or a material with a high magnetic resistance. The coil includes, for example, a coil carrier on which the windings of the coil are wound. The coil 8 at least partially or completely encloses an armature space 26, which extends centrally in the axial direction and concentrically to the tubular part 4. An anchor 11 is mounted so that it can move axially within the anchor space 26. The anchor 11 is preferably cylindrical and has a diameter that is slightly smaller than the diameter of the anchor space 26, so that the anchor 11 is preferably mounted so that it can slide in the axial direction. By way of example, the armature 11 has an upper first cylindrical region facing the upper housing part 5, which is adjoined on the valve region side by a second cylindrical region, which is arranged coaxially to the first region and has a smaller diameter. The anchor space 11 is preferably delimited by a hollow cylinder 16, which is coaxial and is arranged within the pipe part 4. The hollow cylinder 16 preferably has a base and is designed to be open, in particular in the direction of the cylinder tube 21. The bottom preferably points in the direction of the upper housing part 5 and lies, for example, at least partially against it. The hollow cylinder 16 is preferably made of a magnetizable or magnetic material.

The coil 8 is preferably designed and arranged in such a way that when current is applied, it forms a magnetic field which has magnetic field lines which preferably run essentially in the axial direction in the armature space 26. The armature 11 is preferably made of a magnetizable or magnetic material and can be moved in the axial direction in accordance with the polarity of the magnetic field formed by the coil 8. In particular, a pole part 12 is arranged within the armature space 26, which is hollow cylindrical and is arranged coaxially to the tube part 4. The armature 11, in particular the second cylindrical region of the armature 11, extends centrally through the pole part 12 in the axial direction. The pole part 12 is preferably made of a magnetizable or magnetic material. The pole part 12 rests in particular on the inner wall of the hollow cylinder 16 and is, for example, firmly connected to it. An annular space is preferably formed between the pole part 12 and the armature 11, through which in particular a hydraulic fluid can flow.

A flow plate 10 is arranged circumferentially around the hollow cylinder 16 and concentric to it. The flow plate 10 is preferably designed as a hollow cylinder and rests in particular on the outer wall of the hollow cylinder 16. Furthermore, the flux plate 10 lies at least partially on the tube part 4 and preferably represents a magnetic flux connection between the hollow cylinder 16 and the tube part 4. The flux plate 10 preferably lies on the coil 8 and in particular provides a magnetic flux connection between the hollow cylinder 16 and the tube part 4 and/or the coil 8. The flow plate 10 has, for example, at least two recesses that are opposite each other and run in the radial direction from the outside to the inside, through which the section of the illustration in FIG. 2 runs. A pole tube element 6 adjoins the hollow cylinder 16 in the axial direction and coaxially therewith. The pole tube element 6 and the hollow cylinder 16 together form the pole tube 7, the pole tube 7 being formed in particular in one piece or in one piece. Preferably, the pole tube element 6 is formed in one piece with the hollow cylinder 16 or is firmly connected to it, for example in a form-fitting, non-positive and/or material-locking manner. The hollow cylinder 16 extends at least partially or completely in the axial direction along the coil 8. Preferably, the pole tube element 6, together with the hollow cylinder 16, encloses at least the armature 11, the armature space 26 and the pole part 12.

The pole tube 7 has an upper tubular region with, in particular, a constant inner diameter, which preferably comprises the hollow cylinder 16 and extends from the upper housing part in the axial direction to beyond the armature 11. The upper tubular region is adjoined in the axial direction by a lower region with an enlarged diameter, the outer surface of the pole tube, in particular of the pole tube element 6, preferably extending up to the tube part 4 and at least partially resting against it. The inner surface of the lower region of the pole tube element 6 at least partially encloses a valve region 9, which is explained in more detail in one of the following sections. The pole tube 7 preferably has a recess 18, which is formed, for example, in a ring-shaped circumference in the pole tube wall. The recess 18 is preferably arranged coaxially with the coil 8 and in particular within the coil 8. The recess 18 has, for example, a square cross section.

