Hydraulic bearing and hydraulic bearing manufacturing method

Abstract

A hydraulic bearing (10) is provided with: an inner core (20); the cage frame (30) surrounds the inner core (20); an elastic body (40) extending between the inner core (20) and the cage (30) and elastically connecting the inner core (20) and the cage (30) to each other; and an outer sheath (50) surrounding the cage (30). Wherein the elastomer body (40) comprises a suspension spring (60); a first radial fluid chamber pocket (70) and a second radial fluid chamber pocket (72); and a first axial fluid chamber pocket (80) and a second axial fluid chamber pocket (82), a first radial fluid chamber pocket (70) and a second radial fluid chamber pocket (72), and a first axial fluid chamber pocket (80) and a second axial fluid chamber pocket (82), each filled with a working fluid (90) and delimited radially outward by an outer sheath (50), to form first and second radial fluid chambers (74, 76) and first and second axial fluid chambers (84, 86), respectively.

Description

Technical Field

[0001] The invention relates to a hydraulic bearing, in particular a subframe hydraulic bearing, and a method for producing a hydraulic bearing, in particular a subframe hydraulic bearing. Background Art

[0002] Hydraulic bearings are often used to connect a first component to a second component, allowing relative movements, especially vibrations, but damping them. Hydraulic bearings provide a spring force that is restored by the use of elastomeric materials and a damping force that is actively generated by means of dissipative losses in the bearing. The two hydraulic chambers of a hydraulic bearing are usually interconnected via a channel to enable fluid exchange between the two hydraulic chambers.

[0003] For example, in a vehicle structure, a subframe for supporting a vehicle body and / or a driving component is supported on a chassis component by a hydraulic bearing in order to suppress the transmission of road vibrations (especially radial vibrations) through the chassis to the subframe. The radial direction depends on the internal design and position of the vehicle, and usually corresponds to the horizontal direction of the vehicle movement when the hydraulic bearing is installed in the vehicle. In many vehicle structural applications, axial damping is not required. In this case, the axial direction also depends on the internal structure and position of the vehicle, and usually corresponds to the vertical direction of the vehicle movement when the hydraulic bearing is installed in the vehicle.

[0004] If the components to be supported are heavy, such as in combustion engines or electric drives, they can experience not only radial and / or horizontal movements, but also axial vibrations. For electric vehicles, the axial stiffness of the bearings is often increased. This often results in negative acoustic side effects. By using axial damping, the increased axial stiffness can be avoided and its side effects can be reduced. To damp such radial and axial movements, two radially damped hydraulic bearings and two axially damped hydraulic bearings are usually used.

[0005] The prior art has disclosed solutions for damping the support components in radial and axial directions, that is, integrating the damping modes in these two directions in a hydraulic bearing. However, such hydraulic bearings as described in European patent documents EP2906851B1 or EP2906852B1 have a large number of components, such as 4 vulcanization groups and 12 other components, and are very complicated to produce and assemble, resulting in high costs. In addition, in the above solutions, the hydraulic compensation chambers for radial and axial damping are separated by elastic diaphragms, and thus may affect each other. Summary of the invention

[0006] In view of this, an object of the present invention is to provide a hydraulic bearing that is easy to manufacture and low-cost, and can achieve independent damping in the radial direction and the axial direction.

[0007] In order to achieve the above object, the present invention proposes independent claims. The preferred embodiments of the present invention refer to the dependent claims.

[0008] In order to solve the above technical problems, the first aspect of the present invention relates to a hydraulic bearing, comprising: an inner core; a cage surrounding the inner core; an elastomeric body extending between the inner core and the cage and elastically connecting the inner core and the cage to each other; and an outer sheath surrounding the cage; wherein the elastomeric body comprises: a suspension spring; a first radial fluid chamber cavity and a second radial fluid chamber cavity; and a first axial fluid chamber cavity and a second axial fluid chamber cavity, wherein the first radial fluid chamber cavity and the second radial fluid chamber cavity and the first axial fluid chamber cavity and the second axial fluid chamber cavity are each filled with a working fluid and are radially outwardly bounded by the outer sheath to form a first radial fluid chamber cavity and a second axial fluid chamber cavity, respectively. The inner core and the cage frame are provided with a body chamber and a second radial fluid chamber and a first axial fluid chamber and a second axial fluid chamber; wherein the first radial fluid chamber and the second radial fluid chamber are fluidly connected to each other via a radial fluid channel, and are designed so that during the radial relative movement between the inner core and the cage frame, fluid exchange occurs between the first radial fluid chamber and the second radial fluid chamber via the radial fluid channel along a predetermined radial direction; wherein the first axial fluid chamber and the second axial fluid chamber are fluidly connected to each other via the axial fluid channel, and are designed so that during the axial relative movement between the inner core and the cage frame, fluid exchange occurs between the first axial fluid chamber and the second axial fluid chamber via the axial fluid channel.

