DE102019003604B4 - Switchable hydro bearing - Google Patents

Abstract

Switchable hydraulic bearing (1), having: a first fluid chamber (2) which is partially delimited by a spring body (4), a second fluid chamber (10) which is connected via a fluid channel (16) and a bypass channel (20) to the first fluid chamber (2) is fluidically connected, so that when the spring body (4) compresses or expands, a damping fluid can flow between the two fluid chambers (2, 10), and a switchable valve (41) with which the bypass channel ( 20) can be opened or closed in order to change a damping characteristic of the switchable hydraulic bearing (1), the switchable valve (41) having a valve housing (22) and a slide (30), the valve housing (22) having: a valve chamber (24) which at least partially forms the bypass channel (20), an axial valve opening (26) which fluidly connects the valve chamber (24) to the first fluid chamber (2) or the second fluid chamber (10), and at least one radial valve opening (28) showing the valve chamber (24) fluidly connects to the other of the first fluid chamber (2) or the second fluid chamber (10), wherein an opening area projected in the axial direction (Ax) of the spool (30) of the radial valve opening (28) on one side of the valve chamber (24) is approximately equal to zero, the spool (30) being disposed entirely in the valve chamber (24) and in the valve chamber (24) between an open position in which the axial valve port (26) and the radial valve port (28) are opened, and a closed position in which the radial valve opening (28) is closed by a radial outer surface of the slide (30), and wherein the slide (30) is at least partially designed as a permanent magnet or contains ferromagnetic material and wherein the slide (30) for Moving the slide (30) interacts with a magnetic coil (40).

Description

The invention relates to a switchable hydraulic mount for essentially vibration-decoupling mounting of a component, in particular of an engine, for example for a motor vehicle.

Switchable hydraulic mounts of this type are used for component mounting with different damping characteristics, between which it is possible to switch. For example, the switchable hydraulic mount should have a different damping characteristic when the component to be mounted vibrates with a first amplitude and/or frequency than when it vibrates with a second amplitude and/or frequency.

the DE 10 2016 110 703 A1 discloses a hydraulic bearing, in particular for mounting a motor vehicle engine on a vehicle body, with a suspension spring that supports a bearing core and encloses a working chamber, and a compensation chamber that is separated from the working chamber by an intermediate plate and delimited by a compensation membrane, the compensation chamber and the Working chamber filled with a liquid and connected to one another in a liquid-conducting manner via a damping channel arranged in the intermediate plate and via a bypass channel, which is assigned a switchable valve. The valve is arranged on the side of the working chamber and can be switched by means of an electromagnet.

the DE 10 2014 224 244 A1 discloses a hydraulic mount for force transmission in a longitudinal direction L of the hydraulic mount, having an elastic suspension spring, a working chamber which is at least partially surrounded by the suspension spring and is filled with a hydraulic fluid, a compensation chamber, a throttle channel formed between the working chamber and the compensation chamber for exchanging hydraulic fluid, a bypass channel formed between the working chamber and the compensation chamber for the exchange of hydraulic fluid, and a valve assigned to the bypass channel with at least one blocking means for blocking or opening the bypass channel, wherein the blocking means is mounted in such a way that the blocking means for blocking or opening the bypass channel runs transversely to a Flow direction of the bypass channel can be moved on the valve. In addition, the invention relates to a vehicle with such a hydraulic bearing.

FR 2 914 035 A1 discloses a hydraulic anti-vibration mount, the mount comprising: two rigid anchors attached to two rigid members and an elastomeric body connected between the two anchors and defining a fluid-filled working space with a rigid partition. Two flexible pockets define a balance chamber and a fluid-filled hydraulic chamber with the rigid partition where the balance chamber is connected to the working chamber through a restricted passage. The bag is spaced between a rigid enclosure, ie a pot, and an internal grid contained within the bag.

It is an object of the present invention to provide an improved switchable hydraulic bearing in which, in particular, a force required for switching and/or a flow resistance of a switchable valve through which flow occurs in an open position are reduced. The task is solved by means of the switchable hydraulic mount according to the independent claim. Preferred embodiments are given in the respective dependent claims.

One aspect relates to a switchable hydraulic mount, comprising: a first fluid chamber, which is partially delimited by a spring body, a second fluid chamber, which is fluidically connected to the first fluid chamber via a fluid channel and a bypass channel, so that when the Spring body, a damping fluid can flow between the two fluid chambers, and a switchable valve with which the bypass channel can be opened or closed in order to change a damping characteristic of the switchable hydraulic bearing. The switchable valve has a valve housing and a slide, the valve housing having: a valve chamber which at least partially forms the bypass channel, an axial valve opening which fluidly connects the valve chamber to the first fluid chamber or the second fluid chamber, and at least one radial valve opening , which fluidly connects the valve chamber to the other of the first fluid chamber or the second fluid chamber. An opening area, projected in the axial direction of the spool, of the radial valve opening on one side of the valve chamber is approximately zero, and the spool is completely disposed in the valve chamber. Furthermore, the spool is displaceable in the valve chamber between an open position, in which the axial valve opening and the radial valve opening are open, and a closed position, in which the radial valve opening is closed by a radial outer surface of the spool.

An advantage of the present invention is that the slide in the closed position and/or in an initial movement from the closed position into the open position is acted upon by the pressure in the respective fluid chamber exclusively in the radial direction. The pressure components acting on the slide in the axial direction cancel each other out.

The hydraulic bearing can also be referred to as a hydroelastic bearing. The hydraulic mount can be an engine mount for a motor vehicle, for example.

The fluid chambers can be fluid-tight sealed chambers with a damping fluid contained therein. The first fluid chamber can also be referred to as the primary or working chamber. The second fluid chamber can also be referred to as a secondary or compensation chamber. The second fluid chamber may be partially bounded by a bellows of elastomeric material. In the desired position or in the installed state of the hydraulic bearing, the first fluid chamber can be arranged above the second fluid chamber in the vertical direction.

The fluid channel can fluidly connect two fluid chambers with one another, with the damping fluid being able to flow from one fluid chamber into the other fluid chamber when one of the fluid chambers is deformed by means of an external force. In order to achieve a desired damping, the fluid channel can be designed with a predetermined damping characteristic. The fluid channel can also be referred to as a damping channel. The fluid channel may be formed in a partition wall located between the first and second fluid chambers.