The pole tube element 6 of the pole tube 7 preferably has a plurality of different inner diameters, each of which forms cylindrical spaces of different diameters. The pole tube 7 also has, in particular, a plurality of different outer diameters. In the axial direction from the drive region 19 in the direction of the valve region 9, the pole tube 7 preferably has a first outer diameter, which forms the hollow cylinder 16 and preferably extends along the coil 8. This is followed by a second outer diameter which is larger than the first outer diameter, so that a shoulder, in particular an axial end face, is formed which extends in the direction of the Upper housing part 5 has and on which the coil 8 rests at least partially, for example. The second outside diameter is preferably smaller than the inside diameter of the tube part 4 and in particular is spaced from it in such a way that a chamber 14 is formed between the pole tube 7 and the tube part 4. The second outer diameter is followed by, for example, a third outer diameter of the pole tube 7, which is larger than the first and the second outer diameter and preferably essentially corresponds to the inner diameter of the tube part 4, so that the pole tube 7 rests on the tube part 4 with the third outer diameter. A shoulder, in particular an axial end face, is formed between the second and the third outer diameter and points in the direction of the upper housing part 5. The pole tube element 6 is preferably made of a magnetizable or magnetic material.

The chamber 14 is preferably designed to accommodate a sealing element 13, in particular a sealing ring. The chamber 14 is preferably designed in the shape of a circular ring and in particular has a rectangular cross section. The chamber 14 is in particular completely closed and delimited by the pole tube 7, the tube part 4 and, for example, the coil 8. The coil 8 preferably has a projection 15 which runs in the axial direction, in particular along the inner wall of the tube part 4, which extends between the tube part 4 and the pole tube 7 and adjoins the chamber 14. The projection 15 is preferably made of a plastic and is in particular positively connected to the pole part 7 and the tube part 4. The end face of the projection 15 pointing in the valve direction preferably forms a boundary of the chamber 14.

A sealing element 13 is mounted in the chamber 14, the sealing element 13 preferably being a sealing ring. The sealing element 13 is, for example, designed in the shape of a circular ring and preferably has a round, in particular circular, cross section. The sealing element 13 preferably rests at least on the pole tube 7 and the tube part 4 and serves to seal the valve area 9 from the drive area 19, so that no hydraulic fluid passes from the valve area 9 into the coil 8. In particular, the sealing element 13 is additional on a shoulder, preferably the axial end face formed between the second and third outer diameter of the pole tube 7.

Alternatively, it is possible for the projection 15 to be designed as a support 15. The support 15 is, for example, designed separately from the coil 8 and lies at least partially against it with an outer surface. The support 15 is preferably designed in the shape of a circular ring and, for example, has a rectangular cross section. In particular, the support ring rests with its outer surface on the inside of the tube part 4 and with its inner surface on the outer surface of the pole tube 7. The end face of the support ring 15 pointing in the valve direction borders the chamber 14. The support ring 15 is preferably firmly connected to the coil 8, the pole tube 7 and/or the tube part 4. The support ring 15 preferably forms a contact surface for the sealing element 13.

The pole tube element 6 is preferably connected to the tube part 4 via a positive connection. The form-fitting connection preferably comprises a radial recess, in particular recesses, in the pole tube element 6, into which a radial constriction of the tube part 4 engages and interacts with it in such a way that the pole tube element 6 is fixed in the axial and radial directions. The positive connection is in particular a bayonet connection. For example, the pole tube 7, in particular the pole tube element 6, has a plurality of recesses 33, which are in particular hook-shaped. Each recess 33 includes, for example, an area that extends in particular in the axial direction and an area that adjoins this area and extends in the circumferential direction. At least one or more radial constrictions 32 of the tubular part 4 preferably engage in the recess 33. The recesses 33 are preferably radial depressions which are formed in the outer surface of the pole tube 7 which rests on the tube part 4. The recesses 33 preferably extend into the chamber 14 and in particular form interruptions in the support surface of the sealing element 13. In Fig. 2, only the areas of the recess 33 running in the circumferential direction are partially shown.

