Bidirectional damper device, damper, and method

Abstract

The invention relates to a bidirectional damper device (30a-b), in particular a bidirectional shock absorber device, for example for a vehicle shock absorber, comprising a control valve unit (12a-b), which has at least one control valve slide (10a-b), for controlling a traction stage damping hardness and for controlling a compression stage damping hardness, in particular by means of a pilot control of a damper valve slide (14a-b), which is preferably formed separately from the control valve slide (10a-b), on the basis of control valve slide (10a-b) positions which can be set, in particular in a controlled manner. According to the invention, the control valve unit (12a-b) is designed such that in the event of a damping process, a flow is carried out through the control valve slide (10a-b) at least in the same direction and / or a flow is carried out around the control valve slide at least in the same direction regardless of an activation of a compression stage or a traction stage.

Description

[0001] Bidirectional damper device, damper and method

[0002] State of the art

[0003] The invention relates to a bidirectional damper device according to the preamble of claim 1, a damper according to claim 26 and a method for operating the bidirectional damper device according to claim 27.

[0004] A bidirectional damper device for a vehicle shock absorber has already been proposed, comprising a control valve unit having at least one control valve slide for controlling a rebound damping hardness and for controlling a compression damping hardness depending on adjustable positions of the control valve slide.

[0005] The object of the invention is, in particular, to provide a generic device with advantageous hydraulic properties. This object is achieved according to the invention by the features of patent claims 1, 26, and 27, while advantageous embodiments and further developments of the invention can be found in the subclaims.

[0006] Advantages of the invention

[0007] The invention is based on a bidirectional damper device, in particular a bidirectional shock absorber device, for example for a damper or vehicle shock absorber, with a control valve unit having at least one control valve slide for controlling a rebound damping hardness and for controlling a compression damping hardness, in particular by means of a pilot control of a damper valve slide, preferably designed separately from the control valve slide, as a function of, in particular specifically adjustable, positions of the control valve slide.

[0008] It is proposed that the control valve unit be designed such that, in the damping case, the control valve spool is at least flowed through and / or at least flowed around in the same direction in the same direction, regardless of the activation of a compression stage or a rebound stage, in particular of the damper or vehicle shock absorber, and preferably regardless of the direction of action of a damper valve spool piloted by the control valve unit (should this be dependent on the rebound or compression stage at all), in particular of the damper valve spool piloted by the control valve unit. This makes it possible to achieve advantageous hydraulic properties, in particular advantageous flow properties. This advantageously makes it easier and / or better to optimize and / or compensate for any flow forces that occur, particularly in comparison with non-rectified flow. This advantageously makes it possible to reduce costs.In particular, the bidirectional damper device is designed to dampen a rebound stage and a compression stage of a damper. In particular, the bidirectional damper device is designed to selectively damp tensile loads and compressive loads. The terms “intended” and / or “designed” should be understood to mean, in particular, specially programmed, designed and / or equipped. The fact that an object is intended or designed for a specific function should be understood to mean, in particular, that the object fulfills and / or performs this specific function in at least one application and / or operating state. The bidirectional damper device is preferably provided for chassis damping of a vehicle. In particular, the position of the control valve spool is adjustable by means of an actuator device, for example by means of an electromagnet, in particular in the axial direction of the control valve spool.For example, the control valve spool can be connected to a solenoid armature of the electromagnet. In particular, the damping stiffness depends on the maximum possible flow rate of the bidirectional damper device. The lower the maximum possible flow rate, the lower the damping stiffness, and vice versa.

[0009] In particular, the control valve unit is provided for adjusting the maximum possible flow rate of a flow path of the damper bypassing the damper valve spool within an available range by adjusting the control valve spool. In particular, the control valve unit is provided for pilot control of a damper valve spool forming a main valve spool of a damper. In particular, the damper valve spool and the control valve spool are movable independently of one another. In particular, the control valve spool and the damper valve spool are non-contact with one another. In particular, the control valve unit is designed such that the control valve spool must be moved in an identical adjustment direction to adjust the rebound damping hardness and the compression damping hardness, starting from an identical rest position of the control valve spool.In the rest position, an electromagnet that adjusts the position of the control valve spool is preferably de-energized. In the rest position, preferably no electromagnetic force acts on the control valve spool. The control valve spool is preferably moved from the identical rest position in the identical adjustment direction to follow a damping characteristic curve of the rebound damping hardness and the compression damping hardness. In particular, the control valve spool is moved from the identical rest position in the identical adjustment direction to increase the rebound damping hardness and to increase the compression damping hardness. In particular, the control valve spool is moved from the identical rest position in the identical adjustment direction to decrease the rebound damping hardness and to decrease the compression damping hardness.In particular, the actuator device, preferably the electromagnet, is designed for the targeted adjustment of the positions of the control valve slide.

[0010] In particular, the control valve spool can be at least partially flowed through. Alternatively or additionally, it is conceivable for the control valve spool to be at least partially flowed around. In particular, a current total flow rate of the flow through and / or the flow around the control valve spool determines the currently set rebound damping hardness and / or the currently set compression damping hardness. In particular, the flow direction, preferably the mean flow direction of the flow through and / or the flow around the control valve spool when the rebound stage is activated, is at least substantially identical to the flow direction, preferably the mean flow direction of the flow through and / or the flow around the control valve spool when the compression stage is activated.In particular, a pressurized fluid of the damper enters the control valve spool at one point, preferably at an opening, when flowing through the control valve spool and then exits the control valve spool at another point, preferably at a different opening. In particular, the control valve unit, preferably the control valve spool, has a flow-through region and / or a flow-around region which is explicitly designed for the pressurized fluid of the damper to flow through and / or around. In particular, in the damping case, when the compression stage of the damper and the rebound stage of the damper are activated, the flow through and / or around the control valve spool is in the same direction. In particular, there is no operating state of the bidirectional damper device in which a flow direction or a flow around the control valve unit is reversed.In particular, depending on the position in the control valve unit, the control valve spool is either exclusively flowed through, partially flowed through and partially flowed around, or completely flowed around. The proportion of flow through / bypassing depends in particular on the opening cross-section of the flow outlet openings of the control valve spool, which can be open, partially open, or closed depending on the position in the control valve unit.

[0011] It is further proposed that the control valve spool rests on an end stop of the control valve unit in the rest position, wherein the end stop has a flow channel that, in the rest position, is open to a flow inlet of the control valve spool. This advantageously allows for a fail-safe function to be achieved. Advantageously, a basic setting for the damping hardness can be defined, which is set during de-energized operation of the actuator device.

[0012] Furthermore, it is proposed that the rest position of the control valve spool constitutes a fail-safe position of the control valve unit, in particular of the control valve spool. This advantageously allows for a high level of operational reliability to be achieved.

[0013] If, in the fail-safe position of the control valve unit, a rebound damping stiffness is set that differs from a minimum rebound damping stiffness adjustable by the control valve unit and a maximum rebound damping stiffness adjustable by the control valve unit, and / or if, in the fail-safe position of the control valve unit, a compression damping stiffness is set that differs from a minimum compression damping stiffness adjustable by the control valve unit and a maximum compression damping stiffness adjustable by the control valve unit, damper comfort can advantageously be maintained even if the control valve unit fails. Advantageously, a "medium" damping stiffness can be set in the fail-safe state instead of a minimum stiffness or a maximum stiffness.

[0014] It is also proposed that the pressure fluid be deflected at least once as it flows through the control valve spool. This allows a high degree of compactness of the bidirectional damper device to be achieved. Furthermore, advantageous flow properties can be achieved. In particular, an inlet and an outlet direction of the pressure fluid are angled to one another as it flows through the control valve spool, preferably at an angle between 20° and 160°. For example, as it flows through the control valve spool, the pressure fluid can flow into the control valve spool from below and out of the control valve spool from the side.