The spring body can transmit the external force to the damping fluid and can contain elastically deformable material for this purpose, for example an elastomer. The spring body can, for example, be essentially in the form of a hollow truncated cone. A connection device for connecting the hydraulic bearing to a component can be arranged on the spring body.

The switchable valve can have a bypass channel, the damping characteristics of which differ to a desired extent from those of the fluid channel. The bypass channel can have less damping or less flow resistance than the fluid channel. For example, the damping or the flow resistance of the bypass channel can be negligibly small compared to the damping or the flow resistance of the fluid channel. The bypass channel may be formed in a partition wall located between the first and second fluid chambers. By means of the switchable valve, the damping fluid can flow either through the fluid channel or the bypass channel and thus the damping characteristics of the switchable hydraulic mount can be changed, with the open state of the bypass channel, i.e. when the slide is in the open position, part of the damping fluid depending can also flow through the fluid channel depending on the excitation frequency or amplitude.

A valve housing may be at least partially formed in a bulkhead disposed between the first and second fluid chambers, or may be at least partially formed integrally or in one piece with the bulkhead. The valve housing can be made in several parts. The valve chamber is formed inside the valve housing. The bypass channel can include the valve chamber, the axial valve opening and the radial valve opening.

The axial valve opening can be an opening of the valve chamber via which the valve chamber can be fluidically connected to the first fluid chamber, wherein the valve chamber can be fluidly connected or can be connected to the second fluid chamber via at least the radial valve opening. Alternatively, the axial valve opening can be an opening of the valve chamber via which the valve chamber can be fluidically connected to the second fluid chamber, wherein the valve chamber can be fluidly connected or connectable to the first fluid chamber via at least the radial valve opening.

The spool is accommodated in the valve chamber and is displaceable therein for switching the switchable valve. An axial direction of the slide can essentially coincide with an axial direction of the valve chamber, the valve housing and/or the hydraulic bearing. The slider can be magnetic at least in sections and can be displaced by means of a magnetic coil. The slide can be ring-shaped, in particular hollow-cylindrical. Correspondingly, the valve chamber can be of cylindrical design. However, the cross-sectional shape of the slider perpendicular to the axial direction is not limited to circular, and square or oval cross-sectional shapes, for example, are also conceivable.

An axial direction or axial direction is a direction in an extension of a length of a component. In the case of a cylinder-shaped slide, for example, the axial direction is aligned approximately parallel to a surface line or the longitudinal axis of the slide. In the case of a disc-shaped slider, the axial direction is aligned in the direction of the extension of the thickness of the disc-shaped slider due to the lack of a length.

A radial direction or radial direction is oriented perpendicular to the axial direction. For example, in the case of a cylinder-shaped slide or in the case of a disk-shaped slide, the radial direction is coincident lend aligned with the radius of the cylinder-shaped slider or the disk-shaped slider. In the case of a slide of hollow-cylindrical design, the radial direction can run in the direction of the wall thickness of the slide of hollow-cylindrical design.

Accordingly, a circumferential direction is a direction in an extension of the circumference of the component, for example of the hollow-cylindrical slide.

The terms “above” or “above” and the like used in the present application can refer to a direction counter to the direction of gravity. The terms “below” or “below” and the like used in the present application may refer to a direction in the direction of gravity.

In the context of the present invention, the terms “outside” or “inside” and the like used in the present application mean that a particularly idealized or imaginary center point is an innermost point. An outer area in relation to this is an, in particular idealized or imaginary, peripheral area. That is, a point or area that is referred to as being more outward than another point or area is further in the radial direction from the center toward the peripheral area than the other point or area.

The displacement direction of the slide can essentially correspond to the axial direction of the slide. The axial direction of the slide can essentially coincide with an axial direction of the switchable hydraulic bearing and/or an axial direction of the valve chamber.

The slide and the valve chamber can be designed in such a way that the pressure forces of the damping fluid acting on the slide always essentially cancel each other out, at least in the axial direction or the displacement direction. In other words, the forces acting on the axial end faces - i.e. the axial end faces of the slide projected onto a plane perpendicular to the direction of displacement - at its two free ends in the direction of displacement of the slide and caused by the fluid pressure are approximately the same, and thus a resulting force on the slide in the direction of displacement is approximately equal to zero. In particular, the end faces at one free end of the slide can be the same size as the end faces at the other free end of the slide. In order to ensure pressure equalization within the valve chamber between the volume section on one side of the spool and the volume section on the other side of the spool in the direction of displacement, an equalization opening can be formed in the spool, as described below. Alternatively or additionally, a compensating groove or compensating groove can be provided in the inner wall of the valve chamber, which extends in the axial direction or the displacement direction.

With the above configuration, a force balance or balance of forces can be achieved on the spool with respect to forces caused by fluid pressure, particularly when shifting the spool from the open position to the closed position and vice versa. Thus forces for the displacement of the slide can be designed and kept small independently of the fluid pressure in the fluid chambers.

As an alternative or in addition to the displacement direction mentioned above, the displacement direction of the slide can be aligned in a rotating manner in its circumferential direction. This means that the slide can also be rotated to open or close the radial valve opening. The rotating slide can have one or more diametrically, multiaxially and/or multiradially magnetized areas. The rotating slide can close several radial valve openings, which - in particular in different planes spaced apart from one another in the axial direction - can be formed on the valve chamber, with its radial outer surface or at least partially overlap with corresponding openings on its radial outer surface in order to create a fluid flow there allow through.

In particular, the valve housing and/or the partition wall can have a guide element for guiding the damping fluid flow, it being possible for the guide element to protrude into the first fluid chamber or into the second fluid chamber.

The guide element can have an essentially hollow-cylindrical inner contour for guiding the damping fluid flowing through the bypass channel. When flowing through a first end section of the guide element protruding into one of the two fluid chambers, the fluid can be laminarized in the guide element and thus the flow resistance in the guide element and/or in the switchable valve can be reduced.

An outer contour of the guide element can be formed essentially in the shape of a truncated cone on the first end section. On a second end section of the guide element that protrudes into the valve chamber, the outer contour can be essentially cylindrical. One End surface of a second end section of the guide element can be designed as an end stop for the slide. Furthermore, a collar can be formed on the outer contour, which prevents the guide element from penetrating further into the valve chamber.

The guide element can be connected to the valve housing and/or the partition wall by means of a non-positive and/or material connection, for example by means of a snug fit, in particular a press fit, and/or adhesive.