The valve area 9 is preferably integrated into a hydraulic circuit, not shown, and is fluidly connected to the vibration damper 2, in particular the work spaces of the vibration damper 2 connected. The valve area 9 has an inlet 28 and an outlet 29, the functionality of which can be reversed depending on the flow direction of the damping fluid.

The valve region 9 of the damping valve device 1 preferably comprises a control slide 17, which is at least partially or completely circumferentially enclosed by the pole tube element 6 and in particular is arranged coaxially with this and the tube part 4. The control slide 17 preferably has an axial end face which points in the direction of the armature 11 and on which the armature 11, in particular the lower, second region of the armature 11, rests, so that a movement of the armature 11 is transmitted to the control slide 17.

Furthermore, the valve area 9 comprises a valve block 27. The control slide 17 preferably surrounds the valve block 27 circumferentially and is mounted so that it can move in the axial direction relative to the valve block 27. The valve block 27 is in particular funnel-shaped and has, for example, an upper cylindrical region facing the drive unit 19, which is arranged coaxially to the control slide 17. At the lower region facing away from the drive unit 19, the valve block 27 has, for example, a radial expansion. The valve block 27 is in particular stationary relative to the axially movable control slide 17. Preferably, the valve block 27 is at least partially or completely enclosed circumferentially and in the axial direction by the pole tube element 6, with the control slide 17 being arranged between the upper region of the valve block 27 and the pole tube element 6. The lower region of the valve block 27 is arranged in the radial direction directly adjacent to the pole tube element 6 and preferably lies at least partially against it. Only partially shown flow passages 20 are formed within the valve block 27, through which the damping fluid can flow from the inlet 28 in the direction of the outlet 29. The control slide 17 is mounted so that it can move axially in such a way that it completely opens the flow passages 20 in an open position of the damping valve device 1 and completely closes the flow passages 20 in a closed position of the damping valve device 1. The control slide 17 can preferably assume a variety of intermediate positions in which the Flow passages 20 are partially closed. The control slide 17 is preferably biased towards an open valve position by means of a spring, not shown, so that the damping valve is open when the coil 8 is de-energized. The spring is preferably arranged between the control slide 17 and the valve block 27 and preferably acts on the control slide with a force acting axially in the direction of the drive region 19. An annular space 30 for conducting the damping fluid is preferably formed between the valve block 27 and the pole tube element 6. The annular space 30 preferably extends completely around the upper region of the valve block 27 that can be enclosed by the control slide 17 and in particular at least partially or completely around the lower region of the valve block 27. The control slide 17 is preferably axially movable within the annular space 30.

The valve area 9 preferably includes a comfort valve and a solenoid valve, which are hydraulically connected in series with one another. By way of example, the valve block 27 includes two valve bodies. The valve body pointing in the direction of the drive area is, for example, the solenoid valve body, which has the flow passages 20 described above and a plurality of flow channels 31 and cooperates with the control slide 17, which can be moved by means of the coil 8. In the direction of the cylinder tube 21 of the vibration damper 2, the comfort valve body preferably adjoins the magnetic valve body. By way of example, the valve block 27, which is optionally formed from a solenoid valve body and a comfort valve body, is designed in one piece or in one piece.

In particular, the fluid drain 29 is formed between the valve block 27 and the pole tube 7. A plurality of flow channels 31 are preferably formed between the pole tube 7 and the valve block 27. The flow channels 31 are at least partially formed in the valve block 27. The flow channels 31 preferably extend along the pole tube 7, the pole tube 7 preferably having no passage openings, in particular bores, for guiding the damping fluid through the pole tube wall. The pole tube 7, for example, extends at least partially in the axial direction along the comfort valve body. The end region of the pole tube 7 is preferably mechanically formed in order to form a connection between the pole tube 7 and the valve block 27. The pole tube 7 and the valve block 27 are connected to one another in particular by means of a mechanical joining connection. The joining connection is, for example, a crimping or a rolling. Preferably, the end region of the pole tube 7 pointing in the direction of the comfort valve is formed radially inwards, so that in particular a radially inward-pointing forming edge of the pole tube 7 is formed.

