Hydrodynamic bearing

Abstract

According to the present invention, a hydraulic bearing (1) is provided, comprising: an inner core (2); an outer sheath (3) radially surrounding the inner core (2); an elastomer body (4) elastically connecting the inner core (2) and the outer sheath (3) to allow relative displacement between the inner core (2) and the outer sheath (3); a first working chamber (5) and a second working chamber (6) fluidly connected to each other via a working channel; and a bypass chamber (8) connected to the first working chamber (5) via a first bypass channel (9), wherein the first working chamber (5) and the second working chamber (6) are configured such that when the inner core (2) is displaced relative to the outer sheath (3) in a predetermined radial direction, the volume change of the first working chamber (5) is greater than the volume change of the second working chamber (6).

Description

Technical Field

[0001] This invention relates to a hydraulic bearing, particularly a hydraulic bearing for motor vehicles. The hydraulic bearing can be used, for example, to support axle supports or wheel guides, especially lateral guides. Furthermore, the hydraulic bearing can be used as a unit bearing, such as an engine bearing. Additionally, the hydraulic bearing can be used to elastically support the cab of construction machinery or agricultural machinery. Background Technology

[0002] Hydraulic bearings are typically used when the relative motion of vibration-exposed components, such as motor vehicle parts, relative to the vehicle body is permitted and should be damped. Hydraulic bearings provide the spring force restored by the use of elastomeric materials, as well as the damping force actively generated by dissipation losses within the bearing. Summary of the Invention

[0003] The purpose of this invention is to provide a novel hydraulic bearing capable of achieving high damping power over a wide frequency range.

[0004] To achieve the above objectives, the present invention proposes a hydraulic bearing having the features described in the independent technical solution. Preferred embodiments of the present invention are described in the dependent technical solution.

[0005] According to the present invention, a hydraulic bearing is provided, comprising an inner core and an outer sheath radially surrounding the inner core. The hydraulic bearing according to the present invention further comprises an elastomer body that elastically connects the inner core and the outer sheath to allow relative displacement between the inner core and the outer sheath. The hydraulic bearing further comprises a first chamber and a second chamber fluidly connected to each other via a working channel. Furthermore, the hydraulic bearing includes a bypass chamber connected to the first chamber via a first bypass channel. The first and second chambers are configured such that when the inner core is displaced relative to the outer sheath in a predetermined radial direction, the volume change of the first chamber is greater than the volume change of the second chamber.

[0006] The configuration according to the invention advantageously enables fluid exchange not only between the first and second working chambers via the working channel, but also between the first working chamber and the bypass chamber via the first bypass channel, when the inner core is displaced relative to the outer sheath in a predetermined radial direction. By appropriately adjusting the corresponding configurations of the working channel and the first bypass channel, damping peaks can be obtained in two different frequency ranges, thus improving the adjustability of the damping power of the hydraulic bearing at the expected excitation frequency, especially over a wide frequency range. The hydraulic bearing can also be referred to as a hydraulically damped bearing.

[0007] The bypass chamber can be fluidly or pressure-transmittedly connected to the first working chamber via a first bypass channel. In the context of this application, "fluidly connected" can mean that a fluid (e.g., ethylene glycol) can flow from the first working chamber into the bypass chamber via the first bypass channel, and vice versa. In contrast, in the context of this application, "pressure-transmitting connection" can mean that pressure changes within the first working chamber are transmitted from the first working chamber to the bypass chamber via the first bypass channel, without fluid exchange between the first working chamber and the bypass chamber. The same applies to the reverse direction. For example, in the case of a pressure-transmitting connection, elastic deformation, displacement, or vibration of a decoupling element (such as a decoupling membrane or decoupling plate) arranged in the first or second bypass channel may cause reciprocating flow or vibration of the fluid in the corresponding bypass channel, without fluid exchange between the corresponding working chamber and the corresponding bypass chamber.

[0008] As the inner core moves relative to the outer sheath, the volumes of the first and second working chambers decrease or increase. These different volume changes in the first and second working chambers result in different pressure changes within them. Due to these pressure changes, fluid flows from one of the two working chambers into the other through the working channel, depending on the different pressures in the two chambers, resulting in dissipation losses. In other words, during the relative motion between the inner core and the outer sheath, fluid-damped vibrations occur, where damping peaks can appear in the (first) frequency range depending on the configuration of the working channel, such as its cross-section and / or length.

