Hydrolager

Abstract

Hydraulic bearing (1) comprising: an inner core (2); an outer sleeve (3) radially surrounding the inner core (2); an elastomeric body (4) elastically connecting the inner core (2) and the outer sleeve (3) to allow relative displacement between the inner core (2) and the outer sleeve (3); a first working chamber (5) and a second working chamber (6) fluidically connected to each other via a working channel; a displacement chamber (8) connected to the first working chamber (5) via a first displacement channel (9), wherein the first working chamber (5) and the second working chamber (6) are configured such that the magnitude of a volume change upon displacement of the inner core (2) relative to the outer sleeve (3) in a predetermined radial direction is greater for the first working chamber (5) than for the second working chamber (6);a first sealing element (10), wherein the first sealing element (10) is arranged at a first axial end (11) of the hydraulic bearing (1) to at least partially limit the displacement chamber (8) in the axial direction; and a second sealing element (12), wherein the second sealing element (12) is arranged at a second axial end (13) of the hydraulic bearing to at least partially limit the displacement chamber (8) in the axial direction; wherein the displacement chamber (8) is connected to the second working chamber (6) via a second displacement channel (14).

Description

[0001] The present invention relates to a hydraulic mount, particularly for use in a motor vehicle. The hydraulic mount can be used, for example, to support an axle carrier or a wheel link, especially a control arm. Furthermore, the hydraulic mount can be used to support components, such as an engine. Finally, the hydraulic mount can be used for the elastic mounting of a cabin in a construction or agricultural machine.

[0002] A hydraulic mount is generally used when relative movement of a vibration-loaded component, such as a vehicle part, to the body needs to be permitted and damped. Due to the use of elastomer material, the hydraulic mount provides restoring spring forces as well as damping forces actively generated through dissipation losses within the mount.

[0003] The object of the present invention is to provide a novel hydraulic bearing which enables high damping performance in a wide frequency range.

[0004] This problem is solved by a hydraulic bearing with the features of the independent claim. Preferred embodiments are described in the dependent claims.

[0005] According to the present invention, a hydraulic bearing is provided, comprising an inner core and an outer sleeve radially surrounding the inner core. The hydraulic bearing according to the invention also includes an elastomeric body that elastically connects the inner core and the outer sleeve to allow relative displacement between the inner core and the outer sleeve. Furthermore, the hydraulic bearing has a first working chamber and a second working chamber, which are fluidically connected to each other via a working channel. The hydraulic bearing also includes a displacement chamber, which is connected to the first working chamber via a first displacement channel. The first working chamber and the second working chamber are configured such that the magnitude of the volume change during displacement of the inner core relative to the outer sleeve in a predetermined radial direction is greater for the first working chamber than for the second working chamber.

[0006] The configuration according to the invention advantageously enables fluid exchange to occur not only between the first working chamber and the second working chamber via the working channel when the inner core is displaced relative to the outer sleeve in the predetermined radial direction, but also between the first working chamber and the displacement chamber via the first displacement channel. By appropriately adjusting the respective configurations of the working channel and the first displacement channel, damping peaks can be achieved in two different frequency ranges, which allows for improved adjustability of the damping performance of the hydraulic bearing over the expected excitation frequency, particularly over a wide frequency range. The hydraulic bearing can also be referred to as a hydraulically damped bearing.

[0007] The escape chamber can be connected to the first working chamber fluidically or pressure-transmittingly via the first escape channel. "Fluidically connected" in the context of this application can mean that a fluid, for example glycol, can flow from the first working chamber to the escape chamber via the first escape channel and vice versa. In contrast, "pressure-transmitting connected" in the context of this application can mean that a pressure change within the first working chamber is transmitted from the first working chamber to the escape chamber via the first escape channel without any fluid exchange taking place between the first working chamber and the escape chamber. The same applies analogously in the reverse direction. For example, in a pressure-transmitting connection, an elastic deformation or displacement can occur.Vibration of a decoupling element located in the first or second escape channel, such as a decoupling membrane or a decoupling plate, causes a back-and-forth flow or oscillation of the fluid located in the corresponding escape channel, without any fluid exchange taking place between the corresponding working chamber and the corresponding escape chamber.

[0008] When the inner core moves relative to the outer sleeve, the volume of the first and second working chambers decreases or increases. These differing volume changes result in different pressure changes between the two chambers. Consequently, the fluid within the working chambers flows through the working channel from one chamber to the other, depending on the pressure difference, resulting in dissipation losses.In other words, during relative movements between the inner core and the outer sleeve, the fluid dampens vibrations, whereby, depending on the configuration of the working channel, such as the cross-section and / or the length of the working channel, a damping peak may occur in a (first) frequency range.