3 shows a detailed view of the annular space 30, the components shown essentially corresponding to those of FIG. 2.

The valve block 27, in particular the solenoid valve body, has a first cylindrical region 40 in which the flow passages 20 are formed. The first region 40 is preferably adjoined in the direction of the fluid outlet 29 by a second essentially cylindrical region 41 with a larger diameter relative to the first region 40. The second area is not completely shown in FIG. 3. The flow channels 31 are formed in the second area. As shown in Fig. 2, the flow channels 31 are preferably designed to be open in the direction of the pole tube 7, so that the flow channels 31 are each formed between the inner surface of the pole tube 7 and the radially outward-facing surface of the valve block 27, in particular the second region 41 . The second region 41 has, for example, a circumferential surface pointing radially outward and a shoulder surface pointing axially in the direction of the first region 40. The shoulder surface preferably rests on the pole tube 7. The flow channels 31 preferably extend from the shoulder surface to the peripheral surface and in particular represent recesses, preferably bulges, in the shoulder surface and the peripheral surface. By way of example, the direction of extension of the flow channels 31 has an axial and a radial component. For example, the flow channels 31 extend continuously at an angle of 10° to 80°, in particular 20° to 60°, preferably 30° to 50° to the axial. The flow channels 31 are, for example, designed in the shape of a half-shell in the valve block 27 and in particular extend in a star shape away from the first region 40, in particular the flow passages 20. By way of example, the flow channels 31 each extend from a radially inner, completely annular region of the shoulder surface outwards to the peripheral surface. The flow channels 31 have, for example, a round, semicircular, circular, oval, rectangular or square cross section. Preferably, all or a plurality of flow channels 31 are geometrically identical and in particular evenly spaced from one another in the circumferential direction.

The first region 40 of the valve block 27 has the flow passages 20 and is preferably arranged coaxially to the control slide 17. The first area 40 can preferably be completely or partially enclosed by the control slide 17. The flow passages 20 are preferably circular bores in the valve block 27, in particular the wall of the first region 40 of the valve block 27. By way of example, the flow passages 20 are arranged evenly spaced apart from one another. The valve block 27 preferably has six flow passages 20, which are arranged circumferentially around the first region 40 of the valve block 27 and in particular adjacent flow passages 20 are arranged offset from one another by 60 °. The number of flow passages 20 is preferably an even number, in particular four, six, eight or 10.

The annular space 30 is preferably delimited at least by the control slide 17, the pole tube 7 and the valve block 27. The annular space 30 has an inner diameter and an outer diameter. By way of example, the annular space 30 has at least two different outer diameters. The first outer diameter Da1 preferably extends over a length L1 in the axial direction and is preferably formed partially or completely around the control slide 17. The outer diameter of the annular space 30 corresponds in particular to the inner diameter of the pole tube 7.

The annular space 30 preferably comprises a first annular space region 42, which has the constant first outer diameter Da1, and a second annular space region 44, which preferably adjoins the first annular space region 42 in the direction of the fluid outlet 29. The first annular space region preferably extends 42 with the first outer diameter Da1 at least partially around the flow passages 20 formed in the valve block 27. The second annular space region 44 directly adjoins the first annular space region 42 and preferably extends to the second region 41 of the valve block 27, in which the flow channels are formed. Preferably, the second annular space region 44 is at least partially delimited by the flow channels 31. The second annular space region 44 preferably extends at least partially around the flow passages 20 formed in the first region 40 of the valve block 27.

The second annular space region 44 preferably has an outer diameter that is variable, in particular inconstant, over an axial length L2. In particular, the second annular space 44 has a maximum outside diameter Da2 that is larger than the outside diameter Da1 of the first annular space region. The maximum outside diameter Da2 of the second annular space region 44 preferably corresponds to the outside diameter of the flow channels 31. In particular, the second annular space 44 has a minimum outside diameter that is greater than or equal to the outside diameter Da1 of the first annular space region 42. The minimum outside diameter of the second annular space region 44 preferably corresponds to the inside diameter of the flow channels 31. Preferably, the change in outside diameter of the second annular space section 44 between the minimum outside diameter and the maximum outside diameter Da2 corresponds to a pitch circle section.