[0009] In the operation of a hydraulic bearing, the relative motion between the inner core and the outer sheath can also occur within a second frequency range, which differs from the first frequency range. In addition to the first frequency range, it may be desirable to adequately dampen vibrations within this second frequency range. For conventional hydraulic bearings, where the first working chamber is connected to the second working chamber only via a working channel, the damping power within the second frequency range may be insufficient. It is even possible that the working channel is blocked due to its configuration within the second frequency range, preventing fluid exchange between the first and second working chambers or eliminating fluid flow in the working channel, thus preventing any further damping and increasing the stiffness of the hydraulic bearing in this frequency range. Therefore, according to the invention, the first working chamber is additionally connected to a bypass chamber via a first bypass channel, such that when the inner core displaces relative to the outer sheath in a predetermined radial direction, the volume change of the first working chamber is greater than that of the second working chamber. This volume change is particularly evident when displacement occurs near the zero position. In other words, during relative displacement, the effective or acting piston area of ​​the first working chamber is greater than that of the second working chamber. This ensures that when the inner core displaces relative to the outer sheath in a predetermined radial direction, the volume change in the first working chamber is not solely absorbed by the volume change in the second working chamber, thus preventing fluid and / or pressure transmission between the first working chamber and the bypass chamber via the first bypass channel. Fluid and / or pressure transmission between the first working chamber and the bypass chamber via the first bypass channel also occurs when the working channel is not blocked at the relevant excitation frequency. Therefore, by adjusting the configuration of the bypass channel, such as its cross-section and / or length, additional damping peaks can be achieved in the (second) frequency range, thereby increasing the damping power of the hydraulic bearing at the expected excitation frequency. Furthermore, the dynamic stiffness of the hydraulic bearing can be reduced.

[0010] To enhance understanding of the invention, the following description is provided: In the context of this application, all directional information such as “up,” “down,” “longitudinal” or “vertical,” “lateral” or “horizontal,” “horizontal,” and “vertical” refer to a three-dimensional Cartesian reference coordinate system attached to the outer sheath, unless otherwise explicitly stated. The reference coordinate system is oriented such that the x-axis (vertical axis) of the three-dimensional Cartesian reference coordinate system passes through the center point of the outer sheath. The outer sheath may have a shape that is substantially rotationally symmetric about the x-axis. Therefore, the outer sheath may be substantially cylindrical and may extend from the zero point of the Cartesian reference coordinate system along both the negative and positive x-axis directions, wherein the outer sheath may have equal lengths in both directions. In other words, the zero point of the Cartesian reference coordinate system forms the center point of the outer sheath. The information “up,” “down,” and “vertical” refers to the z-axis of the reference coordinate system, while the information “longitudinal” or “vertical” refers to the x-axis of the Cartesian reference coordinate system, and the information “lateral” or “horizontal” refers to the y-axis of the Cartesian reference coordinate system. The predetermined radial direction may be, in particular, the z-direction. The outer sheath may be part of a first component connected to a hydraulic bearing. Alternatively, the outer peripheral surface of the outer sheath can be used as a mounting surface for connecting the hydraulic bearing to the first component.

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

[0012] The inner core can be designed to be substantially mirror-symmetric with respect to the xz plane of the reference coordinate system. Specifically, the inner core can have a substantially wedge-shaped or substantially circular cross-section in the yz plane of the reference coordinate system. In this sense, "substantially wedge-shaped" means that the cross-section of the inner core in the yz plane has a first blunt end in the negative z-axis direction and a second blunt end in the positive z-axis direction, wherein the first blunt end has a greater width in the transverse direction than the second blunt end. The first blunt end can face the first working chamber. The cross-section of the inner core in the yz plane can be substantially isosceles trapezoidal. The first blunt end and / or the second blunt end can also be rounded. The longitudinal axis of the inner core can substantially coincide with or be parallel to the longitudinal axis of the outer sheath. The inner core can be arranged substantially concentrically with the outer sheath, in particular. The inner core can have an assembly slot or assembly hole extending along the longitudinal axis of the inner core, through which a hydraulic bearing can be connected to a second component via an assembly (e.g., a screw), which guides the assembly through the assembly slot. The axial extension of the inner core can substantially correspond to the axial extension of the outer sheath. The elastomer body can be injection molded or vulcanized onto the inner core.

[0013] Alternatively, the first and second working chambers can have a substantially symmetrical configuration in the yz plane (i.e., in the radial cross-section), differing only in length or extension in the x-direction (i.e., the axial direction). According to this design, the different volumes of the two working chambers and the corresponding piston areas are achieved through the different lengths of the two working chambers in the x-direction. This design offers the advantage that the support arms located at the elastomer body can be designed to have equal lengths and thicknesses, thus simplifying the manufacture of the elastomer body and enhancing its robustness. Furthermore, according to this design, the elastomer body can be kept at a "zero position" even when it contracts along the z and y directions.