As an alternative to this, the guide element can be formed in one piece with the valve housing and/or the partition wall. In other words, the guide element and the valve housing can be part of the partition wall between the two fluid chambers. The valve housing can be divisible for mounting/inserting the slide into the valve chamber; in other words, the valve housing can be in several parts.

The valve housing can have a fastening device for the slide in an operating state.

The bypass channel can be designed as an opening in the partition wall between the two fluid chambers. In other words, an extension of the bypass channel in the axial direction can be smaller than its diameter in the radial direction.

In particular, the bypass channel can have the guide element, the valve housing with the valve chamber and the at least one radial valve opening.

In the area of the radial valve opening, a direction of the bypass channel—in particular a flow direction of the damping fluid flowing through the bypass channel—can be aligned perpendicularly to the axial direction or displacement direction of the slide. Alternatively or additionally, in the area in the valve chamber between the radial valve opening and the axial valve opening, the direction of the bypass channel—in particular a flow direction of the damping fluid flowing through the bypass channel—can be oriented at an angle other than 90° to the direction of displacement of the slide be. This can be implemented by means of a flow element, in particular a guide surface, on the slide. A flow resistance through the bypass channel can thus be reduced.

An opening area of the radial valve opening on one side of the valve opening projected in the axial direction or displacement direction of the slide onto a plane transverse to the axial direction or displacement direction is approximately equal to zero. In other words, the opening area of the radial valve hole has no component in the axial direction of the spool or the valve chamber. This means that in the closed position of the slide, when this opening surface of the radial valve opening is closed by the radial outer surface of the slide, essentially no pressure forces of the damping fluid can act on the slide in the axial direction or displacement direction. Only compressive forces transverse to the axial direction or direction of displacement, i.e. in the radial direction, can act on the slide. At least two radial valve openings can be provided, which are arranged and designed in such a way that the pressure forces acting on the slide from the radial valve openings cancel each other out, so that essentially neither axial pressure forces nor radial pressure forces act on the slide.

The slide can have at least one compensating opening which fluidly connects one axial free end of the slide to another axial free end of the slide. Thus, pressure equalization within the valve chamber between the volume section on one side of the slide and the volume section on the other side of the slide can be ensured in the direction of displacement, and flow resistance of the slide can be reduced when it is displaced between the closed position and the open position. The equalization opening can be part of the bypass channel.

For example, in the open position of the switchable valve, the damping fluid can flow from the first fluid chamber in the radial direction through the at least one radial valve opening into the valve chamber. Furthermore, the damping fluid can flow through the at least one compensating opening in the slide approximately in the axial direction through the valve chamber and through the axial valve opening into the second fluid chamber.

Alternatively, for example in the open position of the switchable valve, the damping fluid can flow from the first fluid chamber through the axial valve opening approximately in the axial direction into the valve chamber. Furthermore, the damping fluid can flow through the at least one compensating opening in the slide approximately in the axial direction through the slide and approximately in the radial direction through the at least one radial valve opening into the second fluid chamber.

Furthermore, for example, in the open position of the switchable valve, the damping fluid can flow from the second fluid chamber in the radial direction through the at least one radial valve opening into the valve flow into the chamber. Furthermore, the damping fluid can flow through the at least one compensating opening in the spool, through the axial valve opening, approximately in the axial direction through the valve chamber and into the first fluid chamber.

Alternatively, for example in the open position of the switchable valve, the damping fluid can flow from the second fluid chamber through the axial valve opening approximately in the axial direction into the valve chamber. Furthermore, the damping fluid can flow through the at least one compensating opening in the spool approximately in the axial direction through the spool and approximately in the radial direction through the at least one radial valve opening into the first fluid chamber.

The slide can be hollow-cylindrical, ring-shaped, U-shaped, disk-shaped, hollow spherical or truncated cone-shaped, as long as the radial outer surface thereof can essentially completely close the radial valve opening in the closed position. In particular, the annular slide can have a C-shaped cross section or, depending on the radial valve opening that is present, can be designed as an individual slide with a C-shaped cross section. The advantages described above can thus be achieved with a large number of forms of the slide that can be selected therefrom, and there is flexibility in the construction and/or adaptation to different applications.

The slide can have a guide surface which, at least in the open position, at least partially deflects an axial fluid flow coming from the axial valve opening into a radial fluid flow towards the radial valve opening, and vice versa.

The guide surface is arranged in particular on the side of the slide that faces the axial valve opening. In the open position, the guide surface can reduce the flow resistance of the bypass channel. In particular in the case of the slide designed in the shape of a truncated cone, the guide surface can be designed to be inclined in relation to the axial direction. Thus, the fluid flow can be reliably deflected.

The slide can be arranged in the valve chamber in such a way that the slide, in particular during its displacement, is at least partially guided with its radial outer surface on a radial inner surface of the valve chamber.

The slide may have a friction-reducing material, in particular on its radially outer surface. Thus, the friction when moving the slider can be reduced and a safe moving of the slider can be guaranteed. Examples of friction-reducing material are PTFE (polytetrafluoroethylene), POM (polyoxymethylene) or PA (polyamide).

A gap can be provided there to further reduce the friction between the slide and the valve chamber. The gap between the radially outer surface of the slide and the radially inner surface of the valve chamber can be in the range from about 0.1 to about 0.7 mm, in particular in the range from about 0.3 to about 0.5 mm.

Furthermore, the slide can have an elastic material on its radial outer surface, in particular on a sealing section of the slide. A secure closure or sealing of the radial valve opening in the closed position can thus be ensured. An example of an elastic material is an elastomer.

Two or more radial valve openings can be arranged symmetrically on the valve housing in such a way as to bring about a balancing of forces or a balance of forces on the spool in its radial direction. Force balancing or force balance relates to the compressive forces acting on the spool from the damping fluid. For example, the two or more radial valve openings can be arranged in pairs opposite one another. However, an odd number of radial valve openings can also be provided, as long as the pressure forces cancel each other out. The radial valve openings can have effective cross-sectional areas of the same size, in particular opening areas on one side of the valve chamber.

By balancing forces in the radial direction, friction between the slide and the valve housing can be reduced. In addition, rattling of the slide in the valve housing can be avoided in this way, since the slide is not moved in the radial direction by pulsating forces.

In particular, the radial valve opening can be an opening in a wall of the valve chamber without further expansion in the radial direction. In other words, an extension of the radial valve opening in the radial direction can be smaller than a diameter of the radial valve opening.