[0015] Additionally, it is proposed that the control valve unit be provided to adjust, depending on the adjusted position of the control valve spool, an overall size of a minimum flow cross-section of connecting paths which connect opposite sides of the damper valve spool, in particular a compression side and a tension side of the bidirectional damper device, preferably hydraulically. This advantageously makes it possible to achieve a reliable and / or precise adjustment of the compression and rebound damping hardnesses. In particular, the connecting paths each extend from a tension side of the damper to a compression side of the damper and / or from a compression side of the damper to a tension side of the damper. It is also conceivable for the compression side and the tension side to be interchanged.

[0016] If the connecting paths, in particular regardless of activation of the compression or rebound stage, preferably all of them, run through at least part of the damper valve spool, a particularly compact design can advantageously be achieved. In particular, the connecting paths run identically through the control valve unit. In particular, the connecting paths connecting the tension side and the compression side run differently outside the control valve unit through the bidirectional damper device. In particular, the connecting paths run in different directions through the damper valve spool depending on whether the rebound or compression stage is activated. In particular, when damping, the flow through and / or around the damper valve spool is in the opposite direction, regardless of activation of a compression or rebound stage.

[0017] It is also proposed that the bidirectional damper device have a first rebound stage check valve arranged in at least some of the connecting paths, preferably in the rebound stage connecting paths, which is provided to open a connection from the rebound side to a (pressure fluid) inlet of the control valve unit upon activation of the rebound stage, in particular upon application of a force to be damped on a tension side of the bidirectional damper device, and to close a connection from the rebound side to the (pressure fluid) inlet of the control valve unit upon activation of the compression stage, in particular upon application of the force to be damped on a compression side of the bidirectional damper device. This makes it possible to achieve advantageous hydraulic properties, in particular advantageous flow properties. The unidirectional flow through the control valve spool can advantageously be achieved in this way.The rebound check valves preferably operate automatically, in particular without external control. The rebound check valves are preferably controlled solely by the hydraulic conditions in the damper. The rebound connecting paths are formed, in particular, by the portion of the connecting paths through which the pressurized fluid flows when the rebound stage is activated.

[0018] If the bidirectional damper device additionally has a second rebound stage check valve arranged in at least some of the connecting paths, preferably in the rebound stage connecting paths, which is provided to open a connection from a first (pressure fluid) outlet of the control valve unit to the pressure side of the bidirectional damper device upon activation of the rebound stage, in particular upon application of the force to be damped on the rebound side of the bidirectional damper device, and to close a connection from the pressure side to the first (pressure fluid) outlet of the control valve unit upon activation of the compression stage, in particular upon application of the force to be damped on the pressure side of the bidirectional damper device, advantageous hydraulic properties, in particular advantageous flow properties, can be achieved.This advantageously allows for the uniform flow through the control valve spool. In particular, the rebound check valves can be constructed identically or differently.

[0019] If the bidirectional damper device also has a first compression stage check valve arranged in at least some of the connecting paths, preferably in the compression stage connecting paths, which is provided to open a connection from the compression side to the (pressure fluid) inlet of the control valve unit upon activation of the compression stage, in particular when a force to be damped acts on a pressure side of the bidirectional damper device, and to close a connection from the pressure side to the (pressure fluid) inlet of the control valve unit upon activation of the rebound stage, in particular when the force to be damped acts on a rebound side of the bidirectional damper device, advantageous hydraulic properties, in particular advantageous flow properties, can be achieved. The unidirectional flow through the control valve spool can advantageously be achieved in this way.In particular, the rebound check valves can be structurally identical to the compression check valves but structurally different from the compression check valves.

[0020] If the bidirectional damper device additionally has a second compression stage check valve arranged in at least some of the connecting paths, preferably in the compression stage connecting paths, which is provided to open a connection from a second (pressure fluid) outlet of the control valve unit to the tension side of the bidirectional damper device upon activation of the compression stage, in particular upon application of the force to be damped on the pressure side of the bidirectional damper device, and to close a connection from the tension side to the second (pressure fluid) outlet of the control valve unit upon activation of the rebound stage, in particular upon application of the force to be damped on the tension side of the bidirectional damper device, advantageous hydraulic properties, in particular advantageous flow properties, can be achieved.Advantageously, the unidirectional flow through the control valve spool can be achieved in this way.

[0021] In particular, it is proposed that the damper valve spool have an active surface element arranged between the first rebound check valve and the second compression check valve, which in particular divides the connecting paths into compression-stage connecting paths and rebound-stage connecting paths separated from one another in sections, and which in particular has active active surfaces on opposite sides for the application of rebound forces and compression forces. In particular, the forces acting on the active active surfaces of the active surface element of the damper valve spool generate a damping-generating opening movement of the damper valve spool for a pressure fluid exchange between the compression side and the rebound side along damping paths different from the connecting paths.

[0022] Furthermore, it is proposed that, in a flow-through operating state, the control valve spool is flowed exclusively from the inside to the outside, regardless of the activation of a compression stage or a rebound stage, in particular of the damper, and preferably regardless of the direction of action of the damper valve spool piloted by the control valve unit. This allows advantageous hydraulic properties, in particular advantageous flow properties, to be achieved. The uniform flow through the control valve spool can advantageously be achieved in this way.

[0023] Furthermore, it is proposed that in operating conditions where a

[0024] Flow through the control valve unit is present and in which a minimum rebound damping stiffness or a minimum compression damping stiffness is simultaneously set, the control valve spool is completely free of flow. This allows an advantageous damping characteristic to be achieved. In particular, in this case, the control valve spool is exclusively flowed through, with the flow direction of the pressure fluid being identical, regardless of whether the bidirectional damper device is currently operating at the minimum rebound damping stiffness or the minimum compression damping stiffness.

[0025] It is further proposed that the control valve spool have at least one bypass channel, which runs in particular obliquely or perpendicularly to a movement axis of the control valve spool and / or obliquely or perpendicularly to a normal of an opening plane of a flow inlet of the control valve spool, which bypass channel is arranged in the control valve spool such that, in the rest position of the control valve spool, it is open to the first (pressure fluid) outlet of the control valve unit connected to the pressure side of the bidirectional damper device and / or to the second (pressure fluid) outlet of the control valve unit connected to the tension side of the bidirectional damper device. This makes it possible to achieve advantageous hydraulic properties, in particular advantageous flow properties. The rectified flow through the control valve spool can advantageously be achieved in this way.In particular, the first (pressure fluid) outlet is assigned the second rebound stage check valve, which opens or closes depending on the presence of the higher pressure on the rebound side. In particular, the first (pressure fluid) outlet is assigned the second compression stage check valve, which opens or closes depending on the presence of the higher pressure on the compression side. Depending on the flow direction, the respective check valves will thus open either the first outlet or the second outlet and keep the other closed. It is also proposed that at least one opening of the bypass channel is arranged in the control valve spool in such a way that when the control valve spool is deflected from the rest position, an opening cross-sectional part of the opening of the bypass channel connected to the first outlet and / or the second outlet decreases in size.This advantageously allows the flow rate of the control valve spool to be adjusted depending on the position of the control valve spool. This advantageously allows pre-control of the damper valve spool via the control valve spool. In particular, when the control valve spool is raised from the end stop, the flow cross-section of the bypass channel decreases, preferably to the point of complete closure of the bypass channel.

[0026] It is further proposed that the control valve spool is designed such that, over at least part of a deflection movement that the control valve spool experiences when deflected from the rest position, a total opening cross-section, which is composed of the opening cross-sectional part of the opening of the bypass channel connected to the first output and / or the second output and a further opening cross-section of a control opening of the control valve unit created by the control valve spool being lifted off an end stop of the control valve unit, is reduced. As a result, a flow rate through the control valve spool can advantageously be adjusted depending on the position of the control valve spool. As a result, pilot control of the damper valve spool can advantageously be achieved via the control valve spool.In particular, the control opening connects a (common) inlet of the control valve unit to the first outlet of the control valve unit, which is connected to the pressure side of the bidirectional damper device, and / or to the second outlet of the control valve unit, which is connected to the tension side of the bidirectional damper device. Furthermore, when the control valve spool lifts off the end stop, the overall opening cross-section preferably also decreases at least in a further (different) part of the deflection movement of the control valve spool, whereby, in particular, the damping hardness initially decreases when the control valve spool lifts off the end stop.