[0014] The first and second working chambers can be defined by an outer sheath, an inner core, and an elastomer body. Alternatively, the elastomer body can surround the inner core, such that the elastomer body and the outer sheath define the first and second working chambers. Other components may also exist radially between the elastomer body and the outer sheath. For example, an outer cage radially surrounding the inner core can be arranged between the elastomer body and the outer sheath. The outer cage can be substantially cylindrical. The axial extension of the outer cage can substantially correspond to the axial extension of the outer sheath 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 sheath by press-fitting or press-fitting, wherein the material of the elastomer body can be at least partially arranged between the outer cage and the outer sheath. Alternatively, the outer cage can also be bonded or otherwise fastened to the inner circumferential surface of the outer sheath.

[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 supporting arms extending from the inner core to the outer sheath or outer cage. Alternatively, the elastomer body can have only two supporting arms. These supporting 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 the outer peripheral surface of the elastomer body. Specifically, the elastomer body can have a recess or groove forming the working channel along its outer peripheral surface. The inner peripheral surface of the outer sheath can radially outwardly define or seal the working channel. If an optional outer cage is used, the outer cage can have a recess or groove forming the working channel along its outer peripheral surface, wherein the recess may or may not be covered by a material layer of the elastomer body. The working channel can extend in an arcuate shape from the first working chamber toward the second working chamber in the circumferential direction, but may also include, for example, a section extending axially along the circumferential surface of the elastomer body or the outer cage. The working channel can also be partially constructed in an insert that at least partially radially outwardly encloses the first working chamber.

[0017] The length and / or cross-section of the working channel can affect the damping characteristics of the hydraulic bearing. The length of the working channel can be increased, specifically by having an arcuate or zigzag path. More precisely, the working channel can have multiple arcuate segments arranged parallel to each other in the x-direction. The working channel can at least segmentally have a substantially square or rectangular cross-section with a cross-sectional area of ​​approximately 2 mm². 2 Approximately 150mm 2 Preferably about 5mm 2 Approximately 100mm 2 The optimal size is approximately 10mm. 2 approximately 50mm 2 .

[0018] A first bypass channel connecting the first working chamber to the bypass chamber may extend at least partially along the outer peripheral surface of the elastomer body. Specifically, the elastomer body may have a recess or groove forming the bypass channel along its outer peripheral surface. The inner peripheral surface of the outer sheath may radially define or seal the bypass channel outward. If an optional outer cage is used, the outer cage may have a recess or groove forming the bypass channel along its outer peripheral surface, wherein the recess may or may not be covered by a material layer of the elastomer body. The bypass channel may also be partially or completely constructed in an insert that at least partially radially closes the first working chamber.

[0019] The length and / or cross-section of the bypass channel can affect the damping characteristics of the hydraulic bearing. The length of the bypass channel can be increased, specifically by having a curved or zigzag path. The bypass channel can have a substantially square or rectangular cross-section, at least in segments, with a cross-sectional area of ​​approximately 5 mm². 2 Approximately 200mm 2 Preferably about 10mm 2 Approximately 150mm 2 The optimal size is approximately 20mm. 2 Approximately 100mm 2 .

[0020] The hydraulic bearing preferably includes a first sealing element arranged at a first axial end of the hydraulic bearing to at least partially define a bypass chamber in the axial direction.

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

[0022] The first sealing element may be at least partially made of plastic, particularly of an elastic plastic (such as an elastomer). The first sealing element may be substantially disc-shaped and, for example, connected radially inward to a first axial end of the inner core and radially outward to a first axial end of the outer sheath and / or outer cage by press fitting and / or bonding. For this purpose, the first sealing element may have an outer retaining ring at its radially outer end and / or an inner retaining ring at its radially inner end, wherein the outer and / or inner retaining rings may be molded from metal or plastic. The first sealing element may be at least partially designed as a diaphragm and / or bellows. This provides the advantage that the first sealing element can achieve low-resistance volumetric variations in the bypass chamber. In particular, the wall thickness of the first sealing element measured at its thinnest point may be much smaller than the wall thickness measured at the thinnest point of the elastomer body portion defining the first or second chamber, for example, by about 20%, about 10%, or about 5%.

[0023] In this regard, the hydraulic bearing preferably includes a second sealing element disposed at a second axial end of the hydraulic bearing to at least partially define a bypass chamber in the axial direction. Optionally, the elastomer body has at least one flow cavity extending in the axial direction and forming part of the bypass chamber.