The axial valve opening or the sum of the opening areas of the axial valve opening can be approximately the same size as or larger than the radial valve opening or the sum of the opening areas of the radial valve opening on the side of the valve chamber.

The radial valve opening can have a circular cross-section and be designed in the shape of a cylinder.

Likewise, the valve chamber can have a circular cross-section and be designed in the shape of a cylinder.

A direction of extension of the radial valve opening or directions of extension of a plurality of radial valve openings can be aligned perpendicularly, in particular largely perpendicularly, to the axial direction of the slide.

As an alternative to this, an extension direction of the radial valve opening can be aligned at an angle deviating from 90° to the axial direction of the slide.

The slider is designed at least partially as a permanent magnet or containing ferromagnetic material.

The switchable valve has a magnetic coil that interacts with the slide to move the slide. When the switchable valve of the switchable hydraulic bearing is actuated electromagnetically or electrodynamically as a result, the magnetic coil can be operated in such a way that it attracts or repels the slide.

In particular, the displacement of the above-mentioned rotating slide can be controlled by means of a plurality of magnetic coils and/or a plurality of magnets arranged on the rotating slide - in particular permanent magnets and/or points containing ferromagnetic material.

The slide can have an actuating element for effecting the displacement of the slide, wherein the actuating element can be designed at least partially as a permanent magnet or containing ferromagnetic material.

The actuating element can interact with the magnet coil to move the slide.

The actuating element can be formed in one piece with the slide.

As an alternative to this, the actuating element can be designed separately from the slide and can be arranged on the slide.

The actuating element can be rod-shaped and arranged centrally on the slide and aligned axially with the slide. Furthermore, a bulge can be formed in the valve chamber, which bulge accommodates the actuating element. The valve can be Be slider in the open position or in the closed position.

The slider can be made by an injection molding process using ferromagnetic material or permanent magnet material. In this case, ferromagnetic material or permanent magnet material can be embedded in a plastic or ferromagnetic material or permanent magnet material can be overmoulded with plastic.

The actuating element can have at least one compensation opening which fluidly connects one axial free end of the actuating element to another axial free end of the actuating element. In other words, and taking into account what has been mentioned above, the at least one compensation opening can be formed on the slide and/or on the actuating element.

For example, a plurality of equalizing openings can be distributed equidistantly on an inner circumference of the spool, with the inner circumference lying between a center point of the spool and an outer circumference of the spool.

The magnetic coil can be arranged outside of the two fluid chambers.

The magnetic coil can be arranged in the area of the bulge of the valve chamber, in particular around the bulge.

With the above configuration, a distance between the actuator and/or the slider and the solenoid for electromagnetic operation can be reduced. As a result, a greater actuating force can be exerted on the actuating element and/or the slide. Furthermore, the structural size of the magnetic coil of the actuating element and/or the slide can be reduced as a result. In addition, the effort involved in electrically connecting the magnetic coil can be reduced, in particular a fluid-tight passage of an electrical connection for the magnetic coil into a region within the two fluid chambers can be dispensed with.

As an alternative to this, the magnetic coil can be arranged within the two fluid chambers, for example in the partition wall between the two fluid chambers.

With the alternative configuration, similarly as before, the distance between the actuator and/or slider and the solenoid for electromagnetic actuation can be reduced, thereby allowing a larger actuating force to be applied to the actuator and/or slider. Furthermore, the structural size of the magnetic coil of the actuating element and/or the slide can be reduced as a result. In this case, an electrical connection for the magnetic coil can be carried out in a fluid-tight manner in the area inside the two fluid chambers.

As an alternative or in addition to this, the slide can be reset or moved by means of gravity, depending on whether the switchable valve is designed as an opener or closer. The direction of displacement and/or the axial direction of the slide preferably coincides essentially with the direction of gravity. For this purpose, the slide can be held in the closed position or the open position by means of the above-described electromagnetic actuation against the effect of gravity on the slide, depending on whether the switchable valve is designed as an opener or closer. The resetting or displacement of the slide can then take place by deactivating the magnetic coil.

The switchable hydraulic bearing can have a restoring element that exerts a restoring force on the slide, the restoring force being directed counter to the displacement direction of the slide either from the open position to the closed position or from the closed position to the open position.

In particular, the restoring element can be arranged between the valve housing and the slide. Furthermore, in particular, the restoring element can be arranged between a guide element arranged on the valve housing and the slide. The restoring element can be arranged at least partially in the valve chamber.

For example, the restoring element can be designed as a helical spring.

An end stop with a damping element can be provided in the valve chamber at an end region of a displacement path of the slide.

With the above configuration, an otherwise necessary maximum design of a force constant for the electromagnetically actuated displacement of the slide can be omitted, since the slide is held by the end stop at the end region of the displacement path. A possibly oversized force constant presses the slide a little more against the end stop with the damping element. A damping of a stop of the slide at the end area of the displacement path and/or at the valve chamber can thus be achieved and a noise caused by the stop can thus be reduced.

Alternatively, the damping element can be dispensed with if there is a distance between an end section of the valve chamber and the slide in the open position or the closed position or if it is irrelevant whether a noise is produced when the slide is moved into the open position or the closed position. In particular, the spool can be held in the open position or the closed position without touching the end portion of the valve chamber by means of the above-described electromagnetically operated displacement.

When selecting a material for the bypass channel and/or the slide, an expansion characteristic caused by a pressure difference can be taken into account. The expansion characteristics can be calculated using the following formula, assuming a hollow-cylindrical shape: $$\Delta {\mathrm{right}}_x=\frac{p_i\cdot {\mathrm{right}}_x\cdot {\mathrm{right}}_a{}^2}{E\cdot \left({\mathrm{right}}_a{}^2\cdot {\mathrm{right}}_i{}^2\right)}\cdot \left[\frac{{\mathrm{<figure-callout\; id="2"\; label="right\; i"\; filenames="DE102019003604B4\_0002.png,DE102019003604B4\_0003.png"\; state="\{\{state\}\}">right</figure-callout>}}_i{}^2}{{\mathrm{right}}_x{}^2}\cdot \left(1+v\right)+1-v\right]$$

Δrx:

Zunahme des Radius

ri:

Innenradius [mm]

ra:

Außenradius [mm]

rx:

Radius an bestimmter Position [mm]

pi:

Innendruck [MPa]

E:

E-modul [N/mm²]

v:

Poissonzahl [-]

There are:

Δrx:

increase in radius

here:

inner radius [mm]

ra:

outer radius [mm]

rx:

Radius at specific position [mm]

pi:

internal pressure [MPa]

E:

Modulus of elasticity [N/mm ² ]

f:

Poisson's ratio [-]

For example, for a hollow cylinder made of PTFE with an outside diameter of 25 mm and a wall thickness of 2 mm, the outside diameter of the hollow cylinder increases by about 0.15 mm at 5 bar. If POM is used as the material for the hollow cylinder, the outer diameter of the hollow cylinder increases by only about 0.025 mm, all other things being equal.