[0009] The relative movements between the inner core and the outer sleeve can also occur in a second frequency range during the operation of the hydraulic mount, which differs from the first frequency range. It may be desirable to adequately dampen vibrations in this second frequency range in addition to the first. In conventional hydraulic mounts, where the first working chamber is only connected to the second working chamber via the working channel, the damping performance in the second frequency range may be insufficient. It is even possible that the working channel is blocked in the second frequency range due to its configuration, preventing fluid exchange between the first and second working chambers or preventing fluid flow in the working channel. Consequently, no damping can occur, and the stiffness of the hydraulic mount increases in this frequency range.According to the invention, the first working chamber is therefore additionally connected to the bypass chamber via the first bypass channel, and the magnitude of the volume change during a displacement of the inner core relative to the outer sleeve in the predetermined radial direction is greater for the first working chamber than for the second working chamber. The volume change can be determined, in particular, during a displacement around the zero position. In other words, the active or effective piston area during the relative displacement is larger for the first working chamber than for the second working chamber.It is therefore ensured that if the inner core shifts relative to the outer sleeve in the predetermined radial direction, the volume change in the first working chamber cannot be absorbed solely by the volume change in the second working chamber, so that fluid and / or pressure transfer occurs between the first working chamber and the backup chamber via the first backup channel. This fluid and / or pressure transfer between the first working chamber and the backup chamber via the first backup channel also occurs, in particular, even if the working channel is not blocked at the relevant excitation frequency.By adjusting the configuration of the deflection channel, such as its cross-section and / or length, it is possible to create an additional damping peak in a (second) frequency range, thereby improving the damping performance of the hydraulic mount across the expected excitation frequency. Furthermore, the dynamic stiffness of the hydraulic mount can be reduced.

[0010] To improve the clarity of the present invention, the following is explained: Within the scope of this application, all directional terms such as "top," "bottom," "longitudinal," "transverse," "horizontal," and "vertical" refer, unless explicitly stated otherwise, to a three-dimensional Cartesian reference coordinate system fixed to the outer sleeve. The reference coordinate system is oriented such that an x-axis (longitudinal axis) of the three-dimensional Cartesian reference coordinate system passes through a center point of the outer sleeve. The outer sleeve may have a shape that is substantially rotationally symmetrical with respect to the x-axis.Therefore, the outer sleeve can have a substantially cylindrical shape and can extend from a zero point of the Cartesian reference coordinate system in both the negative and positive x-directions, with the outer sleeve having the same length in both the negative and positive x-directions. In other words, the zero point of the Cartesian reference coordinate system forms the center point of the outer sleeve. The terms "top," "bottom," and "vertical" refer to a z-axis of the reference coordinate system, whereas "longitudinal" refers to the x-axis of the Cartesian reference coordinate system, and "transverse" refers to a y-axis of the Cartesian reference coordinate system. The predetermined radial direction can, in particular, be the z-direction. The outer sleeve can be part of a first component that is or will be connected to the hydraulic bearing.Alternatively, the outer circumferential surface of the outer sleeve can serve as a mounting surface to connect the hydraulic bearing to the first component.

[0011] The first working chamber can have a larger volume than the second working chamber and can be located in the negative z-direction. Conversely, the second working chamber can be located in the positive z-direction. The volume of the first working chamber can be approximately 5-100%, preferably approximately 10-50%, and most preferably approximately 30% larger than the volume of the second working chamber. The first working chamber and / or the second working chamber can have a substantially circular arc-shaped cross-section in the yz-plane.

[0012] The inner core can be designed such that it is essentially mirror-symmetrical to the xz-plane of the reference coordinate system. More precisely, the inner core can have an essentially wedge-shaped or an essentially circular cross-section in the yz-plane of the reference coordinate system. Essentially wedge-shaped in this context means that the cross-section of the inner core in the yz-plane has a first obtuse end in the negative z-direction and a second obtuse end in the positive z-direction, whereby the first obtuse end may have a greater width in the transverse direction than the second obtuse end. The first obtuse end may face the first working chamber. The cross-section of the inner core in the yz-plane can essentially have the shape of an isosceles trapezoid. The first obtuse end and / or the second obtuse end may also be rounded.The inner core can have a longitudinal axis that substantially coincides with or runs parallel to the longitudinal axis of the outer sleeve. In particular, the inner core can be arranged substantially concentrically with the outer sleeve. The inner core can have a mounting recess or bore extending along its longitudinal axis through the inner core, allowing the hydraulic bearing to be connected to a second component by means of a mounting element, such as a screw, that passes through the mounting recess. The axial extent of the inner core can substantially correspond to the axial extent of the outer sleeve. The elastomer body can be injection-molded or vulcanized onto the inner core.

[0013] Alternatively, the first and second working chambers can have an essentially symmetrical shape in the yz plane, i.e., in the radial cross-section, and differ only in their length or extent in the x-direction, i.e., the axial direction. According to this embodiment, the different volumes of the two working chambers and the different piston areas of the corresponding pistons are achieved through the different lengths of the two working chambers in the x-direction. This embodiment offers the advantage that support arms provided on the elastomer body can be made of the same length and thickness, thus simplifying the manufacturing of the elastomer body and improving its robustness. Furthermore, this embodiment ensures that a "zero position" of the elastomer body is maintained even if it shrinks in the z- and y-directions.