[0027] Consequently, if a curve plotting the total opening cross-section of the control valve unit connecting a tension side of the bidirectional damper device and a compression side of the bidirectional damper device over the distance of the control valve spool from the rest position exhibits a global minimum, a particularly advantageous bidirectional damping behavior can be achieved, particularly with the inclusion of a failsafe function. In particular, the adjustable damping hardness is at a minimum at the global minimum of the curve. If the control valve spool is opened further from the global minimum, the previously continuously decreasing damping hardness increases again.

[0028] Furthermore, it is proposed that the total opening cross-section of the control valve unit connecting the tension side of the bidirectional damper device and a compression side of the bidirectional damper device be larger in at least one operating position of the control valve spool other than the rest position than in the rest position. This makes it possible to achieve particularly advantageous bidirectional damping behavior, particularly with the inclusion of a failsafe function. This advantageously makes it possible to achieve a damping hardness that is lower in at least one position of the control valve spool than in the failsafe state, in which the control valve spool rests on the end stop.

[0029] It is further proposed that the control valve unit be designed as a needle valve. This makes it possible to achieve advantageous hydraulic properties, in particular advantageous flow properties. This advantageously makes it easier and / or better to optimize and / or compensate for any flow forces that occur, particularly compared to non-rectified flow. Advantageously, a particularly linear relationship can be achieved between the current required by the actuator device moving the control valve spool to set a specific position and a set damping stiffness. Advantageously, a virtually linear relationship can be achieved between the current of the actuator device and the set flow cross-section. Advantageously, flow optimization can be achieved.In particular, the implementation as a needle valve is also particularly cost-effective, especially compared to a slide valve, which must have the same advantageous flow properties.

[0030] If the control valve slide has an end region which is formed by a part of the control valve slide which faces an end stop of the control valve unit on which the control valve slide sits in the rest position, wherein the control valve slide is designed to be continuous, preferably linearly continuous, tapered or stepped tapered in the direction of the end stop of the control valve unit, a particularly precise flow cross-section adjustment can advantageously be enabled.

[0031] If, in addition, the control valve spool has at least one bypass channel opening toward a radial circumferential surface of the control valve spool, which bypass channel is arranged at a distance from the conically tapered end region of the control valve spool in the axial direction of the control valve spool, a complete flow through or a complete flow around, or a division of the flow through and flow around components of the total opening cross-section can be advantageously enabled, depending on the position of the control valve spool in the control valve unit. A precise adjustment of the total opening cross-section can advantageously be achieved. Furthermore, a particularly advantageous damping hardness curve can be realized.In particular, the bypass channel forms a fail-safe opening, particularly since a fixed flow through the control valve unit is possible even when the control valve spool rests on the end stop and the control opening of the control valve unit is therefore completely closed. Furthermore, it is proposed that the control valve spool have a central region arranged axially between the end region and an opening of the bypass channel, the extension of which in the axial direction is at least greater than a maximum axial opening cross-section of an opening of an output channel of the control valve unit that corresponds to the opening of the bypass channel, at least in the rest position, and establishes a connection to an output of the control valve unit. Advantageously, a precise adjustment of the total opening cross-section can be achieved. Furthermore, a particularly advantageous damping hardness curve can be realized.In particular, when the bypass channel is just completely closed by the control valve spool being lifted from its end stop, the control opening of the control valve unit is not yet open by the tapered end section of the control valve spool. In particular, this position of the control valve spool forms a minimum damping hardness of the bidirectional damper device.

[0032] If an axial extension of the end region is at least 70%, preferably at least 100%, advantageously at least 120% and preferably less than 180% of an axial extension of the central region, a particularly precise and / or fine adjustment of the damping hardness can advantageously be enabled.

[0033] Furthermore, if a cone angle of the end region of the control valve spool is at most 40°, preferably at most 35°, and preferably at most 30° and / or at least 20°, preferably at least 25°, and preferably at least 30°, a particularly precise and / or fine adjustment of the damping hardness can advantageously be enabled. The cone angle corresponds in particular to twice the convergence angle of a cone. In particular, the end region of the control valve spool forms the cone with the cone angle.

[0034] In addition, it is proposed that an imaginary annular surface formed by a difference between a first surface circumscribed by a cross-section perpendicular to the axial direction of the control valve spool at a beginning of the conical taper of the end region and a second surface circumscribed by a cross-section perpendicular to the axial direction of the control valve spool at an end of the conical taper of the end region be larger than a total area of ​​opening cross-sections of openings of all bypass channels of the control valve spool that are open toward a radial lateral surface of the control valve spool, in particular outside the end region. This makes it possible, in particular, to achieve a particularly advantageous damping hardness curve. Advantageously, at least one operating position of the control valve spool can be achieved in which the damping hardness is lower than in the rest position of the control valve spool (failsafe state).

[0035] Furthermore, a damper, in particular a shock absorber, preferably in a vehicle chassis, with the bidirectional damper device is proposed. This makes it possible to achieve a damper with advantageous damping properties, in particular with a particularly advantageous damping stiffness curve.

[0036] Furthermore, a method for operating the bidirectional damper device, in particular the bidirectional shock absorber device, for example for the vehicle shock absorber, is proposed, wherein the rebound damping hardness and the compression damping hardness are controlled as a function of, in particular specifically adjustable, positions of the control valve spool of the control valve unit, in particular by means of a pilot control of the damper valve spool, which is preferably designed separately from the control valve spool, and wherein, in the damping case, the control valve spool is at least flowed through and / or at least flowed around in the same direction, independently of the activation of a compression stage or a rebound stage. Advantageous hydraulic properties, in particular advantageous flow properties, can thereby be achieved.This advantageously allows for easier and / or better optimization and / or compensation of flow forces, particularly compared to non-unidirectional flow. This can also lead to cost reduction.

[0037] The bidirectional damper device according to the invention, the damper according to the invention, and the method according to the invention are not intended to be limited to the application and embodiment described above. In particular, the bidirectional damper device according to the invention, the damper according to the invention, and the method according to the invention may have a number of individual elements, components, and units that differs from the number stated herein to fulfill a function described herein.

[0038] Drawings

[0039] Further advantages will become apparent from the following description of the drawings. The drawings illustrate two exemplary embodiments of the invention. The drawings, the description, and the claims contain numerous features in combination. Those skilled in the art will also expediently consider the features individually and combine them into useful further combinations.

[0040] They show:

[0041] Fig. 1 a is a schematic hydraulic circuit diagram of a bidirectional damper device of a damper with a control valve unit having a control valve slide when forces to be damped are applied on a tension side of the damper,

[0042] Fig. 1 b is a schematic sectional view of the bidirectional damper device from Fig. 1 a,

[0043] Fig. 2a is a schematic hydraulic circuit diagram of the bidirectional damper device when forces to be damped are applied to a pressure side of the damper, Fig. 2b is a schematic sectional view of the bidirectional damper device from Fig. 2a,

[0044] Fig. 3 a schematic and exemplary diagram of the flow situation in the control valve unit,

[0045] Fig. 4 is a schematic flow diagram of a method for operating the bidirectional damper device,

[0046] Fig. 5a is a schematic sectional view of part of an alternative bidirectional damper device with an alternative control valve unit, the control valve spool being in a rest position,

[0047] Fig. 5b is a schematic sectional view of the part of the alternative bidirectional damper device, wherein the control valve spool is in a first further position,

[0048] Fig. 5c is a schematic sectional view of the part of the alternative bidirectional damper device, wherein the control valve spool is in a second further position and

[0049] Fig. 6 different schematically illustrated opening levels of a control opening at different positions of the control valve spool of the alternative control valve unit.