A switchable valve is described, having a valve housing and a slide, the valve housing having: a valve chamber, an axial valve opening which fluidically connects the valve chamber to a first fluid region det, and at least one radial valve opening which fluidly connects the valve chamber with a second fluid area, wherein an opening area of the radial valve opening projected in the axial direction of the spool is approximately equal to zero on one side of the valve chamber, and wherein the spool is arranged entirely in the valve chamber and in the valve chamber between an open position, in which the axial valve opening and the radial valve opening are opened, and a closed position, in which the radial valve opening is closed by a radial outer surface of the slide. The first fluid area or the second fluid area can also be referred to as the first volume or second volume.

The switchable valve described above can be designed in particular as a switchable valve in the switchable hydraulic bearing described above. What was described above for the switchable valve of the switchable hydraulic bearing applies correspondingly to the switchable valve described above according to the further aspect. As described above, the switchable valve can be used in a switchable hydraulic bearing or used on its own, for example, in automotive fluid systems, dosing systems, pneumatic and hydraulic systems, air conditioning and temperature control systems and/or energy systems for controlling a hydraulic or pneumatic fluid. The valve chamber of the switchable valve can at least partially form a channel between two fluid chambers or fluid lines of a device.

It is an advantage of the switchable valve that a symmetrical pressure distribution is achieved in the switchable valve.

Another advantage of the switchable valve is that it works in a roughly comparable manner with pressures in both directions.

In addition, an advantage of the switchable valve is that very rapid actuation is made possible because of the small moving masses in the switchable valve.

Another advantage of the switchable valve is that pressure surges can be intercepted very quickly.

Another advantage of the switchable valve is that the manufacturing costs are relatively low due to the use of predominantly rotationally symmetrical parts.

Exemplary embodiments of the switchable hydraulic bearing according to the invention are explained in more detail below with reference to drawings. It goes without saying that the present invention is not restricted to the embodiments described below, and that individual features of the described embodiments can be combined to form further embodiments.

• 1 einen Querschnitt der Vorderansicht des schaltbaren Hydrolagers gemäß einem ersten Ausführungsbeispiel der Erfindung,
• 2 eine vereinfachte Darstellung des schaltbaren Hydrolagers, anhand der dessen Funktionsprinzip veranschaulicht wird,
• 3 eine weitere vereinfachte Darstellung des schaltbaren Hydrolagers gemäß 2, anhand der dessen Funktionsprinzip veranschaulicht wird,
• 4 ein zweites Ausführungsbeispiel des schaltbaren Hydrolagers,
• 5 ein drittes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 6 ein viertes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 7 ein fünftes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 8 ein sechstes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 9 ein siebtes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 10 ein achtes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 11 ein neuntes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 12 ein zehntes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 13 ein elftes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 14 ein zwölftes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 15 ein dreizehntes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 16 ein vierzehntes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 17 ein fünfzehntes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 18 ein sechzehntes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 19 ein siebzehntes Ausführungsbeispiel des schaltbaren Hydrolagers,
• 20 ein vereinfachte Darstellung des schaltbaren Hydrolagers anhand der Konstruktionsüberlegungen betrachtet werden und
• 21 eine Graphik, in der zwei Werkstoffe bezüglich ihrer Querdehnungseigenschaft gegenübergestellt werden.

Show it:

• 1 a cross section of the front view of the switchable hydraulic bearing according to a first embodiment of the invention,
• 2 a simplified representation of the switchable hydraulic mount, which is used to illustrate its functional principle,
• 3 a further simplified representation of the switchable hydro bearing according to 2 , on the basis of which its functional principle is illustrated,
• 4 a second embodiment of the switchable hydraulic mount,
• 5 a third embodiment of the switchable hydraulic mount,
• 6 a fourth embodiment of the switchable hydraulic mount,
• 7 a fifth embodiment of the switchable hydraulic mount,
• 8th a sixth embodiment of the switchable hydraulic bearing,
• 9 a seventh embodiment of the switchable hydraulic bearing,
• 10 an eighth embodiment of the switchable hydraulic bearing,
• 11 a ninth embodiment of the switchable hydraulic bearing,
• 12 a tenth embodiment of the switchable hydraulic bearing,
• 13 an eleventh embodiment of the switchable hydraulic bearing,
• 14 a twelfth embodiment of the switchable hydraulic bearing,
• 15 a thirteenth embodiment of the switchable hydraulic bearing,
• 16 a fourteenth embodiment of the switchable hydraulic bearing,
• 17 a fifteenth embodiment of the switchable hydraulic bearing,
• 18 a sixteenth embodiment of the switchable hydraulic bearing,
• 19 a seventeenth embodiment of the switchable hydraulic bearing,
• 20 a simplified representation of the switchable hydro bearing based on the design considerations and
• 21 a graphic in which two materials are compared with regard to their transverse strain properties.

An axial direction Ax, a circumferential direction Um and a radial direction Ra are shown in the figures by means of directional arrows, in particular in the form of a coordinate system. Although the directional arrows each only point in one direction, the directional information also includes a respective opposite direction. Two radial directions Ra are given as an example; this is only intended to give an impression of the many possible radial directions Ra.

in the in 1 shown cross-section of the front view of the switchable hydraulic bearing 1 according to a first embodiment of the invention, a first fluid chamber 2 is surrounded by a spring body 4 at least partially. A connection device 14 for connecting a component to be mounted by means of the switchable hydraulic mount 1 , for example an engine, is provided on the spring body 4 , in particular on an upper side thereof.

A bearing body 6 connects the spring body 4 in a fluid-tight manner to a partition wall 8 which separates the first fluid chamber 2 from a second fluid chamber 10 . In the partition wall 8 there is a fluid channel 16 which, as shown here for example, can be in the form of an annular channel. The first fluid chamber 2 is fluidically connected to the second fluid chamber 10 via the fluid channel 16 . A membrane 18 is also provided in the partition wall 8 . The second fluid chamber 10 is at least partially surrounded by a compensating membrane 12 .