[0014] The first and second working chambers can be bounded by the outer sleeve, the inner core, and the elastomer body. Alternatively, the elastomer body can enclose the inner core in such a way that the elastomer body and the outer sleeve together define the first and second working chambers. Additional components can also be located radially between the elastomer body and the outer sleeve. For example, an outer cage can be arranged between the elastomer body and the outer sleeve, radially surrounding the inner core. The outer cage can have a substantially cylindrical shape. The axial extent of the outer cage can substantially correspond to the axial extent of the outer sleeve and / or the inner core. The outer cage can be at least partially embedded in the elastomer body. The elastomer body can be injection-molded or vulcanized onto the inner core and the outer cage.The outer cage can be connected to the outer sleeve via a press fit or interference fit, whereby material of the elastomer body may be at least partially located between the outer cage and the outer sleeve. Alternatively, the outer cage can also be glued or otherwise attached to the inner circumferential surface of the outer sleeve.

[0015] The elastomer body can have a substantially x-shaped cross-section in the yz-plane. More precisely, the elastomer body can be designed such that its cross-section in the yz-plane has four support arms extending from the inner core to the outer sleeve or cage. It is also conceivable that the elastomer body has only two support arms. These support arms can also be referred to as spring arms.

[0016] The working channel connecting the first and second working chambers can extend at least partially along an outer circumferential surface of the elastomer body. More precisely, the elastomer body can have a recess or groove along its outer circumferential surface, which forms the working channel. The inner circumferential surface of the outer sleeve can radially delimit or seal the working channel. If the optional outer cage is used, the outer cage can have a recess or groove along its outer circumferential surface, which forms the working channel, and this recess may or may not be covered by a layer of the elastomer body material. The working channel can extend from the first working chamber in a circular arc circumferentially towards the second working chamber, but it can also include sections where it extends, for example, axially along the circumferential surface of the elastomer body.of the outer cage. The working channel can also be partially formed in an insert that at least partially closes off the first working chamber radially outwards.

[0017] The length of the working channel and / or its cross-section can influence the damping characteristics of the hydraulic mount. The length of the working channel can be increased by giving it a curved or zigzag shape. More precisely, the working channel can have several arc-shaped sections arranged parallel to each other in the x-direction. The working channel can have, at least in sections, a substantially square or rectangular cross-section with a cross-sectional area of ​​approximately 2 mm². 2 up to about 150 mm 2 , preferably of about 5 mm 2 up to about 100 mm 2 , most preferred from about 10 mm 2 up to about 50 mm 2 exhibit.

[0018] The first bypass channel connecting the first working chamber and the bypass chamber can extend at least partially along an outer circumferential surface of the elastomer body. More precisely, the elastomer body can have a recess or groove along its outer circumferential surface that forms the bypass channel. The inner circumferential surface of the outer sleeve can define or seal the bypass channel radially outward. If the optional outer cage is used, the outer cage can have a recess or groove along its outer circumferential surface that forms the bypass channel, the recess being either covered by a layer of the elastomer body material or not. The bypass channel can also be formed partially or completely within an insert that at least partially seals the first working chamber radially outward.

[0019] The length of the deflection channel and / or its cross-section can influence the damping characteristics of the hydraulic mount. The length of the deflection channel can be increased by giving it a curved or zigzag shape. The deflection channel can, at least in sections, have a substantially square or rectangular cross-section with a cross-sectional area of ​​approximately 5 mm². 2 up to about 200 mm 2 , preferably of about 10 mm 2 up to about 150 mm 2 , most preferred from about 20 mm 2 up to about 100 mm 2 exhibit.

[0020] Preferably, the hydraulic bearing has a first sealing element which is arranged at a first axial end of the hydraulic bearing in order to at least partially limit the displacement chamber in the axial direction.

[0021] Advantageously, by providing the first sealing element, a free space between the outer sleeve and the inner core can be easily used as a backup chamber.

[0022] The first sealing element can be made at least partially of a plastic, in particular an elastic plastic such as an elastomer. The first sealing element can be essentially disc-shaped and radially connected on its inner side to a first axial end of the inner core and radially on its outer side to a first axial end of the outer sleeve and / or the outer cage, for example by an interference fit and / or adhesive bond. For this purpose, the first sealing element can have an outer retaining ring at its radial outer end and / or an inner retaining ring at its radial inner end, wherein the outer retaining ring and / or inner retaining ring can be made of metal or plastic. The first sealing element can be designed at least partially as a membrane and / or bellows. This offers the advantage that the first sealing element allows for low-resistance volume changes in the escape chamber.In particular, the wall thickness of the first sealing element, measured at its thinnest point, may be significantly thinner than the wall thickness of the parts of the elastomer body that define the first working chamber or the second working chamber, measured at their thinnest point, for example, less than about 20%, less than about 10% or less than about 5%.