The first annular space section 42 preferably has an inner diameter Di1, which corresponds, for example, to the outer diameter of the control slide 17 or the outer diameter of the valve block 27, in particular the first region 40 of the valve block 27. The ratio of the outer diameter Da1 to the inner diameter Di1 in the first annular space section 42 is preferably Da1 / Di1 = 0.7 to 0.95, in particular 0.8 to 0.9. The second annular space section 44 preferably has an inner diameter Di2, which corresponds, for example, to the outer diameter of the valve block 27, in particular the second region 41 of the valve block 27. The ratio of the outer diameter Da2 to the The inside diameter Di2 in the second annular space section 44 is preferably Da2 / Di2 = 0.7 to 0.95, in particular 0.8 to 0.9.

The second annular space section 44 preferably extends over a length L2 in the axial direction. By way of example, the second annular space section 44 extends from the first annular section 42 with a constant outer diameter Da1 to the second region 41 of the valve block 27. In particular, the second annular space section 44 exclusively includes the region which has an outer diameter Da2x that continuously changes in the axial direction. The second annular space section 44 is adjoined in the direction of the fluid outlet 29 by, for example, a further annular space section which preferably has a constant outer diameter. Preferably, the ratio of half the diameter difference to the length L2 corresponds to approximately 0.4 to 0.7, in particular 0.5 to 0.6. 0.4 to 0.7, especially 0.5 to 0.6

The damping valve device 1 serves, in particular, to continuously adjust the damping of the vibration damper 2. When the vibration damper 2 is in operation, the coil 8 is supplied with electrical current to set the desired damping. This creates a magnetic field whose magnetic field lines run essentially in the axial direction inside the coil and in particular in the armature space 26. The magnetic flux of the magnetic field runs in a magnetic circuit which is formed within the damping valve device 1. The magnetic circuit includes components made of materials with a low magnetic resistance, preferably made of magnetic or magnetizable material. The magnetic circuit for conducting the magnetic field, in particular the magnetic flux, is preferably formed from the flux plate 10, the hollow cylinder 16, the pole tube element 6, the armature 11, the tube part 4 and/or the pole part 12. The armature is based on the polarity of the magnetic field 11 moved in the axial direction. The movement of the armature 11 is transmitted to the control slide 17 coupled to the armature 11, so that it closes or at least partially opens the flow passages 20 of the valve block 27. 2 shows an example of an open position of the damping valve device 1. Reference symbol list

1 damping valve device

2 vibration dampers

3 Damping valve housing

4 pipe part

5 upper housing part

6 pole tube element

7 pole tube

8 coil

9 valve area

10 River Plate

11 anchors

12 pole part

13 sealing element

14 chamber

15 Lead / Support

16 hollow cylinders

17 control slides

18 recess

19 drive unit

20 flow passages

21 cylinder tube

22 lid section

23 hollow cylinder section/receptacle

24 positive connection

25 connection area

26 anchor room

27 valve block

28 Inlet / fluid inlet

29 Drain / fluid outlet

30 annulus

31 flow channels

32 constriction

33 recess in the pole tube

34 valve body solenoid valve

35 valve body comfort valve

36 forming edge

37 prestressing element

38 support shoulder

40 first area

41 second area

42 first rinsing area

44 second rinsing area

Da1 outer diameter of the first annular space area

Di 1 inner diameter of the first annular space area

Da2 maximum outside diameter of the second annular space area

Da2x variable outside diameter of the second annular space Di2 inner diameter of the second annulus area

Claims

Patent claims

1 . Damping valve device (1) for a hydraulic vibration damper (2) for a vehicle, comprising: a drive area (19) and a valve area (9), a damping valve housing (3) with a pipe part (4) that the drive area