[0024] Using this design, the hydraulic bearing can be provided with a very large bypass chamber, which extends particularly along the entire axial length between the axial ends of the hydraulic bearing. The second sealing element can be designed similarly to the first sealing element, wherein the above-described embodiments regarding the first sealing element can be correspondingly applied to the second sealing element, particularly regarding the second axial end. This allows for a very large, low-resistance volume variation of the bypass chamber.

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

[0026] The advantage provided by the above configuration is that the damping characteristics of the hydraulic bearing can be better adjusted by the excitation frequency. In particular, by adjusting the configuration of the first auxiliary bypass channel, such as the arrangement, cross-sectional dimensions, and / or length of the first auxiliary bypass channel, an additional (third) frequency range in which additional damping peaks occur can be provided. The first auxiliary bypass channel is particularly configured to be different from the first bypass channel.

[0027] More preferably, the bypass chamber is connected to the second working chamber via a second bypass passage.

[0028] This provides the advantage that the damping characteristics of the hydraulic bearing can be further adjusted by changing the excitation frequency. In particular, by adjusting the configuration of the second bypass channel, such as its arrangement, cross-sectional dimensions, and / or length, an additional (fourth) frequency range in which additional damping peaks can be provided.

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

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

[0031] The advantage provided by the above configuration is that the damping characteristics of the hydraulic bearing can be further adjusted by the excitation frequency. In particular, by adjusting the configuration of the second auxiliary bypass channel, such as the arrangement, cross-sectional dimensions, and / or length of the second auxiliary bypass channel, an additional (fifth) frequency range in which additional damping peaks occur can be provided. The second auxiliary bypass channel is particularly configured to be different from the second bypass channel.

[0032] The bypass channel and the auxiliary bypass channel can each be configured such that they extend at least partially substantially along the axial direction or x-direction of the bearing, or at least partially substantially along the circumferential direction of the bearing, or both partially substantially along the x-direction and partially substantially along the circumferential direction of the bearing. Both the bypass channel and the auxiliary bypass channel can be defined radially outward by the outer sheath. For example, a configuration in which the second bypass channel extends substantially along the x-direction, while the second auxiliary bypass channel extends substantially along the circumferential direction, i.e., in the yz plane, is conceivable. The same applies to the first bypass channel and the first auxiliary bypass channel. The opposite 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 a first bypass passage and / or a first auxiliary bypass passage (if any). The second sub-bypass chamber can be connected to the second working chamber via a second bypass passage and / or a second auxiliary bypass passage (if any).

[0034] The advantage of the above configuration is that it provides two separate bypass chambers, each connected to a first working chamber via a first bypass channel and / or a first auxiliary bypass channel (if any) and connected to a second working chamber via a second bypass channel and / or a second auxiliary bypass channel (if any), thus enabling more precise adjustment of the damping characteristics by the excitation frequency. The first and second sub-bypass chambers can be separated by a partition wall, which can be part of the elastomer body. The partition wall can be configured such that there is substantially no pressure exchange between the first and second sub-bypass chambers across the partition wall. For example, the partition wall can extend substantially in or parallel to the yz plane, and the first sub-bypass chamber can be defined at least partially axially outward by a first sealing element, and the second sub-bypass chamber can be defined at least partially axially outward by a second sealing element. Alternatively, the partition wall can also extend substantially in or parallel to the xy plane.

[0035] Preferably, decoupling elements are arranged in the first bypass channel and / or the first auxiliary bypass channel and / or the second bypass channel and / or the second auxiliary bypass channel. In other words, the aforementioned channels can be implemented with or without decoupling elements. For example, decoupling elements can be arranged only in the first bypass channel, while the second bypass channel and the auxiliary bypass channel (if any) may not have decoupling elements. However, for example, both the first and second bypass channels, as well as the first and second auxiliary bypass channels (if any), may have decoupling elements.

[0036] Incorporating one or more decoupling elements further improves the adjustability of the damping characteristics of hydraulic bearings. Decoupling elements are particularly useful for targeted reduction of the dynamic stiffness of hydraulic bearings at specific frequencies or within specific frequency ranges. Decoupling elements can be configured as freely vibrating decoupling plates that transmit both fluid and pressure, or as sealed decoupling membranes that transmit only pressure. The decoupling elements and corresponding channels can be configured such that the decoupling elements reciprocate within a specific frequency range of the excitation, thereby allowing fluid to flow back and forth within the channels to generate damping, while there is little or no significant fluid exchange between the corresponding chambers.