[0050] Description of the embodiments

[0051] Figures 1a, 1b, 2a, and 2b each show schematic representations of a bidirectional damper device 30a of a damper 106a. In Figures 1a and 1b, a flow path of a pressurized fluid when forces to be damped act on a tension side 28a of the damper 106a is indicated by arrows. In Figures 2a and 2b, a flow path of the pressurized fluid when forces to be damped act on a compression side 26a of the damper 106a is indicated by arrows. In Fig. 1a, the bidirectional damper device 30a of the damper 106a is illustrated in a schematic hydraulic circuit diagram, and in Fig. 1b, the bidirectional damper device 30a of the damper 106a is shown in a schematic cross-sectional drawing. The damper 106a is designed, for example, as a shock absorber in a vehicle. Therefore, the bidirectional damper device 30a is also designed as a bidirectional vehicle shock absorber device.The bidirectional damper device 30a has a control valve unit 12a. The control valve unit 12a has a control valve spool 10a. The bidirectional damper device 30a has a main valve unit 108a. The main valve unit 108a has a damper valve spool 14a. The main valve unit 108a is designed separately from the control valve unit 12a. The damper valve spool 14a is designed separately from the control valve spool 10a. The main valve unit 108a is provided for damping tensile forces and compressive forces by opening / moving the damper valve spool 14a. The damper 106a and / or the bidirectional damper device 30a have the tension side 28a. The damper 106a and / or the bidirectional damper device 30a have the compression side 26a.By opening / closing the damper valve spool 14a, a main pressure fluid path 110a of a pressure fluid flowing through the damper 106a, connecting the pressure side 26a and the tension side 28a, is opened / closed. The damper 106a has a damper housing 136a. The main pressure fluid path 110a extends from a first opening 134a of the damper housing 136a, which is connected to the pressure side 26a of the damper 106a (a pressure reservoir 118a on the pressure side 26a of the damper 106a), to a second opening 138a of the damper housing 136a, which is connected to the tension side 28a of the damper 106a (another pressure reservoir 120a on the tension side 28a of the damper 106a), and vice versa. The flow of the pressure fluid between the pressure side 26a and the tension side 28a creates a damping of an external force acting on the damper 106a.The bidirectional damper device 30a has a reset unit 122a for restoring a compression or rebound deflection of the damper valve spool 14a. The reset unit 122a is designed as a spiral compression spring. However, alternative spring elements are also conceivable. The reset unit 122a is supported by a first end 124a on the damper valve spool 14a. The reset unit 122a is supported by a second end 126a, which is arranged opposite the first end 124a, on a fixed element 128a of the bidirectional damper device 30a. The fixed element 128a forms a flow channel to and from the control valve unit 12a (depending on the open connecting path 22a, 24a). The damper valve spool 14a has an active surface element 44a. The active surface element 44a forms the pressure effective surfaces on which the tensile and compressive forces of the tensile and compressive stages act.The active surface element 44a separates the compression side 26a and the tension side 28a from each other. A first side 130a of the active surface element 44a is connected to the tension side 28a when the rebound stage is activated. The first side 130a of the active surface element 44a is connected to the compression side 26a when the compression stage is activated. A second side 132a of the active surface element 44a is connected to the compression side 26a when the rebound stage is activated. The second side 132a of the active surface element 44a is connected to the tension side 28a when the compression stage is activated. The active surface element 44a is arranged above the two openings 134a, 138a of the damper housing 136a.

[0052] The control valve unit 12a is provided for pilot control of the main valve unit 108a. The control valve unit 12a is provided for pilot control of the damper valve spool 14a. The pilot control occurs as a function of specifically adjustable positions of the control valve spool 10a. The control valve unit 12a is provided for controlling a rebound damping stiffness of the damper 106a via the pilot control. The control valve unit 12a is provided for controlling a compression damping stiffness of the damper 106a via the pilot control. The bidirectional damper device 30a has an actuator device 112a. The actuator device 112a is formed by an electromagnet. The actuator device 112a is provided for a controllable adjustment of the position of the control valve spool 10a in the control valve unit 12a.The control valve unit 12a is provided to adjust, depending on the adjusted position of the control valve spool 10a, an overall size of a minimum flow cross-section of connecting paths 22a, 24a, which hydraulically connect opposite sides 114a, 116a of the damper valve spool 14a, in particular the pressure side 26a and the tension side 28a of the bidirectional damper device 30a.

[0053] The connecting paths 22a, 24a run in the same direction through the control valve spool 10a in all flow-through operating states of the control valve spool 10a. The connecting paths 22a, 24a run in the same direction around the control valve spool 10a in all flow-around operating states of the control valve spool 10a. The connecting paths 22a, 24a all run through a part of the damper valve spool 14a, regardless of whether the compression or rebound stage is activated. The connecting paths 22a, 24a run in opposite directions through a part of the damper valve spool 14a depending on whether the compression or rebound stage is activated. The connecting paths 22a, 24a run through the part of the damper valve spool 14a in different flow areas of the damper valve spool 14a depending on whether the compression or rebound stage is activated.The connecting paths 22a, 24a connect the compression side 26a of the damper 106a, in particular the pressure reservoir 118a on the compression side 26a of the damper 106a, and the rebound side 28a of the damper 106a, in particular the further pressure reservoir 120a on the rebound side 28a of the damper 106a, which is separate from the pressure reservoir 118a on the compression side 26a. Depending on the activation of the rebound stage or the compression stage, one of the connecting paths 22a, 24a is open, while the other is closed. In no operating state are both connecting paths 22a, 24a open simultaneously. When the rebound stage is activated, the first connecting path 22a is open and the second connecting path 24a is closed. When the compression stage is activated, the first.

[0054] Connecting path 22a closed and the second connecting path 24a opened.

[0055] In Figures 1b and 2b, the control valve spool 10a is shown in a rest position 58a. The control valve unit 12a has an end stop 16a. In the rest position 58a of the control valve spool 10a, the control valve spool 10a sits on the end stop 16a of the control valve unit 12a. The end stop 16a has extensions 154a that protrude in the direction of the control valve spool 10a from the element forming the end stop 16a. In the rest position 58a of the control valve spool 10a, the control valve spool 10a sits on the extensions 154a of the end stop 16a. The rest position 58a of the control valve spool 10a forms a fail-safe position of the control valve unit 12a. When the actuator device 112a is deactivated, the control valve spool 10a assumes the rest position 58a. When the actuator device 112a is (sufficiently) energized, the control valve spool 10a is lifted from the end stop 16a.In the fail-safe position of the control valve unit 12a, a rebound damping stiffness of the damper 106a is automatically set, which differs from a minimum rebound damping stiffness adjustable by the control valve unit 12a. In the fail-safe position of the control valve unit 12a, a rebound damping stiffness of the damper 106a is automatically set, which differs from a maximum rebound damping stiffness adjustable by the control valve unit 12a. In the fail-safe position of the control valve unit 12a, a compression damping stiffness of the damper 106a is automatically set, which differs from a maximum compression damping stiffness adjustable by the control valve unit 12a. In the fail-safe position of the control valve unit 12a, a compression damping hardness of the damper 106a is automatically set, which is different from a minimum compression damping hardness adjustable by the control valve unit 12a.See also curve 68a in Fig. 3. The end stop 16a has a flow channel 18a. The control valve spool 10a is designed to allow flow through. The control valve spool 10a forms at least one flow path for the flow through the control valve spool 10a. The flow path through the control valve spool 10a has at least one curve / bend. The control valve spool 10a has a flow inlet 20a. In the rest position 58a of the control valve spool 10a, the flow channel 18a of the end stop 16a is open to the flow inlet 20a of the control valve spool 10a. The flow channel 18a of the end stop 16a is open to the flow inlet 20a of the control valve spool 10a in every possible operating position of the control valve spool 10a. The flow channel 18a is arranged eccentrically in the end stop 16a. The end stop 16a can have additional flow channels.

[0056] The control valve unit 12a is designed such that the control valve slide 10a is flowed through and / or flowed around in the same direction in the damping case, regardless of the activation of a compression stage or a rebound stage (see, among other things, the comparison of the two flow paths designated as connecting paths 22a, 24a for the compression stage and the rebound stage in Figures 1b and 2b).