A bypass channel 20 is formed in the partition wall 8, via which the first fluid chamber 2 and the second fluid chamber 10 are or can be fluidly connected to one another. The bypass channel 20 has a valve housing 22 in which a valve chamber 24 is formed. An axial valve opening 26 of the valve chamber 24 is fluidly connected to the first fluid chamber 2 , with two or more radial valve openings 28 of the valve chamber 24 being fluidly connected to the second fluid chamber 10 .

A slide 30 is arranged in the valve chamber 24 and is pressed into its normal position by means of a restoring element 32 . As shown, the return element 32 can be in the form of a coil spring. The restoring element 32 is supported on a guide element 34 which is arranged on the axial valve opening 26 . In principle, the guide element 34 can be fastened to the valve housing 22 by means of a non-detachable connection such as welding, in particular thermal welding or friction welding. As an alternative or in addition to this, the guide element 34 can generally be fastened to the valve housing 22 by means of a detachable connection such as, for example, a screw connection or snap-in connection.

As shown here, the slider 30 can be made of ferromagnetic material. An end stop 36, preferably with a damping element 38, can be provided in the valve chamber 24 at an end region of a displacement path of the slide 30, as shown here.

A magnetic coil 40 for the electromagnetic displacement of the slide 30 against the restoring element 32 is arranged on the valve housing 22 outside of the two fluid chambers 2 , 10 .

A switchable valve 41, which - as shown here, for example - has the bypass channel 20, the valve housing 22 with the valve chamber 24, the slide 30, the magnetic coil 40, the restoring element 32 and the guide element 34 is designed here as an opener, ie In its normal position, which corresponds to the closed position, the slide 30 seals the radial valve openings 28 and thus separates a fluid connection between the two fluid chambers 2, 10 via the bypass channel 20.

in the in 2 shown simplified representation of the switchable hydraulic bearing 1 is illustrated its principle of operation.

An exemplary embodiment of the switchable hydraulic bearing 1 is shown in its closed position with the axial valve opening 26 pointing toward the first fluid chamber 2 and the radial valve openings 28 pointing toward the second fluid chamber 10 . The switchable valve 41 is designed as an opener here, i.e. it is closed in its normal position. The force of gravity acts here as the restoring force on the slide 30, the indicated axial direction Ax being aligned approximately against the force of gravity. Damping elements 38 are provided both at an upper end portion of the spool 30 and at a lower portion of the valve chamber 24 . The magnetic coil 40 is arranged at an upper area of the valve housing 22 .

First forces 42 from the pressure in the first fluid chamber 2 are shown with short solid lines, second forces 44 from the pressure in the second fluid chamber 10 are shown with longer dashed lines. A direction of movement 46 of the slide 30 is shown with thick double arrows.

The first forces 42 acting on the slide 30, which are directed in the direction of movement of the slide 30, balance each other out, ie no first forces 42 from the pressure in the first fluid chamber 2 act on the slide 30 in its displacement direction.

The second forces 44 acting on the slide 30, which are directed perpendicular to the displacement direction 46 of the slide 30, also balance out, ie no second forces 44 from the pressure in the second fluid chamber 10 act on the slide 30 perpendicular to its displacement direction 46

In the 3 shown further simplified representation of the switchable hydraulic bearing 1 according to 2 shows the switchable hydraulic bearing 1 in its open position. The electromagnetically displaced slide 30 rests with its upper damping element 38 on the end stops of the valve housing 22 and opens the radial valve openings 28.

Fluid can thus flow between the two fluid chambers 2, 10, as indicated by the curved double arrows, which represent the fluid flow 48.

This in 4 shown second embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the closed position. The switchable valve 41 is therefore designed as an opener. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slide 30 is designed as a permanent magnet with magnetization in the axial direction Ax. The magnetic coil 40 is arranged outside of the two fluid chambers 2, 10 in order to enable simpler electrical connection. The restoring element 32 is arranged between the slide 30 and the guide element 34 .

This in 5 shown third embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the open position. The switchable valve 41 is therefore designed as a closer. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slide 30 is designed as a permanent magnet with magnetization in the axial direction Ax. The magnetic coil 40 is arranged outside of the two fluid chambers 2, 10 in order to enable simpler electrical connection. The restoring element 32 is arranged between the slide 30 and the valve housing 22 .

This in 6 shown fourth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the open position. The switchable valve 41 is therefore designed as a closer. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slider 30 is made of ferromagnetic material. The magnetic coil 40 is arranged outside of the two fluid chambers 2, 10 in order to enable simpler electrical connection. The restoring element 32 is arranged between the slide 30 and the valve housing 22 .

This in 7 shown fifth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the closed position. The switchable valve 41 is therefore designed as an opener. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slide 30 is designed as a permanent magnet with magnetization in the radial direction Ra. The magnetic coil 40 is arranged within the fluid chambers 2, 10 in order to achieve a higher force constant. As shown, the magnetic coil 40 can be arranged in the partition wall 8 . The restoring element 32 is arranged between the slide 30 and the guide element 34 .

This in 8th shown sixth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the open position. The switchable valve 41 is therefore designed as a closer. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slide 30 is designed as a permanent magnet with magnetization in the radial direction Ra. The magnetic coil 40 is arranged within the fluid chambers 2, 10 in order to achieve a higher force constant. As shown, the magnetic coil 40 can be arranged in the partition wall 8 . The restoring element 32 is arranged between the slide 30 and the valve housing 22 .

This in 9 shown seventh embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the closed position. The switchable valve 41 is therefore designed as an opener. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slider 30 is made of ferromagnetic material. The magnetic coil 40 is arranged within the fluid chambers 2, 10 in order to achieve a higher force constant. As shown, the magnetic coil 40 can be arranged in the partition wall 8 . The restoring element 32 is arranged between the slide 30 and the guide element 34 .

This in 10 shown eighth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the closed position. The switchable valve 41 is therefore designed as an opener. The axial valve opening 26 is designed towards the second fluid chamber 10 , the radial valve openings 28 are designed towards the first fluid chamber 2 . The slide 30 is designed as a permanent magnet with magnetization in the radial direction Ra. The magnetic coil 40 is arranged within the fluid chambers 2, 10 in order to achieve a higher force constant. As shown, the magnetic coil 40 can be arranged in the partition wall 8 . The restoring element 32 is arranged between the slide 30 and the valve housing 22 .