[0037] Preferably, the hydraulic bearing includes a first insert disposed between the elastomer body and the outer sheath and partially defining a first working chamber, wherein a first bypass channel is at least partially disposed within the first insert. Optionally, a first auxiliary bypass channel is at least partially disposed within the first insert.

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

[0039] In this regard, the hydraulic bearing preferably has a second insert disposed between the elastomer body and the outer sheath and partially defining a second working chamber, wherein a second bypass channel is at least partially disposed in the second insert. Optionally, a second auxiliary bypass channel is at least partially disposed in the first insert.

[0040] The above configuration allows for the simple provision of a second bypass channel and / or a second auxiliary bypass channel. The radially 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 arranged substantially at the diametrically opposed positions of the hydraulic bearing.

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

[0042] In this regard, the corresponding decoupling elements are preferably arranged in the first insert and / or the second insert.

[0043] The above configuration allows the corresponding decoupling elements to be easily arranged in the first and / or second inserts. The first and / or second inserts can in particular be constructed as multi-piece, such as two-piece, and enclose the corresponding decoupling elements within them. Attached Figure Description

[0044] The embodiments of the present invention will now be described in detail with reference to the accompanying drawings. It is self-evident that the present invention is not limited to these embodiments, but rather that the features disclosed within the scope of this specification can be combined to form more embodiments.

[0045] In the picture:

[0046] Figure 1 A schematic cross-sectional view of a hydraulic bearing according to a first embodiment is shown;

[0047] Figure 2 Another cross-sectional schematic diagram of the hydraulic bearing according to the first embodiment is shown;

[0048] Figure 3 A schematic cross-sectional view of a hydraulic bearing according to a second embodiment is shown;

[0049] Figure 4 Another cross-sectional schematic diagram of the hydraulic bearing according to the second embodiment is shown;

[0050] Figure 5A schematic cross-sectional view of a hydraulic bearing according to a third embodiment is shown;

[0051] Figure 6 A schematic cross-sectional view of a hydraulic bearing having an elastomeric body with two support arms is shown.

[0052] Figure 7 A schematic cross-sectional view of a hydraulic bearing having an elastomeric body with four support arms is shown.

[0053] Figure 8 A schematic cross-sectional view of a hydraulic bearing according to the first embodiment, marked with different channels and fluid flow directions, is shown.

[0054] Figure 9 A schematic cross-sectional view of a hydraulic bearing according to a second embodiment, marked with different channels and fluid flow directions, is shown.

[0055] Explanation of reference numerals in the attached figures

[0056] 1 Hydraulic bearing

[0057] 2 inner cores

[0058] 3 outer sheath

[0059] 4. Elastomer Body

[0060] Studio 5

[0061] Studio 6

[0062] 7 outer cages

[0063] 8 bypass rooms

[0064] 9. First Bypass

[0065] 10 First sealing element

[0066] 11. First axial end of hydraulic bearing

[0067] 12 Second sealing element

[0068] 13 Second axial end of hydraulic bearing

[0069] 14 Second Bypass Passage

[0070] 15 decoupling elements

[0071] 16 First Insert

[0072] 17 Second Insert Detailed Implementation

[0073] Figure 1The cross-section of the hydraulic bearing 1 in the yz plane of a Cartesian reference coordinate system attached to the outer sheath 3 of the hydraulic bearing 1 is shown. The zero point of the Cartesian reference coordinate system coincides with the center point of the outer sheath 3.

[0074] from Figure 1 As can be seen, the hydraulic bearing 1, in addition to the outer sheath 3, also includes an inner core 2, an outer cage 7, and an elastomer body 4 extending between the inner core 2 and the outer sheath 3. The outer sheath 3 is cylindrical and surrounds the inner core 2 in the radial direction. In the present case, the outer sheath 3 is made of metal, but it may also contain at least partially plastic, especially fiber-reinforced plastic.

[0075] The inner core 2 includes a tubular inner part with a circular cross-section extending along the x-direction in the yz-plane and a piston extending radially around the inner part. The piston is substantially wedge-shaped in the yz-plane and has a first blunt end and a second blunt end. The first blunt end in the negative z-axis direction has a wider width in the transverse direction than the second blunt end in the positive z-axis direction. The transverse sides of the piston are rounded. The piston can be molded from plastic and injection molded onto the inner part, which can be molded from metal.

[0076] The elastomer body 4 elastically connects the inner core 2 to the outer sheath 3 or outer cage 7, allowing the inner core 2 to move relative to the outer sheath 3 or relative to the outer cage 7. The elastomer body 4 is substantially X-shaped in the yz plane, having four support arms extending from the inner core 2 toward the outer sheath 3. The elastomer body 4 can be injection molded or vulcanized onto the outer cage 7 and the inner core 2. Figure 1 and Figure 2 As can be seen, the elastomer body 4 basically surrounds the inner core 2 in the radial direction.