(19) and encloses the valve area (9), the drive area (19) having a coil (8) which is designed such that it generates a magnetic circuit within the damping valve device (1) and with one within the coil (8) axially movably attached anchor (11) cooperates to move the armature (11) in the axial direction, the armature (11) being arranged within a pole tube (7) and the pole tube (7) forming a guide of the armature (11), the valve area (9) has a fluid inlet (28) and a fluid outlet (29) for inlet and outlet of a hydraulic fluid into the valve area (9) and a valve block (27) with a plurality of flow passages

(20) for directing the hydraulic fluid, wherein the valve area (9) has a control slide (17) which is movably mounted relative to the valve block (27) in such a way that it can move between a closed position in which the flow passages (20) through the Control slide (17) are closed, and an open position in which the flow passages (20) are free, is movable, characterized in that an annular space (30) filled with hydraulic fluid is separated from the control slide (17), the pole tube (7) and the valve block and wherein the annular space (30) has at least two different outer diameters, wherein the annular space (30) has a first annular space region (42) and a second annular space region (44) and wherein the first annular space region (42) is controlled by the control slide (17 ) is limited and the second annular space region (44) comprises flow channels (31) formed between the valve block (27) and the pole tube (7). 2. Damping valve device (1) according to claim 1, wherein the first annular space region (42) has a first outside diameter (Da1) and the second annular space region (44) has a second outside diameter (Da2) and wherein the second outside diameter (Da2) is larger than the first outside diameter (Da1).

3. Damping valve device (1) according to one of the preceding claims, wherein the first outer diameter (Da1) is constant over the first annular space region (42) and the second outer diameter (Da2x) is variable over the second annular space region (44).

4. Damping valve device (1) according to one of the preceding claims, wherein the second annular space region (44) has a maximum outside diameter (Da2) which corresponds to the outside diameter of the flow channels (31).

5. Damping valve device (1) according to one of the preceding claims, wherein the second annular space region (44) has a minimum outside diameter which corresponds to the first outside diameter (Da1) of the first annular space region (42).

6. Damping valve device (1) according to one of the preceding claims, wherein the change in the outside diameter of the second annular space section (44) between the minimum outside diameter and the maximum outside diameter (Da2) corresponds to a mathematical function, preferably a pitch circle section.

7. Damping valve device (1) according to one of the preceding claims, wherein the first annular space region (42) has an inner diameter (Di1) and wherein the ratio of the outer diameter (Da1) to the inner diameter (Di1) is 0.7 to 0.95, in particular 0 .8 to 0.9.

8. Damping valve device (1) according to one of the preceding claims, wherein the second annular space region (44) has an inner diameter (Di2). and wherein the ratio of the outer diameter (Da2x) to the inner diameter (Di2) is 0.7 to 0.95, in particular 0.8 to 0.9. Damping valve device (1) according to one of the preceding claims, wherein the ratio of the inside diameter (Di2) to the maximum outside diameter (Da2) of the second annular space region (44) corresponds to less or equal to 0.51. Damping valve device (1) according to one of the preceding claims, wherein the ratio of the inner diameter of the flow channels (31) to the outer diameter of the flow channels (31) is 0.6 to 1.1, preferably 0.7 to 1.02. Damping valve device (1) according to one of the preceding claims, wherein a plurality of flow channels (31) are formed between the pole tube (7) and the valve block (27), which extend at least partially in the radial and axial directions. Damping valve device (1) according to one of the preceding claims, wherein the pole tube (7) extends in the axial direction beyond the valve block (27). Damping valve device (1) according to one of the preceding claims, wherein the damping valve housing (3) has an upper housing part (5) which is attached to the front side at one end of the tube part (4) and wherein the pole tube (7) extends from the upper housing part (5). extends to the valve block (27). Vibration damper (2) for a vehicle comprising a damping valve device (1) according to one of the preceding claims, wherein the vibration damper has an outer cylinder tube (21) and wherein the tube part (4) of the damping valve device (1) is connected to the cylinder tube (21).