[0057] The bidirectional damper device 30a has a first rebound check valve 32a. The first rebound check valve 32a is arranged in the rebound connection path 22a. The first rebound check valve 32a is provided to open a connection from the rebound side 28a to an inlet 34a of the control valve unit 12a when a force to be damped is applied to the rebound side 28a. The first rebound check valve 32a is provided to close a connection from the rebound side 28a to the inlet 34a of the control valve unit 12a when the force to be damped is applied to the compression side 26a. In the illustrated case, the first rebound check valve 32a is at an opening 140a of the damper housing 136a, which connects the pressure reservoir 120a of the rebound side 28a with a cavity 142a of the bidirectional damper device 30a connected to the inlet 34a of the control valve unit 12a.The cavity 142a is arranged between the damper housing 136a and an outer side of the control valve unit 12a. The inlet 34a of the control valve unit 12a connects the cavity 142a to an interior 144a of the control valve unit 12a, which is arranged on a side of the end stop 16a facing away from the control valve spool 10a and is bounded on at least one side by the end stop 16a. The inlet 34a forms an inlet of a channel 146a connecting the cavity 142a to the interior 144a. The cavity 142a is at least partially bounded by the first side 130a of the active surface element 44a.

[0058] The bidirectional damper device 30a has a second rebound check valve 36a. The second rebound check valve 36a is arranged in the rebound connection path 22a. The second rebound check valve 36a is provided to open a connection from a first output 38a of the control valve unit 12a to the compression side 26a when a force to be damped is applied to the rebound side 28a. The second rebound check valve 36a is provided to close a connection from the compression side 26a to the first output 38a of the control valve unit 12a when the force to be damped is applied to the compression side 26a. In the illustrated case, the second rebound check valve 36a is arranged on the fixed element 128a, which forms a guide channel extending through the damper valve spool 14a from the control valve unit 12a to the pressure side 26a.

[0059] The bidirectional damper device 30a has a first compression-stage check valve 40a. The first compression-stage check valve 40a is arranged in the compression-stage connection path 24a. The first compression-stage check valve 40a is provided to open a connection from the compression side 26a to the inlet 34a of the control valve unit 12a when a force to be damped acts on the compression side 26a. The first compression-stage check valve 40a is provided to close a connection from the compression side 26a to the inlet 34a of the control valve unit 12a when the force to be damped acts on the tension side 28a. The first compression-stage check valve 40a is arranged on a side of the damper valve spool 14a that faces away from the control valve unit 12a.The pressure stage connecting path 24a extends in the region between the first pressure stage check valve 40a and the inlet 34a of the control valve unit partially through an interior space 148a of the damper valve spool 14a. The pressure stage connecting path 24a extends in the region between the first pressure stage check valve 40a and the inlet 34a of the control valve unit 12a partially through the cavity 142a.

[0060] The bidirectional damper device 30a has a second compression-stage check valve 42a. The second compression-stage check valve 42a is arranged in the compression-stage connection path 24a. The second compression-stage check valve 42a is provided to open a connection from a second output 46a of the control valve unit 12a to the tension side 28a when the force to be damped acts on the compression side 26a. The second compression-stage check valve 42a is provided to close a connection from the tension side 28a to the second output 46a of the control valve unit 12a when the force to be damped acts on the tension side 28a. In the illustrated case, the second compression stage check valve 42a is at an opening 150a of the damper housing 136a, which connects the pressure reservoir 120a of the tension side 28a with a further cavity 152a of the bidirectional damper device 30a connected to the second output 46a of the control valve unit 12a.The further cavity 152a is arranged between the damper housing 136a and an outer side of the control valve unit 12a. The second outlet 46a of the control valve unit 12a connects the further cavity 152a to an outlet channel 88a of the control valve unit 12a, which is arranged on a side of the end stop 16a facing the control valve spool 10a. The second outlet 46a forms an outlet of the outlet channel 88a connecting the control valve spool 10a to the further cavity 152a. The further cavity 152a is at least partially delimited by the second side 132a of the active surface element 44a.

[0061] In all flow-through operating states, in which the pressure fluid flowing through the control valve unit 12a flows completely or partially through the control valve spool 10a, the flow is exclusively from the inside to the outside. In all flow-through operating states, the flow is exclusively from the inside to the outside through the control valve spool 10a, regardless of the activation of a compression or rebound stage. Furthermore, in those operating states in which there is flow through the control valve unit 12a and in which, at the same time, a minimum rebound damping stiffness or a minimum compression damping stiffness is set by means of the control valve unit 12a, the flow through the control valve spool 10a is completely free of any flow through the pressure fluid of the damper 106a.

[0062] The control valve spool 10a has a bypass channel 56a. The bypass channel 56a forms an outlet channel for the pressurized fluid flowing out of the control valve spool 10a during flow. The control valve spool 10a can have a plurality of bypass channels 56a, each of which, in particular, fulfills the same function. The control valve spool 10a has a movement axis 48a. During positioning, the control valve spool 10a is moved (up and down) along the movement axis 48a by means of the actuator device 112a. In the illustrated case, the bypass channel 56a runs perpendicular to the movement axis 48a of the control valve spool 10a. The control valve spool 10a has the flow inlet 20a. The flow inlet 20a of the control valve spool 10a is arranged on a side of the control valve spool 10a facing the end stop 16a, in particular on a side of the control valve spool 10a facing an outlet opening of the flow channel 18a of the end stop 16a.The flow inlet 20a forms an opening plane 52a. In the illustrated case, the bypass channel 56a runs perpendicular to a normal 50a of the opening plane 52a of the flow inlet 20a of the control valve spool 10a. The bypass channel 56a is arranged in the control valve spool 10a such that, in the rest position 58a of the control valve spool 10a, the bypass channel 56a is open to the first outlet 38a of the control valve unit 12a connected to the pressure side 26a or to the second outlet 46a of the control valve unit 12a connected to the tension side 28a, depending on the pressure conditions in the damper 106a.

[0063] The bypass channel 56a has an opening 64a. The opening 64a forms a flow outlet of the control valve spool 10a. The opening 64a of the bypass channel 56a is arranged in the control valve spool 10a such that when the control valve spool 10a is deflected from the rest position 58a (along the movement axis 48a), a portion of the opening cross-section of the opening 64a of the bypass channel 56a, which is connected to the first outlet 38a or to the second outlet 46a depending on the pressure situation in the damper 106a, decreases in size. The control valve unit 12a has a control opening 66a. The control opening 66a is completely closed by the control valve spool 10a in the rest position 58a. The control opening 66a opens partially when the control valve slide 10a is moved sufficiently far away from the end stop 16a along the movement axis 48a.The control opening 66a can be fully open in at least one position of the control valve spool 10a along the movement axis 48a. When the control opening 66a is partially or fully open, a pressure fluid connection exists between the inlet 34a of the control valve unit 12a and the first outlet 38a or the second outlet 46a (depending on the pressure situation in the damper 106a), which is free of flow through the control valve spool 10a and / or flows around the control valve spool 10a.The control valve spool 10a is designed such that, over at least part of a deflection movement which the control valve spool 10a experiences when deflected from the rest position 58a (along the movement axis 48a), a total opening cross-section of the control valve spool 10a, which is composed of the opening cross-sectional part of the opening 64a of the bypass channel 56a connected to the first outlet 38a or to the second outlet 46a depending on the pressure situation in the damper 106a and a further opening cross-section of the control opening 66a of the control valve unit 12a resulting from the lifting of the control valve spool 10a from an end stop 16a of the control valve unit 12a / by the displacement of the control valve spool 10a along the movement axis 48a in a direction away from the end stop 16a, is reduced.The total opening cross-section of the control valve unit 12a is composed of all openings of the control valve unit 12a that currently permit a flow of pressurized fluid and that connect the tension side 28a and the compression side 26a of the bidirectional damper device 30a. The total opening cross-section of the control valve unit 12a is larger in at least one operating position of the control valve spool 10a that differs from the rest position 58a than in the rest position 58a. The total opening cross-section of the control valve unit 12a is smaller in at least one operating position of the control valve spool 10a that differs from the rest position 58a than in the rest position 58a.