[0023] In this context, the hydraulic bearing preferably comprises a second sealing element, which is arranged at a second axial end of the hydraulic bearing in order to at least partially limit the displacement chamber in the axial direction. Optionally, the elastomer body has at least one through-hole extending in the axial direction, which forms part of the displacement chamber.

[0024] With this design, a hydraulic bearing with a particularly large expansion chamber can be provided, extending especially over the entire axial length between the axial ends of the hydraulic bearing. The second sealing element can be designed analogously to the first sealing element, whereby the above descriptions for the first sealing element can apply accordingly to the second sealing element, particularly with regard to the second axial end. This enables a particularly large, low-resistance volume change of the expansion chamber.

[0025] Preferably, the bypass chamber is additionally connected to the first working chamber via a first bypass secondary channel.

[0026] The above configuration offers the advantage that the damping characteristics of the hydraulic mount can be adjusted even more precisely via the excitation frequency. In particular, by adjusting the configuration of the first auxiliary channel—for example, its arrangement, cross-sectional area, and / or length—a further (third) frequency range can be provided in which another damping peak occurs. The first auxiliary channel is configured differently from the first auxiliary channel.

[0027] Preferably, the bypass chamber is connected to the second working chamber via a second bypass channel.

[0028] This offers the advantage of a further adjustment option for the damping characteristics of the hydraulic mount via the excitation frequency. In particular, by adjusting the configuration of the second escape channel, i.e., for example, its arrangement, cross-sectional size and / or length, a further (fourth) frequency range can be provided in which another damping peak occurs.

[0029] The second bypass channel can have a shape analogous to the first bypass channel. It is also conceivable that the second bypass channel differs from the first, for example, in its configuration, such as its length, cross-sectional area, and / or cross-sectional shape.

[0030] In this context, the bypass chamber is preferably additionally connected to the second working chamber via a second bypass auxiliary channel.

[0031] The above configuration offers the advantage that the damping characteristics of the hydraulic mount can be further adjusted via the excitation frequency. In particular, by adjusting the configuration of the second bypass channel, i.e., its arrangement, cross-sectional area, and / or length, a further (fifth) frequency range can be provided in which another damping peak occurs. The second bypass channel is configured differently from the second bypass channel.

[0032] The bypass channels and bypass secondary channels can each be configured to extend at least partially substantially in the axial or x-direction of the bearing, or to extend at least partially substantially in the circumferential direction of the bearing, or to extend both partially substantially in the x-direction and partially substantially in the circumferential direction of the bearing. The bypass channels and bypass secondary channels can each be radially bounded outwards by the outer sleeve. For example, a configuration is conceivable in which the second bypass channel extends substantially in the x-direction, while the second bypass secondary channel extends substantially in the circumferential direction, i.e., within the yz-plane. The same applies to the first bypass channel and the first bypass secondary channel. A reverse configuration is also conceivable.

[0033] Preferably, the bypass chamber is divided into a first sub-bypass chamber and a second sub-bypass chamber. The first sub-bypass chamber can be connected to the first working chamber via the first bypass channel and / or the first bypass auxiliary channel (if provided). The second sub-bypass chamber can be connected to the second working chamber via the second bypass channel and / or the second bypass auxiliary channel (if provided).

[0034] The above configuration offers the advantage of providing two separate sub-basic chambers, each connected to the first working chamber via the first sub-basic channel and / or the first sub-basic channel (if provided), and to the second working chamber via the second sub-basic channel and / or the second sub-basic channel (if provided). This allows for more precise adjustment of the damping characteristics across the excitation frequency. The first sub-basic chamber and the second sub-basic chamber can be separated by a partition, which may be part of the elastomer body. The partition can be configured such that essentially no pressure exchange occurs between the first and second sub-basic chambers across it.For example, the partition wall can extend essentially in the yz plane or parallel to it, the first lower escape chamber can be at least partially bounded axially outwards by the first sealing element, and the second lower escape chamber can be at least partially bounded axially outwards by the second sealing element. Alternatively, the partition wall can also extend essentially in the xy plane or parallel to it.

[0035] Preferably, a decoupling element is arranged in the first bypass channel and / or in the first bypass branch channel and / or in the second bypass channel and / or in the second bypass branch channel. In other words, the aforementioned channels can each be designed with or without a decoupling element. For example, a decoupling element can be arranged only in the first bypass channel, while the second bypass channel and the bypass branch channels, if present, can be free of decoupling elements. However, for example, the first and second bypass channels, as well as the first and second bypass branch channels, if present, can each have a decoupling element.