[0077] The hydraulic bearing 1 also includes a first chamber 5 and a second chamber 6 that are fluidly connected to each other via a working channel (not shown). Figure 1 and Figure 2 As can be seen, the first working chamber 5 is located in the negative z-axis direction. Conversely, the second working chamber is located in the positive z-axis direction. The first insert 16 is arranged between the elastomer body 4 and the outer sheath 2 along the negative z-axis direction. Furthermore, a second insert 17 is arranged between the elastomer body 4 and the outer sheath 3 along the positive z-axis direction. Therefore, the first working chamber 5 is defined by the elastomer body 4 and the first insert 16, while the second working chamber 6 is defined by the elastomer body 4 and the second insert 17.

[0078] The outer cage 7 is substantially tubular in shape and has a substantially circular cross-section. The outer cage 7 has two recesses in two radially outward regions, wherein a first insert 15 can be precisely matched and inserted into one of the two recesses, and a second insert 17 can be precisely matched and inserted into the other of the two recesses, such that the inserts can be supported on the outer cage 7 at least indirectly by the elastomer body 4.

[0079] The elastomeric body 4 of the present invention is die-cast and surrounds the piston of the inner core 2. The elastomeric body 4 has a first piston surface in the first blunt end region of the piston of the inner core 2, and a second piston surface in the second blunt end region of the piston of the inner core 2. In other words, both the first and second piston surfaces of the elastomeric body 4 represent extensions of the piston of the inner core 2. When the inner core 2 moves relative to the outer sheath 3, particularly in the z-direction, the first and second piston surfaces change the volumes of the first and second working chambers 5 and 6 according to the direction of movement of the inner core 2 and / or the outer sheath 3. For example, when the inner core 2 displaces along the positive z-axis, the second piston surface of the elastomeric body 4 displaces together with the first piston surface of the elastomeric body 4 along the positive z-axis. As a result, the volume of the second working chamber 6 decreases, while the volume of the first working chamber 5 increases, wherein the corresponding volume change of the first working chamber 5 is greater than the corresponding volume change of the second working chamber 6. In other words, with the displacement of the inner core 2, the increase in volume of the first working chamber 5 is greater than the decrease in volume of the second working chamber. This also applies to the displacement of the inner core 2 along the negative z-axis.

[0080] The different volume changes in chamber 5 and chamber 6 result in different pressure changes in chamber 5 and chamber 6. Due to these pressure changes, fluid flows from one chamber of chamber 5 or 6 into the other chamber of chamber 6 or 6 via a working channel, depending on the different pressures in the two chambers. As fluid flows from one chamber to the other via the working channel, dissipation losses occur in the working channel, which suppress, for example, relative motion or vibration between a vehicle assembly (not shown) fastened to hydraulic bearing 1 and a vehicle body (not shown) also coupled to hydraulic bearing 1. The damping power may have a damping peak at a specific frequency or within a first frequency range.

[0081] from Figure 1 and Figure 2 As can be seen from the diagram, the hydraulic bearing 1 according to the first embodiment is designed with a first bypass channel 9 arranged between the inner circumferential surface of the outer sheath 3, the outer cage 7, and the first insert 16. In addition, a second bypass channel 14 is arranged between the inner circumferential surface of the outer sheath 3, the outer cage 7, and the second insert 17.

[0082] The first bypass passage 9 and the second bypass passage 14 extend substantially along the positive x-axis and lead into the bypass chamber 8 in the positive x-axis direction.

[0083] The bypass chamber 8 is defined in the positive x-axis direction by a first sealing element 10 disposed at the first axial end 11 of the hydraulic bearing 1. The first sealing element 10, comprising elastic plastic or elastomer, is designed in a bellows shape, thereby enabling low-resistance volume changes in the bypass chamber through deformation of the first sealing element 10. A second sealing element 12 is located at the second axial end 13 of the hydraulic bearing 1, opposite to the first axial end 10 of the hydraulic bearing 1. This second sealing element 12 is also designed in a bellows shape and also comprises elastic plastic or elastomer.