[0064] Figure 3 shows a schematic and exemplary diagram 72a of the flow situation in the control valve unit 12a. The total opening cross-section of the control valve unit 12a is shown on an abscissa 60a of the diagram 72a. A distance 178a (cf. Fig. 5c) of the control valve spool 10a from the rest position 58a along the movement axis 48a is shown on an ordinate 62a of the diagram 72a. Curve 68a is plotted in the diagram 72a. Using curve 68a, the total opening cross-section of the control valve unit 12a is plotted against the distance 178a of the control valve spool 10a from the rest position 58a. The curve 68a has a global minimum 70a.

[0065] Figure 4 shows a schematic flow diagram of a method for operating the bidirectional damper device 30a, wherein the rebound damping stiffness and the compression damping stiffness are controlled by means of a pilot control of the damper valve spool 14a as a function of specifically adjustable positions of the control valve spool 10a. In the method, in the damping case, the flow through and / or around the control valve spool 10a is uniformly directed, regardless of activation of the compression stage or the rebound stage. In at least one method step 156a, the control valve spool 10a is positioned in the rest position 58a. In the rest position 58a, in the damping case, the pressurized fluid passing through the control valve unit 12a flows completely through the control valve spool 10a, regardless of activation of the compression stage or the rebound stage.The pressurized fluid enters the control valve spool 10a through the flow inlet 20a, passes through the bypass channel 56a(s) of the control valve spool 10a, and exits from the opening 64a of the bypass channel 56a into a connecting channel unit 158a of the control valve unit 12a, which is connected to the first outlet 38a and the second outlet 46a. In method step 156a, the control opening 66a is completely closed by the control valve spool 10a.

[0066] In at least one further method step 160a, the control valve spool 10a is positioned in a second position 162a (see Fig. 3), in which the control valve spool 10a is lifted from the end stop 16a, but in which the control opening 66a remains closed by the control valve spool 10a. In the second position 162a, the flow pattern of the pressure fluid is essentially identical to the flow pattern of the pressure fluid in the rest position 58a, except for a lower overall flow due to a reduction in the overall opening cross-section when the control valve spool 10a is lifted. In at least one further method step 164a, the control valve spool 10a is positioned in a third position 166a (see Fig. 3), in which the control valve spool 10a is lifted further from the end stop 16a than in the second position 162a. In the third position 166a, the control valve spool 10a is neither flowed through nor around.Alternatively, in the third position 166a, the flow pattern of the pressurized fluid could be substantially identical to the flow pattern of the pressurized fluid in the rest position 58a or in the second position 162a, merely with an even lower total flow than in the second position 162a due to a further reduction of the total opening cross-section upon further lifting of the control valve spool 10a. In the third position 166a, the total flow is the lowest of all possible positions of the control valve spool 10a. In at least one further method step 168a, the control valve spool 10a is positioned in a fourth position 170a (see Fig. 3), in which the control valve spool 10a is lifted further from the end stop 16a than in the third position 166a.In the fourth position 170a, the flow pattern of the pressurized fluid is different from the flow pattern of the pressurized fluid in the rest position 58a or in the second position 162a or in the third position 166a. In the fourth position 170a, the control opening 66a is partially open. As a result, the total flow is again higher than in the third position 166a. Nevertheless, the total flow is still lower than in the rest position 58a. In at least one further method step 172a, the control valve spool 10a is positioned in a fifth position 174a (see Fig. 3), in which the control valve spool 10a is lifted further from the end stop 16a than in the fourth position 170a. In the fifth position 174a, the flow pattern of the pressurized fluid is essentially identical to the flow pattern of the pressurized fluid in the fourth position 170a. In the fifth position 174a, the control opening 66a is wider open than in the fourth position 170a.This makes the total flow even higher than in the fourth position 170a. The total flow in the fifth position 174a is also higher than in the rest position 58a. The rebound damping stiffness / compression damping stiffness depends on the total flow through the control valve unit 12a. The greater the total flow through the control valve unit 12a, the softer the rebound damping stiffness / compression damping stiffness of the damper 106a. The smaller the total flow through the control valve unit 12a, the softer the rebound damping stiffness / compression damping stiffness of the damper 106a. In at least one further method step 176a, the damper 106a is operated with one of the positions 58a, 162a, 166a, 170a, 174a set in the previous method steps 156a, 160a, 164a, 168a, 172a.In method step 176a, the damper valve slide 14a is pre-controlled by the correspondingly adjusted control valve unit 12a.

[0067] Figures 5a to 6 show a further embodiment of the invention. The following descriptions and the drawings are essentially limited to the differences between the embodiments, whereby with regard to components with the same designation, in particular with regard to components with the same reference numerals, reference can in principle also be made to the drawings and / or the description of the other embodiments, in particular Figures 1 to 4. To distinguish the embodiments, the letter a is placed after the reference numerals of the embodiment in Figures 1 to 4. In the embodiments of Figures 5a to 6, the letter a is replaced by the letter b.

[0068] Figures 5a to 5c each show a schematic sectional view of a portion of an alternative bidirectional damper device 30b. The alternative bidirectional damper device 30b has an alternative control valve unit 12b. The control valve unit 12b has a control valve spool 10b. The alternative control valve unit 12b is designed as a needle valve. The control valve spool 10b has an end region 74b. The end region 74b is formed by the portion of the control valve spool 10b that faces an end stop 16b of the alternative control valve unit 12b, on which end stop the control valve spool 10b rests in a rest position 58b of the control valve spool 10b. The control valve spool 10b is designed to taper linearly and continuously in the direction of the end stop 16b in the end region 74b.Alternatively, a stepped conical taper or a non-linear, continuous taper of the control valve spool 10b in the end region 74b toward the end stop 16b is also conceivable. Parts of the control valve spool 10b that project beyond the conically tapered end region 74b in an axial direction 78b of the control valve spool 10b do not necessarily have a negative effect on the function of the control valve spool 10b. Such a configuration can therefore be considered equivalent. The control valve spool 10b forms a conical taper 100b in the end region 74b.

[0069] The control valve spool 10b has a radial outer surface 76b. The radial outer surface 76b surrounds at least a portion of the control valve spool 10b in a circumferential direction radial to a movement axis 48b of the control valve spool 10b. The radial outer surface 76b forms a cylindrical surface portion of the control valve spool 10b. The control valve spool 10b has a bypass channel 56b. The bypass channel 56b is open toward the radial outer surface 76b of the control valve spool 10b. The bypass channel 56b is arranged at a distance from the conically tapered end region 74b of the control valve spool 10b in the axial direction 78b of the control valve spool 10b. The cylindrical surface portion formed by the radial surface 76b of the control valve spool 10b is spaced apart from the conically tapered end portion 74b of the control valve spool 10b. The control valve spool 10b has a central portion 80b.The central region 80b is arranged axially between the end region 74b and an opening 64b of the bypass channel 56b arranged on a radial outer periphery of the control valve spool 10b. An extension 82b of the central region 80b parallel to the axial direction 78b of the control valve spool 10b is larger than a maximum axial opening cross-section 84b of an opening 86b of an output channel 88b of the control valve unit 12b, which opening corresponds to the opening 64b of the bypass channel 56b, at least in the rest position 58b of the control valve spool 10b, and establishes a connection to an output 38b, 46b of the control valve unit 12b.

[0070] The end region 74b has an axial extension 90b. The axial extension 90b of the end region 74b is at least 100% of the axial extension 82b of the central region 80b. The control valve spool 10b has a cone angle 92b in the end region 74b. The cone angle 92b of the end region 74b of the control valve spool 10b is at most 35°. The cone angle 92b of the end region 74b of the control valve spool 10b is at least 25°. An imaginary annular surface 94b (cf. Fig.6), which is formed by a difference between a first area, which is circumscribed by a cross section 96b perpendicular to the axial direction 78b of the control valve spool 10b at a start 98b of the conical taper 100b of the end region 74b, and a second area, which is circumscribed by a cross section 102b perpendicular to the axial direction 78b of the control valve spool 10b at an end 104b of the conical taper 100b of the end region 74b, is larger than a total area of ​​opening cross sections of openings 86b of all bypass channels 56b of the control valve spool 10b that are open towards the radial jacket surface 76b of the control valve spool 10b, in particular outside the end region 74b.