[0036] The inclusion of one or more decoupling elements further improves the adjustability of the hydraulic mount's damping characteristics. In particular, a decoupling element can be used to selectively reduce the hydraulic mount's dynamic stiffness at a specific frequency or within a specific frequency range. The decoupling element can be configured as a freely oscillating decoupling plate that allows both fluid and pressure transmission, or as a decoupling membrane that is arranged to seal and allows only pressure transmission. The decoupling element and the corresponding channel can be configured such that the decoupling element oscillates back and forth within a specific excitation frequency range, thus enabling a damping-generating back-and-forth flow of fluid within the channel with little or no significant fluid exchange between the respective chambers.

[0037] Preferably, the hydraulic bearing comprises a first insert element arranged between the elastomer body and the outer sleeve, partially delimiting the first working chamber, with the first deflection channel being at least partially located in the first insert element. Optionally, the first secondary deflection channel is at least partially located in the first insert element.

[0038] The above configuration allows for easy provision of the first bypass channel and / or the first bypass secondary channel. The radial inner surface of the first insert can also serve as the first radial stop for the inner core.

[0039] Preferably, the hydraulic bearing in this context has a second insert element, which is arranged between the elastomer body and the outer sleeve and partially delimits the second working chamber, wherein the second deflection channel is at least partially arranged in the first insert element. Optionally, the second deflection channel is at least partially arranged in the first insert element.

[0040] The above configuration allows for easy provision of the second bypass channel and / or the second bypass auxiliary channel. The radial inner surface of the second insert can also serve as a second radial stop for the inner core. The first and second inserts can be positioned essentially diametrically opposite each other on the hydraulic bearings.

[0041] As an alternative to being arranged in the first and / or second insert, the decoupling element can also be arranged at an axial end of the outer sleeve. In particular, the decoupling element can be clamped between the outer retaining ring of the sealing element and an axial end section of the outer cage, extending, for example, substantially in the axial direction. The decoupling element can also be arranged or clamped in a decoupling element retaining ring, extending substantially in the radial direction, wherein the decoupling element retaining ring is pressed into the outer sleeve and / or clamped between the outer retaining ring of the sealing element and an axial end section of the outer cage.

[0042] Preferably, in this context, the respective decoupling element is arranged in the first insert and / or in the second insert.

[0043] The above configuration allows for easy placement of the respective decoupling element in the first insert and / or the second insert. In particular, the first insert and / or the second insert can be multi-part, for example, two-part, and enclose the corresponding decoupling element within.

[0044] The following section describes embodiments of the invention in detail with reference to the accompanying figures. It is understood that the invention is not limited to these embodiments, but that individual features disclosed in the present description can be combined to form further embodiments.

[0045] They show: Fig. 1 a schematic representation of a cross-section of a hydraulic bearing according to a first embodiment; Fig. 2 a schematic representation of a further cross-section of the hydraulic bearing according to the first embodiment; Fig. 3 a schematic representation of a cross-section of a hydraulic bearing according to a second embodiment; Fig. 4 a schematic representation of a further cross-section of the hydraulic bearing according to the second embodiment; Fig. 5 a schematic representation of a cross-section of a hydraulic bearing according to a third embodiment; Fig. 6 a schematic representation of a cross-section of a hydraulic bearing with an elastomer body with two support arms; Fig. 7 a schematic representation of a cross-section of a hydro bearing with an elastomer body with four support arms; Fig. 8 a schematic representation of a cross-section of the hydraulic bearing according to the first embodiment, showing various channels and fluid flow directions; and Fig. 9 A schematic representation of a cross-section of the hydraulic bearing according to the second embodiment, showing different channels and fluid flow directions.

[0046] Fig. Figure 1 shows a cross-section of a hydraulic bearing 1 in a yz-plane of a Cartesian reference coordinate system fixed to an outer sleeve 3 of the hydraulic bearing 1, the zero point of which coincides with a center point of the outer sleeve 3.

[0047] As from Fig. As can be seen in Figure 1, the hydraulic bearing 1 comprises, in addition to the outer sleeve 3, an inner core 2, an outer cage 7, and an elastomer body 4 extending between the inner core 2 and the outer sleeve 3. The outer sleeve 3 has a cylindrical shape and surrounds the inner core 2 in a radial direction. In this case, the outer sleeve 3 is made of a metal, but it can also comprise at least some sections of plastic, in particular fiber-reinforced plastic.

[0048] The inner core 2 comprises a tubular inner element with a circular cross-section in the yz-plane, extending in the x-direction, and a piston extending radially around the inner element. The piston has a substantially wedge-shaped form in the yz-plane and features a first blunt end and a second blunt end. The first blunt end, located in the negative z-direction, is wider in the transverse direction than the second blunt end, located in the positive z-direction. The transverse flanks of the piston are rounded. The piston can be molded from plastic and injection-molded onto the inner element, which can be made of metal.