[0084] The first insert 16 has at least one recess or groove extending in the z-direction, which interconnects the first working chamber 5 with the first bypass channel 9. The first insert 16 may, in particular, have two, three, or, as in the present case, four recesses. According to the first embodiment, a decoupling element 15 is located within the four recesses, designed as a flexible decoupling membrane, and fluidly separates the first working chamber 5 from the bypass chamber 8. However, the first working chamber 5 and the bypass chamber 8 are pressure-connected to each other via the first bypass channel 9. The second insert 17 is similarly designed to the first insert 16 and also includes a decoupling element 15 that fluidly separates the second working chamber 6 from the bypass chamber 8. However, the second working chamber 6 and the bypass chamber 8 are pressure-connected to each other via the second bypass channel 14. The configuration of inserts 16, 17, bypass channels 9, 14, and decoupling elements 15, 16 can vary depending on requirements or available structural space. Figure 1 and Figure 2 As can be seen, in the current situation, both inserts 16 and 17 are designed as two-piece units, which allows for easy insertion or replacement of the corresponding decoupling element 15 inserted into inserts 16 and 17.

[0085] Figure 3 and Figure 4 A hydraulic bearing 1 according to the invention, based on a second embodiment, is shown. The design of the hydraulic bearing 1 according to the second embodiment is largely consistent with the design of the hydraulic bearing 1 according to the first embodiment. Therefore, only the differences between the two embodiments will be described in detail below.

[0086] Unlike the hydraulic bearing 1 according to the first embodiment, the hydraulic bearing 1 according to the second embodiment has only one insert 17. Furthermore, the bypass chamber 8 according to the second embodiment is connected to the first working chamber 5 only through a first bypass channel 9. Unlike the hydraulic bearing 1 according to the first embodiment, in the hydraulic bearing 1 according to the second embodiment, the second working chamber 6 and the bypass chamber 8 are not connected to each other. Therefore, the hydraulic bearing 1 according to the second embodiment does not have a second bypass channel 14.

[0087] According to the second embodiment, vibrations in the first frequency range are damped similarly to those in the first embodiment by means of fluid flowing through the working channel between the first working chamber 5 and the second working chamber 6, while vibrations in the second frequency range are damped only by fluid flowing in the first bypass channel 9. This design has advantages due to its simple structural form.

[0088] Figure 5 A hydraulic bearing 1 according to a third embodiment is shown, wherein the first chamber 5 and the second chamber 6 have a substantially symmetrical configuration in the yz plane (i.e., in the radial cross-section at the center point of the hydraulic bearing), differing only in their length or extension in the x-direction. According to this embodiment, the different volumes of the two chambers 5 and 6 are achieved by the different lengths or extensions in the x-direction. Figure 5 As can be seen, according to this embodiment, the outer cage 7 is at least segmentedly surrounded or wrapped by the elastomer body 4 on both the radially inner and radially outer sides. The substantially symmetrical design of the working chambers 5 and 6 in the radial cross-section provides the advantage that the support arms disposed within the elastomer body 4 can also be substantially symmetrically designed, particularly having substantially equal lengths and thicknesses, thereby making the elastomer body 4 easier to manufacture and improving its robustness. Furthermore, according to this design, it is possible to ensure that the elastomer body 4 remains in a "zero position" when it contracts along the z and y directions.

[0089] Figure 6 and Figure 7 The design of the elastomeric body 4 of the hydraulic bearing 1 relative to its support arm in the radial cross-section according to the third embodiment is shown in simplified form. In this regard, "in simplified form" means that specific sections of the outer cage 7 and the elastomeric body 4 are not shown in the figures.

[0090] from Figure 6 As can be seen, the elastomer body 4 can have only two opposing support arms with basically equal thickness and width, so that the first working chamber 5 and the second working chamber 6 are symmetrically designed in the yz plane.

[0091] from Figure 7 As can be seen, the elastomer body 4 can also have four X-shaped support arms in the yz plane. These four support arms are basically the same thickness and the same width, and are arranged so that the first working chamber 5 and the second working chamber 6 are symmetrically designed in the yz plane.

[0092] Figure 8 The hydraulic bearing 1 according to the first embodiment is shown marked with the fluid flow direction. From Figure 8As can be seen, the first working chamber 5 and the second working chamber 6 are fluidly connected, allowing fluid exchange between the two chambers 5 and 6 and damping the vibration of the hydraulic bearing 1 within a first frequency range during operation. In contrast, the first working chamber 5 and the second working chamber 6 are each pressure-transmitted to a bypass chamber 8 via bypass channels 9 and 14. Here, the bypass chamber 8 can be divided into a first sub-bypass chamber and a second sub-bypass chamber, such that the first sub-bypass chamber and the second sub-bypass chamber are separated from each other by walls extending substantially in the xy plane from the inner core 2 along the y-direction. Due to pressure changes in the first working chamber 5, deformation or vibration of the decoupling element 15 arranged in the first insert 16 causes the fluid in the first bypass channel 9 to reciprocate or flow within the first bypass channel 9, thereby damping the vibration of the hydraulic bearing 1 within a second frequency range. Due to pressure changes in the second working chamber 6, deformation or vibration of the decoupling element 15 arranged in the second insert 17 causes the fluid in the second bypass channel 14 to reciprocate or flow within the second bypass channel 14, thereby damping the vibration of the hydraulic bearing 1 within another frequency range. The first bypass channel 9 and the second bypass channel 14 and / or the decoupling element 15 of the first bypass channel 9 and the decoupling element 15 of the second bypass channel 14 can be configured in different ways to adjust the corresponding frequency range.