[0071] Figures 5a to 5c show the control valve spool 10b of the alternative control valve unit 12b in different positions. In Fig. 5a, the control valve spool 10b is shown in the rest position 58b. Flow can pass through the control valve spool 10b, and a control opening 66b of the alternative control valve unit 12b is closed. Thus, flow cannot pass around the control valve spool 10b. In Fig. 5b, the control valve spool 10b is arranged in a position 166b, which corresponds to the third position 166a of method step 164a from Fig. 4. Flow cannot pass through the control valve spool 10b in this position 166b. The control opening 66b is closed. Flow cannot pass around the control valve spool 10b in this position 166b. In Figure 5c, the control valve slide 10b is arranged in a position 170b, which corresponds to the fourth position 170a of the method step 168a from Figure 4.In this position 170b, no flow passes through the control valve spool 10b. The control opening 66b is open. Flow passes around the control valve spool 10b in this position 170b. In this case, an opening plane of the control opening 66b defines the annular surface 94b. The parts of connecting paths 22b, 24b shown as examples in Figures 5a to 5c are identical for tension damping and compression damping.

[0072] Figure 6 shows various schematically illustrated opening planes of the control opening 66b at different positions of the control valve spool 10b in the alternative control valve unit 12b. Viewed from left to right, Fig. 6 shows the opening planes of the annular surfaces 94b, 94'b, 94"b, 94"'b, which arise when the control valve spool 10b is increasingly moved away from the end stop 16b and is also located above the position 166b, which corresponds to the third position 166a of method step 164a from Fig. 4. The size of the annular surfaces 94b, 94'b, 94"b, 94"'b has an approximately linear relationship to a stroke of the control valve spool 10b (to a distance 178b of the control valve spool 10b from the end stop 16b).By selecting the cone angle 92b of the taper 100b of the end region 74b of the control valve slide 10b, the course of the enlargement / reduction of the annular surfaces 94b when adjusting the control valve slide 10b can be adjusted to optimize the curve 68a shown in Fig. 3 or flow forces or flows within the alternative control valve unit 12b.

[0073] Reference symbol

[0074] 10 control valve spools

[0075] 12 Control valve unit

[0076] 14 damper valve slide

[0077] 16 End stop

[0078] 18 flow channel

[0079] 20 Flow inlet

[0080] 22 Connection path

[0081] 24 Connection path

[0082] 26 printed pages

[0083] 28 train side

[0084] 30 Bidirectional damper device

[0085] 32 First rebound check valve

[0086] 34 Entrance

[0087] 36 Second rebound check valve

[0088] 38 First Exit

[0089] 40 First pressure stage check valve

[0090] 42 Second pressure stage check valve

[0091] 44 Effective surface element

[0092] 46 Second Exit

[0093] 48 Movement axis

[0094] 50 Normal

[0095] 52 opening level

[0096] 56 Bypass channel

[0097] 58 Resting position

[0098] 60 abscissa

[0099] 62 ordinates

[0100] 64 Opening

[0101] 66 Standard opening

[0102] 68 Curve Minimum Diagram End area Shell surface Axial direction Middle area Extension

[0103] Axial opening cross-section Opening Outlet channel Extension Cone angle Annular area Cross-section start Taper Cross-section end Damper Main valve unit Pressure fluid main path Actuator device Side Side Pressure reservoir

[0104] Additional pressure reservoir Reset unit First end Second end Fixed element First side Second side First opening Damper housing Second opening Opening Cavity

[0105] Interior

[0106] channel

[0107] Interior

[0108] opening

[0109] Additional cavity

[0110] appendage

[0111] Process step

[0112] Connecting channel unit process step

[0113] Second position

[0114] Process step

[0115] Third position

[0116] Process step

[0117] Fourth position

[0118] Process step

[0119] Fifth position

[0120] Process step removal

Claims

Claims 1. Bidirectional damper device (30a-b), in particular bidirectional shock absorber device, for example for a vehicle shock absorber, with a control valve unit (12a-b) having at least one control valve spool (10a-b) for controlling a rebound damping hardness and for controlling a compression damping hardness, in particular by means of a pilot control of a damper valve spool (14a-b), preferably designed separately from the control valve spool (10a-b), as a function of, in particular specifically adjustable, positions of the control valve spool (10a-b), characterized in that the control valve unit (12a-b) is designed such that the control valve spool (10a-b) is flowed through and / or at least flowed around in the same direction in the damping case, regardless of an activation of a compression stage or a rebound stage.

2. Bidirectional damper device (30a-b) according to claim 1, characterized in that the control valve slide (10a-b) in a rest position (58a-b) sits on an end stop (16a-b) of the control valve unit (12a-b), wherein the end stop (16a-b) has a flow channel (18a-b) which in the rest position (58a-b) is open to a flow inlet (20a-b) of the control valve slide (10a-b).

3. Bidirectional damper device (30a-b) according to claim 1 or 2, characterized in that the rest position (58a-b) of the control valve slide (10a-b) forms a fail-safe position of the control valve unit (12a-b).

4. Bidirectional damper device (30a-b) according to claim 3, characterized in that in the fail-safe position of the control valve unit (12a-b) a rebound damping hardness is set which is different from a minimum rebound damping hardness adjustable by the control valve unit and from a maximum rebound damping hardness adjustable by the control valve unit (12a-b), and / or that in the fail-safe position of the control valve unit (12a-b) a compression damping hardness is set which is different from a minimum compression damping hardness adjustable by the control valve unit (12a-b) and from a maximum compression damping hardness adjustable by the control valve unit (12a-b).

5. Bidirectional damper device (30a-b) according to one of the preceding claims, characterized in that the control valve unit (12a-b) is provided to adjust, depending on the set position of the control valve spool (10a-b), an overall size of a minimum flow cross-section of connecting paths (22a-b, 24a-b) which connect opposite sides of the damper valve spool (14a-b), in particular a pressure side (26a-b) and a tension side (28a-b) of the bidirectional damper device (30a-b), preferably hydraulically.

6. Bidirectional damper device (30a-b) according to claim 5, characterized in that the connecting paths (22a-b, 24a-b), in particular independently of an activation of the compression stage or the rebound stage, preferably all, run through the damper valve slide (14a-b).

7. Bidirectional damper device (30a-b) according to one of claims 5 or 6, characterized by a first rebound stage check valve (32a-b) arranged in at least some of the connecting paths (22a-b, 24a-b), preferably in the rebound stage connecting paths (22a-b), which is provided for Activation of the rebound stage, in particular when a force to be damped acts on a tension side (28a-b) of the bidirectional damper device (30a-b), to open a connection from the tension side (28a-b) to an inlet (34a-b) of the control valve unit (12a-b) and when activation of the compression stage, in particular when the force to be damped acts on a compression side (26a-b) of the bidirectional damper device (30a-b), to close a connection from the tension side (28a-b) to the inlet (34a-b) of the control valve unit (12a-b).

8. Bidirectional damper device (30a-b) according to claim 7, characterized by a second rebound stage check valve (36a-b) arranged in at least some of the connecting paths (22a-b, 24a-b), preferably in the rebound stage connecting paths (22a-b), which is provided to open a connection from a first output (38a-b) of the control valve unit (12a-b) to the compression side (26a-b) of the bidirectional damper device (30a-b) upon activation of the rebound stage, in particular upon application of the force to be damped on the compression side (28a-b) of the bidirectional damper device (30a-b), and to open a connection from the compression side (26a-b) to the first output (38a-b) of the control valve unit (12a-b).

9. Bidirectional damper device (30a-b) according to one of claims 5 to 8, characterized by a first compression stage check valve (40a-b) arranged in at least some of the connecting paths (22a-b, 24a-b), preferably in the compression stage connecting paths (24a-b), which is provided to open a connection from the compression side (26a-b) to an inlet (34a-b) of the control valve unit (12a-b) upon activation of the compression stage, in particular upon application of a force to be damped on a compression side (26a-b) of the bidirectional damper device (30a-b), and to open a connection from the compression side (26a-b) to the inlet (34a-b) of the control valve unit upon activation of the rebound stage, in particular upon application of the force to be damped on a rebound side (28a-b) of the bidirectional damper device (30a-b) (12a-b) to close.