[0049] The elastomer body 4 elastically connects the inner core 2 and the outer sleeve 3 or the outer cage 7 such that the inner core 2 is movable relative to the outer sleeve 3 or relative to the outer cage 7. The elastomer body 4 has a substantially x-shaped form in the yz-plane with four support arms extending from the inner core 2 towards the outer sleeve 3. The elastomer body 4 can be injection-molded or vulcanized onto the outer cage 7 and the inner core 2. As can be seen from the Fig. 1 and Fig. As can be seen in Figure 2, the elastomer body 4 essentially surrounds the inner core 2 in a radial direction.

[0050] The hydraulic bearing 1 also has a first working chamber 5 and a second working chamber 6, which are fluidically connected to each other via a working channel (not shown). As shown Fig. 1 and Fig. As can be seen in Figure 2, the first working chamber 5 is located in the negative z-direction. In contrast, the second working chamber is located in the positive z-direction. A first insert 16 is arranged in the negative z-direction between the elastomer body 4 and the outer sleeve 2. Furthermore, a second insert 17 is arranged in the positive z-direction between the elastomer body 4 and the outer sleeve 3. The first working chamber 5 is therefore bounded by the elastomer body 4 and the first insert 16. The second working chamber 6, on the other hand, is bounded by the elastomer body 4 and the second insert 17.

[0051] The outer cage 7 has a substantially tubular shape with a substantially circular cross-section. The outer cage 7 has two recesses on two radially outer areas, in which the first insert 15 can be inserted into one of the two recesses and the second insert 17 into the other of the two recesses in such a way that the inserts can be supported at least indirectly via the elastomer body 4 on the outer cage 7.

[0052] The elastomer body 4, manufactured here as an injection-molded part and enclosing the piston of the inner core 2, has a first piston surface in the region of the first blunt end of the piston of the inner core 2. In contrast, the elastomer body 4 has a second piston surface in the region of the second blunt end of the piston of the inner core. In other words, the first piston surface and the second piston surface of the elastomer body 4 each represent an extension of the piston of the inner core 2. During relative movement of the inner core 2 to the outer sleeve 3, particularly in the z-direction, the first piston surface and the second piston surface change the volume of the first working chamber 5 and the second working chamber 6, depending on the direction of movement of the inner core 2 and / or the outer sleeve 3.For example, when the inner core 2 is displaced in the positive z-direction, the second piston surface of the elastomer body 4 is displaced in the positive z-direction along with the first piston surface of the elastomer body 4. As a result, the volume of the second working chamber 6 decreases, while the volume of the first working chamber 5 increases, with the magnitude of the corresponding volume change being greater for the first working chamber 6 than for the second working chamber 6. In other words, when the inner core 2 is displaced, the volume of the first working chamber 6 increases more than the volume of the second working chamber decreases. The same applies to a displacement of the inner core 2 in the negative z-direction.

[0053] The different volume changes in the first working chamber 5 and in the second working chamber 6 lead to different pressure changes in the first working chamber 5 and in the second working chamber 6. As a result of the pressure changes in the two working chambers 5, 6, a fluid located in the working chambers 5, 6 flows through the working channel from one of the two working chambers 5, 6 to the other, depending on the different pressures in the two working chambers 5, 6. When the fluid flows from one working chamber to the other through the working channel, dissipation losses occur in the working channel, which dampen, for example, relative movements or vibrations between a component (not shown) of a vehicle attached to the hydraulic mount 1 and a vehicle body (not shown) also coupled to the hydraulic mount 1. The damping performance can be determined at a specific frequency or...exhibit a damping peak in a first frequency range.

[0054] As from the Fig. 1 and Fig. As can be seen in Figure 2, the hydraulic bearing 1 according to the first embodiment is designed such that a first deflection channel 9 is arranged between the inner circumferential surface of the outer sleeve 3, the cage 7 and the first insert 16. Furthermore, a second deflection channel 14 is arranged between the inner circumferential surface of the outer sleeve 3, the cage 7 and the second insert 14.

[0055] The first diversion channel 9 and the second diversion channel 14 run essentially in the positive x-direction and lead into a diversion chamber 8 located in the positive x-direction.

[0056] The displacement chamber 8 is bounded in the positive x-direction by a first sealing element 10 located at a first axial end 11 of the hydraulic bearing 1. The first sealing element 10, comprising an elastic plastic or elastomer, is bellows-shaped, allowing for low-resistance volume changes in the displacement chamber through deformation of the first sealing element 10. At a second axial end 13 of the hydraulic bearing 1, opposite the first axial end 10, there is a second sealing element 12, also bellows-shaped and likewise comprising an elastic plastic or elastomer.