[0093] Figure 9 The hydraulic bearing 1 according to the second embodiment is shown marked with the fluid flow direction. From Figure 9 As can be seen, the first working chamber 5 and the second working chamber 6 are fluidly connected, allowing fluid exchange between the two chambers 5 and 6, and damping the vibration of the hydraulic bearing 1 within a first frequency range during operation. In contrast, the first working chamber 5 is pressure-transmittingly connected to the bypass chamber 8. Due to pressure changes in the first working chamber 5, deformation or vibration of the decoupling element 15 arranged in the first insert 16 causes the fluid in the first bypass channel 9 to reciprocate or flow within the first bypass channel 9, thereby damping the vibration of the hydraulic bearing 1 within a second frequency range.

Claims

1. A hydraulic bearing (1), comprising: Inner core (2); Outer sheath (3) radially surrounds the inner core (2); An elastomer body (4) that elastically connects the inner core (2) and the outer sheath (3) to allow relative displacement between the inner core (2) and the outer sheath (3); The first studio (5) and the second studio (6) are fluidly connected to each other through a working channel; Bypass chamber (8), which is connected to the first working chamber (5) via a first bypass passage (9); A first sealing element (10) is arranged at the first axial end (11) of the hydraulic bearing (1) to at least partially define the bypass chamber (8) in the axial direction; and A second sealing element (12) is arranged at the second axial end (13) of the hydraulic bearing to at least partially define the bypass chamber (8) in the axial direction. The first working chamber (5) and the second working chamber (6) are configured such that when the inner core (2) is displaced relative to the outer sheath (3) in a predetermined radial direction, the volume change of the first working chamber (5) is greater than the volume change of the second working chamber (6).

2. The hydraulic bearing (1) according to claim 1, wherein, The elastomer body (4) has at least one flow cavity that forms part of the bypass chamber (8).

3. The hydraulic bearing (1) according to claim 1 or 2, wherein, The bypass chamber (8) is additionally connected to the first working chamber via a first auxiliary bypass passage.

4. The hydraulic bearing (1) according to claim 3, wherein, The bypass chamber (8) is connected to the second working chamber (6) via a second bypass passage (14).

5. The hydraulic bearing (1) according to claim 4, wherein, The bypass chamber (8) is additionally connected to the second working chamber (6) via a second auxiliary bypass passage.

6. The hydraulic bearing (1) according to claim 5, wherein, The bypass chamber (8) is divided into a first sub-bypass chamber and a second sub-bypass chamber. The first sub-bypass chamber is connected to the first working chamber (5) through the first bypass channel (9) and / or the first auxiliary bypass channel, and the second sub-bypass chamber is connected to the second working chamber (6) through the second bypass channel (14) and / or the second auxiliary bypass channel.

7. The hydraulic bearing (1) according to claim 5, wherein, A decoupling element (15) is arranged in the first bypass channel (9) and / or the first auxiliary bypass channel and / or the second bypass channel (14) and / or the second auxiliary bypass channel.

8. The hydraulic bearing (1) according to claim 7, wherein, The hydraulic bearing (1) further includes a first insert (16) disposed between the elastomer body (4) and the outer sheath (3) and partially defining the first working chamber (5), wherein the first bypass channel (9) is at least partially disposed in the first insert (16).

9. The hydraulic bearing (1) according to claim 8, wherein, The first auxiliary bypass channel is at least partially disposed in the first insert (16).

10. The hydraulic bearing (1) according to claim 8, wherein, The hydraulic bearing (1) further includes a second insert (17) disposed between the elastomer body (4) and the outer sheath (3) and partially defining the second working chamber (6), wherein the second bypass channel (14) is at least partially disposed in the second insert (17).

11. The hydraulic bearing (1) according to claim 10, wherein, The second auxiliary bypass channel is at least partially arranged in the second insert (17).

12. The hydraulic bearing (1) according to claim 10, wherein, The corresponding decoupling element (15) is arranged in the first insert (16) and / or the second insert (17).

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