This in 11 shown ninth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the open position. The switchable valve 41 is therefore designed as a closer. The axial valve opening 26 is designed towards the second fluid chamber 10 , the radial valve openings 28 are designed towards the first fluid chamber 2 . The slide 30 is designed as a permanent magnet with magnetization in the radial direction Ra. The magnetic coil 40 is arranged within the fluid chambers 2, 10 in order to achieve a higher force constant. As shown, the magnetic coil 40 can be arranged in the partition wall 8 . The restoring element 32 is arranged between the slide 30 and the valve housing 22 .

This in 12 shown tenth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the closed position. The switchable valve 41 is therefore designed as an opener. The axial valve opening 26 is designed towards the second fluid chamber 10 , the radial valve openings 28 are designed towards the first fluid chamber 2 . The slider 30 is made of ferromagnetic material. The magnetic coil 40 is arranged within the fluid chambers 2, 10 in order to achieve a higher force constant. As shown, the magnetic coil 40 can be arranged in the partition wall 8 . The restoring element 32 is arranged between the slide 30 and the valve housing 22 .

This in 13 shown eleventh embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the closed position. The switchable valve 41 is therefore designed as an opener. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slider 30 is formed with a rod-shaped actuating element 50 which is arranged centrally on the slider 30 and is axially aligned with the slider 30 . The actuating element 50 is designed as a permanent magnet with magnetization in the axial direction Ax. The magnetic coil 40 is arranged outside of the two fluid chambers 2, 10 in order to enable simpler electrical connection. The restoring element 32 is arranged between the slide 30 and an end stop 36 formed on the valve housing 22 .

This in 14 shown twelfth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the open position. The switchable valve 41 is therefore designed as a closer. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slider 30 is formed with the rod-shaped actuating element 50 which is arranged centrally on the slider 30 and is axially aligned with the slider 30 . The actuating element 50 is designed as a permanent magnet with magnetization in the axial direction Ax. The magnetic coil 40 is arranged outside of the two fluid chambers 2, 10 in order to enable simpler electrical connection. The restoring element 32 is arranged between the slide 30 and the valve housing 22 , with the end stop 36 being formed on the valve housing 22 .

This in 15 shown thirteenth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the open position. The switchable valve 41 is therefore designed as a closer. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slider 30 is formed with the rod-shaped actuating element 50 which is arranged centrally on the slider 30 and is axially aligned with the slider 30 . The actuating element 50 is made of ferromagnetic material. The magnetic coil 40 is arranged outside of the two fluid chambers 2, 10 in order to enable simpler electrical connection. The restoring element 32 is arranged between the slide 30 and the valve housing 22 , with the end stop 36 being formed on the valve housing 22 .

This in 16 shown fourteenth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the closed position. The switchable valve 41 is therefore designed as an opener. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slider 30 is formed with the rod-shaped actuating element 50 which is arranged centrally on the slider 30 and is axially aligned with the slider 30 . The actuating element 50 is designed as a permanent magnet with magnetization in the axial direction Ax. The magnetic coil 40 is arranged outside of the two fluid chambers 2, 10 in order to enable simpler electrical connection. The restoring element 32 is arranged between the slide 30 and the valve housing 22 .

A guide element 34 which protrudes into the first fluid chamber 2 is arranged on the valve housing 22 . Slider 30 is frustoconical in shape and has an inclined guide surface 52 in order, at least in the open position, to at least partially deflect an axial fluid flow coming from axial valve opening 26 into a radial fluid flow toward at least one of radial valve openings 28 or one of at least one of the radial Valve openings 28 to deflect incoming fluid flow towards the axial valve opening 26 . The slide 30 has a plurality of equalization openings 54 .

This in 17 shown fifteenth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the closed position. The switchable valve 41 is therefore designed as an opener. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slider 30 is formed with the rod-shaped actuating element 50 which is arranged centrally on the slider 30 and is axially aligned with the slider 30 . The actuating element 50 is designed as a permanent magnet with magnetization in the axial direction Ax. The magnetic coil 40 is arranged outside of the two fluid chambers 2, 10 in order to enable simpler electrical connection. The restoring element 32 is arranged between the slide 30 and the guide element 34 , with the end stop 36 being formed on the guide element 34 .

A guide element 34 which protrudes into the first fluid chamber 2 is arranged on the valve housing 22 . The slide 30 is designed as a hollow cylinder and has a number of equalizing openings 54 .

This in 18 shown sixteenth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the open position. The switchable valve 41 is therefore designed as a closer. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slider 30 is formed with the rod-shaped actuating element 50 which is arranged centrally on the slider 30 and is axially aligned with the slider 30 . The actuating element 50 is made of ferromagnetic material. The magnetic coil 40 is arranged outside of the two fluid chambers 2, 10 in order to enable simpler electrical connection. The restoring element 32 is arranged between the slide 30 and the valve housing 22 , with the end stop 36 being formed on the slide 30 .

A guide element 34 which protrudes into the first fluid chamber 2 is arranged on the valve housing 22 . The slide 30 is designed as a hollow cylinder and has a number of equalizing openings 54 . The actuating element 50 has a compensation opening 54 which is formed with one of the compensation openings 54 of the slider 30 in overlap.

This in 19 shown seventeenth embodiment of the switchable hydraulic bearing 1 is shown in its normal position, which corresponds to the closed position. The switchable valve 41 is therefore designed as an opener. The axial valve opening 26 is designed towards the first fluid chamber 2 , the radial valve openings 28 are designed towards the second fluid chamber 10 . The slider 30 is formed with the rod-shaped actuating element 50 which is arranged centrally on the slider 30 and is axially aligned with the slider 30 . The actuating element 50 is made of ferromagnetic material. The magnetic coil 40 is arranged outside of the two fluid chambers 2, 10 in order to enable simpler electrical connection. The restoring element 32 is arranged between the slide 30 and the valve housing 22 , with the end stop 36 being formed on the slide 30 .

A guide element 34 which protrudes into the first fluid chamber 2 is arranged on the valve housing 22 . The slide 30 is designed as a hollow cylinder and has a number of equalizing openings 54 . The actuating element 50 has a compensation opening 54 which is formed with one of the compensation openings 54 of the slider 30 in overlap.