[0057] The first insert 16 has at least one recess or cutout extending in the z-direction, which connects the first working chamber 5 and the first bypass channel 9. The first insert 16 can, in particular, have two, three, or, as in the present case, four recesses. According to the first embodiment, a decoupling element 15, designed as a flexible decoupling membrane, is located within the four recesses and fluidically separates the first working chamber 5 from the bypass chamber 8. However, the first working chamber 5 and the bypass channel 8 remain pressure-transmittingly connected to each other via the first bypass channel 9. The second insert 17 is designed analogously to the first insert 16 and also has a decoupling element 15, which fluidly separates the second working chamber 6 from the bypass chamber 8.The second working chamber 6, however, remains pressure-transmittingly connected to the bypass chamber 8 via the second bypass channel 14. The configuration of the inserts 16, 17, the bypass channels 9, 14, and the decoupling elements 15, 16 can be varied depending on the requirements or available installation space. As shown in the... Fig. 1 and Fig. As can be seen in Figure 2, in the present case the two insert parts 16, 17 are each designed in two parts, so that the respective decoupling element 15 inserted into the insert parts 16, 17 can be easily inserted or replaced.

[0058] The Fig. 3 and Fig. Figure 4 shows a hydraulic bearing 1 according to the invention in a second embodiment. The hydraulic bearing 1 according to the second embodiment corresponds in a substantial part of its design to the hydraulic bearing 1 according to the first embodiment. Therefore, only the differences between the two embodiments are explained in more detail below.

[0059] Unlike the hydraulic mount 1 according to the first embodiment, the hydraulic mount 1 according to the second embodiment has only one insert 17. Furthermore, the displacement chamber 8 according to the second embodiment is connected to the first working chamber 5 only via the first displacement channel 9. Unlike the hydraulic mount 1 according to the first embodiment, the second working chamber 6 of the hydraulic mount 1 according to the second embodiment is not connected to the displacement chamber 8. Therefore, the hydraulic mount 1 according to the second embodiment does not have a second displacement channel 14.

[0060] According to the second embodiment, the damping of vibrations in the first frequency range is analogous to the first embodiment, achieved by means of the fluid flowing between the first working chamber 5 and the second working chamber 6 via the working channel. In contrast, vibrations in the second frequency range are damped solely by the fluid flowing in the first bypass channel 9. This design is advantageous due to its simple construction.

[0061] Fig. Figure 5 shows a hydraulic bearing 1 according to a third embodiment, in which the first working chamber 5 and the second working chamber 6 have a substantially symmetrical shape in the yz-plane, i.e., in the radial cross-section at the center of the hydraulic bearing, and differ from each other only with respect to their length or extent in the x-direction. According to this embodiment, the different volumes of the two working chambers 5, 6 are achieved by the different lengths or extents of the two working chambers 5, 6 in the x-direction. As can be seen from Fig. As can be seen in Figure 5, according to this embodiment, the outer cage 7 is radially internal and radially externally surrounded or encased at least partially by the elastomer body 4. The essentially symmetrical design of the working chambers 5, 6 in the radial cross-section offers the advantage that the support arms provided in the elastomer body 4 can also be designed essentially symmetrically, in particular with essentially the same length and thickness, which makes the elastomer body 4 easier to manufacture and improves its robustness. Furthermore, this design ensures that a "zero position" of the elastomer body 4 is maintained in the event of shrinkage in the z and y directions.

[0062] The Fig. 6 and Fig. Figures 7 show, in simplified form, how the elastomer body 4 of the hydro-bearing 1 can be configured in radial cross-section with respect to its support arms according to the third embodiment. Simplified form in this context means that the outer cage 7 and certain sections of the elastomer body 4 are not shown.

[0063] As from Fig. As can be seen in Figure 6, the elastomer body 4 can only have two opposing support arms of essentially the same thickness and width, so that the first working chamber 5 and the second working chamber 6 are symmetrical to each other in the yz-plane.

[0064] As from Fig. As can be seen from Figure 7, the elastomer body 4 can also have four support arms which are x-shaped in the yz-plane, wherein the four support arms each have essentially the same thickness and width and are arranged such that the first working chamber 5 and the second working chamber 6 are symmetrical to each other in the yz-plane.

[0065] Fig. Figure 8 shows the hydraulic bearing 1 according to the first embodiment with the fluid flow directions indicated. As shown in Figure 8, the hydraulic bearing 1 according to the first embodiment is shown in Figure 8. Fig. As can be seen in Figure 8, the first working chamber 5 and the second working chamber 6 are fluidically connected, allowing fluid exchange between them and damping of vibrations of the hydraulic bearing 1 in a first frequency range during operation. In contrast, the first working chamber 5 and the second working chamber 6 are each pressure-transmitting and connected to the bypass chamber 8 via a bypass channel 9, 14. The bypass chamber 8 can be subdivided into a first sub-bypass chamber and a second sub-bypass chamber, such that the first and second sub-bypass chambers are separated from each other by a wall extending essentially in the xy-plane from the inner core 2 in the y-direction.Deformations or vibrations of the decoupling element 15 arranged in the first insert 16, due to pressure changes in the first working chamber 5, cause the fluid located in the first bypass channel 9 to oscillate or flow back and forth within the first bypass channel 9, thus damping vibrations of the hydraulic mount 1 in a second frequency range. Deformations or vibrations of the decoupling element 15 arranged in the second insert 17, due to pressure changes in the second working chamber 6, cause the fluid located in the second bypass channel 14 to oscillate or flow back and forth within the second bypass channel 14, thus damping vibrations of the hydraulic mount 1 in a further frequency range.In particular, the first diversion channel 9 and the second diversion channel 14 and / or the decoupling element 15 of the first diversion channel 9 and the decoupling element 15 of the second diversion channel 14 can be configured differently to set the respective frequency ranges.