10. Bidirectional damper device (30a-b) according to claim 9, characterized by a second compression stage check valve (42a-b) arranged in at least some of the connecting paths (22a-b, 24a-b), preferably in the compression stage connecting paths (24a-b), which is provided to open a connection from a second output (46a-b) of the control valve unit (12a-b) to the tension side (28a-b) of the bidirectional damper device (30a-b) upon activation of the compression stage, in particular upon application of the force to be damped on the compression side (26a-b) of the bidirectional damper device (30a-b), and to open a connection from the tension side (28a-b) to the second output upon activation of the rebound stage, in particular upon application of the force to be damped on the tension side (28a-b) of the bidirectional damper device (30a-b) (46a-b) of the control valve unit (12a-b).

11. Bidirectional damper device (30a-b) according to one of the preceding claims, characterized in that the control valve slide (10a-b) is flowed through exclusively from the inside to the outside in a flow-through operating state, regardless of an activation of a compression stage or a rebound stage.

12. Bidirectional damper device (30a-b) according to one of the preceding claims, characterized in that in operating states in which there is a flow through the control valve unit (12a-b) and in which at the same time a minimum rebound damping hardness or a minimum compression damping hardness is set, the control valve slide (10a-b) is completely free of flow.

13. Bidirectional damper device (30a-b) according to one of the preceding claims, characterized in that the control valve slide (10a-b) has at least one bypass channel (56a-b), which runs in particular obliquely or perpendicularly to a movement axis (48a-b) of the control valve slide (10a-b) and / or obliquely or perpendicularly to a normal (50a-b) of an opening plane (52a-b) of a flow inlet (20a-b) of the control valve slide (10a-b), which bypass channel is arranged in the control valve slide (10a-b) in such a way that, in the rest position (58a-b) of the control valve slide (10a-b), it leads to a first outlet (38a-b) of the control valve unit (12a-b) connected to a pressure side (26a-b) of the bidirectional damper device (30a-b) and / or to a first outlet (38a-b) of the control valve unit (12a-b) connected to a tension side (28a-b) of the bidirectional damper device (30a-b) connected second output (46a-b) of the control valve unit (12a-b) is open.

14. Bidirectional damper device (30a-b) according to claim 13, characterized in that at least one opening (64a-b) of the bypass channel (56a-b) is arranged in the control valve slide (10a-b) in such a way that when the control valve slide (10a-b) is deflected from the rest position (58a-b), an opening cross-sectional part of the opening (64a-b) of the bypass channel (56a-b) connected to the first outlet (38a-b) and / or to the second outlet (46a-b) decreases in size.

15. Bidirectional damper device (30a-b) according to claim 14, characterized in that the control valve slide (10a-b) is designed such that over at least part of a deflection movement which the control valve slide (10a-b) experiences when deflected from the rest position (58a-b), a total opening cross-section which is composed of the opening cross-sectional part of the opening (64a-b) of the bypass channel (56a-b) connected to the first outlet (38a-b) and / or to the second outlet (46a-b) and a further opening cross-section of a control opening (66a-b) of the control valve unit (12a-b) resulting from the lifting of the control valve slide (10a-b) from an end stop (16a-b) of the control valve unit (12a-b), is reduced.

16. Bidirectional damper device (30a-b) according to one of the preceding claims, in particular according to claim 15, characterized in that a curve (68a-b) by means of which a total opening cross-section of the control valve unit (12a-b) connecting a tension side (28a-b) of the bidirectional damper device (30a-b) and a pressure side (26a-b) of the bidirectional damper device (30a-b) is plotted over a distance (178a-b) of the control valve spool (10a-b) from the rest position (58a-b) has a global minimum (70a-b).

17. Bidirectional damper device (30a-b) according to one of the preceding claims, in particular according to claim 15 or 16, characterized in that a total opening cross-section of the control valve unit (12a-b) connecting a tension side (28a-b) of the bidirectional damper device (30a-b) and a pressure side (26a-b) of the bidirectional damper device (30a-b) is larger in at least one operating position of the control valve slide (10a-b) different from the rest position (58a-b) than in the rest position (58a-b).

18. Bidirectional damper device (30b) according to the preamble of claim 1, in particular according to one of the preceding claims, characterized in that the control valve unit (12b) is designed as a needle valve.

19. Bidirectional damper device (30b) according to claim 18, characterized in that the control valve slide (10b) has an end region (74b) which is formed by a part of the control valve slide (10b) which faces an end stop (16b) of the control valve unit (12b), on which stop the control valve slide (10b) rests in the rest position (58b), wherein the control valve slide (10b) is designed to taper continuously, preferably linearly continuously, or in a stepped conical manner in the direction of the end stop (16b) of the control valve unit (12b).

20. Bidirectional damper device (30b) according to claim 19, characterized in that the control valve slide (10b) has at least one bypass channel (56b) open towards a radial jacket surface (76b) of the control valve slide (10b), which bypass channel is arranged at a distance in the axial direction (78b) of the control valve slide (10b) from the conically tapered end region (74b) of the control valve slide (10b).

21. Bidirectional damper device (30b) according to claim 20, characterized in that the control valve spool (10b) has a central region (80b) arranged axially between the end region (74b) and an opening (64b) of the bypass channel (56b), the extension (82b) of which central region in the axial direction (78b) of the control valve spool (10b) is at least greater than a maximum axial opening cross-section (84b) of an opening (86b) of an output channel (88b) of the control valve unit (12b) which corresponds to the opening (64b) of the bypass channel (56b) at least in the rest position (58b) of the control valve spool (10b) and establishes a connection to an output (38b, 46b) of the control valve unit (12b).

22. Bidirectional damper device (30b) according to claim 21, characterized in that an axial extension (90b) of the end region (74b) is at least 70%, preferably at least 100%, advantageously at least 120% and preferably less than 180% of an axial extension (82b) of the central region (80b).

23. Bidirectional damper device (30b) according to one of claims 19 to 22, characterized in that a cone angle (92b) of the end region (74b) of the control valve slide (10b) is at most 40°, preferably at most 35° and preferably at most 30°.

24. Bidirectional damper device (30b) according to one of claims 19 to 23, characterized in that a cone angle (92b) of the end region (74b) of the control valve slide (10b) is at least 20°, preferably at least 25° and preferably at least 30°.

25. Bidirectional damper device (30b) according to one of claims 19 to 24, characterized in that an imaginary annular surface (94b), which is formed by a difference between a first surface, which is circumscribed by a cross-section (96b) perpendicular to the axial direction (78b) of the control valve slide (10b) at a beginning (98b) of the conical taper (100b) of the end region (74b), and a second surface, which is circumscribed by a cross-section (102b) perpendicular to the axial direction (78b) of the control valve slide (10b) at an end (104b) of the conical taper (100b) of the end region (74b), is larger than a total area of ​​opening cross-sections of openings (86b) of all, in particular outside the end region (74b), to a radial lateral surface (76b) of the control valve slide (10b) open bypass channels (56b) of the control valve slide (10b).

26. Damper (106a-b), in particular shock absorber, preferably in a vehicle, with a bidirectional damper device (30a-b) according to one of claims 1 to 25.

27. Method for operating a bidirectional damper device (30a-b), in particular a bidirectional shock absorber device, for example for a vehicle shock absorber, preferably according to one of claims 1 to 25, wherein a rebound damping hardness and a compression damping hardness are controlled as a function of, in particular specifically adjustable, positions of a control valve spool (10a-b) of a control valve unit (12a-b), in particular by means of a pilot control of a damper valve spool (14a-b), which is preferably designed separately from the control valve spool (10a-b), characterized in that the control valve spool (10a-b) is at least flowed through and / or at least flowed around in the same direction in the damping case, independently of an activation of a compression stage or a rebound stage.

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