20 shows a simplified representation of the switchable hydraulic bearing 1 to illustrate design considerations. The slider 30 has been omitted for the sake of clarity.

In order to design the switchable hydraulic bearing 1 appropriately for the fluid, a sum of the opening areas of the radial valve openings 28 projected in the radial direction Ra of the slide 30 on the side of the valve chamber 24 is designed to be approximately the same as or smaller than a cross-sectional area of the valve chamber 24 projected in the axial direction Ax of the valve chamber 24.

Furthermore, a height 56 of the cylindrical radial valve opening 28 is approximately the same size as or less than a quarter of a diameter 58 of the cylindrical valve chamber 24. In this consideration, the radial valve opening 28 is assumed to be idealized as a continuous lateral surface of a cylinder. Partition walls therein or connecting webs bridging the radial valve opening 28 must be taken into account when designing the height, ie the height must then be increased accordingly.

In 21 a graph is shown in which the characteristic curves of two materials are compared with regard to their transverse strain properties.

The original outer diameter in mm is entered on the abscissa. The increase in the outer diameter in mm is entered on the ordinate.

Transverse expansion of a pipe with an outside diameter of 25 mm and an assumed wall thickness of 1 mm to 2 mm and a pressure difference of 5 bar is shown.

For the upper line 60, which represents the transverse elongation property of PTFE, it can be read that, for example, with a wall thickness of 2 mm, the outside diameter increases by approximately 0.15 mm.

For the lower line 62, which represents the transverse elongation property of POM, it can be read that, for example, with a wall thickness of 2 mm, the outside diameter increases by only about 0.025 mm.

reference list

1

switchable hydro bearing

2

first fluid chamber

4

spring body

6

bearing body

8th

partition wall

10

second fluid chamber

12

compensating membrane

14

connection device

16

fluid channel

18

membrane

20

bypass channel

22

valve body

24

valve chamber

26

axial valve opening

28

radial valve opening

30

slider

32

return element

34

guide element

36

end stop

38

damper element

40

magnetic coil

41

switchable valve

42

first powers

44

second powers

46

displacement direction of the slider

48

fluid flow

50

actuator

52

guide surface

54

compensation opening

56

Height of the cylindrical radial valve opening

58

diameter of the valve chamber

60

upper line for PTFE

62

bottom line for POM

axe

axial direction

Ra

radial direction

Around

circumferential direction

Claims (14)

Switchable hydraulic bearing (1), comprising: a first fluid chamber (2) which is partially delimited by a spring body (4), a second fluid chamber (10) which is connected via a fluid channel (16) and a bypass channel (20) to the first fluid chamber (2) is fluidically connected, so that when the spring body (4) compresses or extends, a damping fluid can flow between the two fluid chambers (2, 10), and a switchable valve (41) with which the bypass channel (20) can be opened or closed in order to change a damping characteristic of the switchable hydraulic bearing (1), the switchable valve (41) having a valve housing (22) and a slide (30), the valve housing (22) having: a valve chamber (24) which at least partially forms the bypass channel (20), an axial valve opening (26) which fluidly connects the valve chamber (24) to the first fluid chamber (2) or the second fluid chamber (10), and at least one radial valve opening (28) which the Vent The oil chamber (24) fluidly connects to the other of the first fluid chamber (2) or the second fluid chamber (10), wherein an opening area of the radial valve opening (28) projected in the axial direction (Ax) of the spool (30) on one side of the valve chamber (24) is approximately equal to zero, the spool (30) being arranged entirely in the valve chamber (24) and in of the valve chamber (24) between an open position, in which the axial valve opening (26) and the radial valve opening (28) are open, and a closed position, in which the radial valve opening (28) is closed by a radial outer surface of the slide (30). , is displaceable, and wherein the slider (30) is at least partially constructed as a permanent magnet or containing ferromagnetic material and wherein the slider (30) for displacing the slider (30) interacts with a magnetic coil (40). Switchable hydro bearing (1) after claim 1 , The slide (30) having at least one compensating opening (54) which fluidly connects one axial free end of the slide (30) to another axial free end of the slide (30). Switchable hydro bearing (1) after claim 1 or 2 , the slide (30) having a guide surface (52) which, at least in the open position, at least partially deflects an axial fluid flow coming from the axial valve opening (26) into a radial fluid flow towards the radial valve opening (28), and vice versa. Switchable hydraulic bearing (1) according to one of the preceding claims, wherein two or more radial valve openings (28) are arranged symmetrically on the valve housing (22) in order to bring about a balancing of forces on the slide (30) in its radial direction (Ra). Switchable hydraulic bearing (1) according to one of the preceding claims, wherein the axial valve opening (26) or a sum of the opening areas of the axial valve opening (26) is approximately the same size as or is larger than the radial valve opening (28) or a sum of the opening areas of the radial valve opening (28) on the side of the valve chamber (24). Switchable hydraulic bearing (1) according to one of the preceding claims, wherein an extension direction of the radial valve opening (28) is aligned perpendicularly to the axial direction (Ax) of the slide (30). Switchable hydraulic bearing (1) according to one of the preceding claims, wherein the slide (30) has an actuating element (50) for effecting the displacement of the slide (30), the actuating element (50) being designed at least partially as a permanent magnet or containing ferromagnetic material and wherein the actuating element (50) for displacing the slide (30) interacts with the magnetic coil (40). Switchable hydro bearing (1) after claim 7 , wherein the actuating element (50) is formed in one piece with the slide (30). Switchable hydro bearing (1) after claim 7 or 8th , wherein the actuating element (50) has at least one compensation opening (54) which fluidly connects an axial free end of the actuating element (50) to another axial free end of the actuating element (50). Switchable hydraulic bearing (1) according to one of the preceding claims, wherein the magnet coil (40) is arranged outside of the two fluid chambers (2, 10). Switchable hydro bearing (1) according to one of Claims 1 until 9 , wherein the magnetic coil (40) is arranged within the two fluid chambers (2, 10). Switchable hydro bearing (1) after claim 11 , wherein the magnetic coil (40) is arranged in the partition wall (8) between the two fluid chambers (2, 10). Switchable hydraulic mount (1) according to one of the preceding claims, with a restoring element (32) which exerts a restoring force on the slide (30), the restoring force being directed counter to the displacement direction of the slide (30). Switchable hydraulic bearing (1) according to one of the preceding claims, wherein an end stop with a damping element (38) is provided in the valve chamber (24) at an end region of a displacement path of the slide (30).

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