[0066] Fig. Figure 9 shows the hydraulic bearing 1 according to the second embodiment with the fluid flow directions indicated. As shown in Figure 9, the hydraulic bearing 1 according to the second embodiment is shown in Figure 9. Fig.As can be seen in Figure 9, the first working chamber 5 and the second working chamber 6 are fluidically connected, allowing fluid exchange between the two chambers 5 and 6. This damping of vibrations of the hydraulic mount 1 in a first frequency range during operation is achieved. In contrast, the first working chamber 5 is pressure-transmittingly connected to the displacement chamber 8. Deformations or vibrations of the decoupling element 15 arranged in the first insert 16, due to pressure changes in the first working chamber 5, cause the fluid in the first displacement channel 9 to oscillate or flow back and forth within the first displacement channel 9, thus damping vibrations of the hydraulic mount 1 in a second frequency range. Reference symbol list 1 hydraulic bearing 2 inner core 3 Outer sleeve 4 elastomer bodies 5 first chamber of labor 6 second chamber of labor 7 outer cages 8 Backup chamber 9 first diversion channel 10 first sealing element 11 first axial end of the hydraulic bearing 12 second sealing element 13 second axial end of the hydraulic bearing 14 second escape route 15 decoupling element 16 first insert 17 second insert

Claims

[1] Hydro bearing (1), comprising: an inner core (2), an outer sleeve (3) which radially surrounds the inner core (2), an elastomer body (4) which elastically connects the inner core (2) and the outer sleeve (3) to allow relative displacement between the inner core (2) and the outer sleeve (3), a first working chamber (5) and a second working chamber (6) which are fluidically connected to one another via a working channel, an alternative chamber (8) which is connected to the first working chamber (5) via a first alternative channel (9), wherein the first working chamber (5) and the second working chamber (6) are configured such that an amount of volume change upon displacement of the inner core (2) relative to the outer sleeve (3) in a predetermined radial direction is greater for the first working chamber (5) than for the second working chamber (6). [2] Hydraulic bearing (1) according to claim 1, further comprising a first sealing element (10), wherein the first sealing element (10) is arranged at a first axial end (11) of the hydraulic bearing (1) in order to at least partially delimit the escape chamber (8) in the axial direction. [3] Hydro bearing (1) according to claim 2, further comprising a second sealing element (12), wherein the second sealing element (12) is arranged at a second axial end (13) of the hydro bearing in order to at least partially delimit the escape chamber (8) in the axial direction, wherein the elastomer body (4) optionally has at least one through-cutout extending in the axial direction, which forms part of the escape chamber (8). [4] Hydraulic bearing (1) according to one of the preceding claims, wherein the escape chamber (8) is additionally connected to the first working chamber via a first escape secondary channel. [5] Hydraulic bearing (1) according to one of the preceding claims, wherein the escape chamber (8) is connected to the second working chamber (6) via a second escape channel (14). [6] Hydro bearing (1) according to claim 5, wherein the escape chamber (8) is additionally connected to the second working chamber (6) via a second escape secondary channel. [7] Hydraulic bearing (1) according to one of claims 5 or 6, wherein the escape chamber (8) is divided into a first sub-escape chamber and a second sub-escape chamber, wherein the first sub-escape chamber is connected to the first working chamber (5) via the first escape channel (9) and / or the first escape sub-channel, and the second sub-escape chamber is connected to the second working chamber (6) via the second escape channel (14) and / or the second escape sub-channel. [8] Hydraulic bearing (1) according to one of the preceding claims, wherein a decoupling element (15) is arranged in the first escape channel (9) and / or in the first escape secondary channel and / or in the second escape channel (14) and / or in the second escape secondary channel. [9] Hydro bearing (1) according to one of the preceding claims, further comprising a first insert part (16) which is arranged between the elastomer body (4) and the outer sleeve (3) and partially delimits the first working chamber (5), wherein the first escape channel (9) is arranged at least partially in the first insert part (16), and wherein optionally the first escape secondary channel is arranged at least partially in the first insert part (16). [10] Hydro bearing (1) according to claim 9, further comprising a second insert part (17) which is arranged between the elastomer body (4) and the outer sleeve (3) and partially delimits the second working chamber (6), wherein the second escape channel (14) is at least partially arranged in the second insert part (17), and wherein optionally the second escape secondary channel is at least partially arranged in the second insert part (17). [11] Hydro bearing (1) according to claim 9 or 10, dependent on claim 8, wherein the respective decoupling element (15) is arranged in the first insert part (16) and / or in the second insert part (17).

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