[0009] The invention is advantageous in that, compared to such conventional bearings, particularly for use as subframe bearings, the bearings of the invention are simpler, more compact and less expensive, while still providing good damping and isolation of vibrations in both vertical and horizontal directions. The structural complexity is reduced by reducing the number of parts in the hydraulic bearing, while also achieving damping in two independent damping directions, rather than just damping in one of the two directions.

[0010] In the context of this application, all spatial direction terms "up", "down", and "vertical" refer to the z-axis of the three-dimensional coordinate system, whose origin is approximately located at the center of mass of the bearing of the present invention, and the z-axis direction represents the principal axis of inertia of the bearing. Therefore, the term "axial" refers to the z-axis, and the term "radial" refers to the xy plane formed by the x-axis and y-axis of the coordinate system, and the xy plane is orthogonal to the z-axis. That is, "radial" refers to the direction perpendicular to the z-axis. The term "horizontal" also refers to the xy plane. In view of the bearing of the present invention, the term "lateral" refers to the direction along the xy plane or parallel to the xy plane, and the term "longitudinal" refers to the direction along the z-axis or parallel to the z-axis.

[0011] In the context of the present application, the term "surrounding" may mean that the cage of the bearing of the present invention frames, fences or encircles the inner core and partially delimits the inner core in the radial direction and in the circumferential direction around the z-axis. That is, in the state of the bearing without the elastomeric body, the cage may represent the radial limit of the inner core. On the other hand, in the context of the present application, the term "enclosing" may mean that the outer sheath completely delimits the height of the cage in the vertical direction in the radial direction and in the circumferential direction, thereby enveloping the cage.

[0012] The hydraulic bearing has an outer sheath and a vulcanized component, wherein the outer sheath at least partially surrounds the vulcanized component. The hydraulic bearing or the outer sheath may be cylindrical or substantially cylindrical. However, the hydraulic bearing may also be designed to be conical or approximately conical, or the axial end face of the hydraulic bearing may also be designed to be elliptical, rectangular or a shape suitable for the hydraulic bearing, rather than circular. The hydraulic bearing may also be called a hydraulic suspension.

[0013] The vulcanized component of the hydraulic bearing can have at least an inner core, a cage and an elastomer body. The profile of the vulcanized component is designed so that the vulcanized component can be pressed into the outer sheath during the manufacturing process of the hydraulic bearing, and the inner side of the outer sheath surrounds and / or is defined outside the vulcanized component. The cage surrounds the inner core of the vulcanized component at least in the radial direction, and the elastomer body elastically connects the inner core to the cage. In particular, the inner core and the cage are partially or completely embedded in the elastomer body. The axial elastomer stop and the radial sealing element can protrude outside the inner core and / or the cage in the axial and / or radial direction. In order to manufacture the vulcanized component, the inner core and the cage can be inserted into a common mold, in particular, inserted concentrically, and then overmolded with an elastomer material by an injection molding process. In other words, the elastomer body can be vulcanized to the cage and / or the inner core. The elastomer material can form the elastomer body, and the vulcanized component can be taken out of the mold as a component. As a supplement or alternative to the injection molding process, other manufacturing processes can also be used. For example, a low pressure casting process or similar process may also be applied to manufacture vulcanized parts from non-rubber based elastomeric materials.

[0014] The inner core may be formed of a shape-stable material, such as metal or plastic, in particular aluminum. The inner core may be substantially cylindrical and extend in the axial direction of the bearing. An axial through hole may be formed in the inner core as an assembly groove. The cross-sectional shape of the inner core is not limited to a circular shape and may have a cross-sectional shape that varies in the axial direction. In particular, the inner core may include a pair of radially protruding thickenings, which are offset in the axial direction and opposite in the radial direction. The pair of thickenings may be configured to enhance the axial stiffness of the bearing and / or support the deformation or volume change of the axial fluid chamber during the relative axial movement of the inner core and the cage. The inner core may include a pair of radial stop protrusions, which both extend in the radial direction to the corresponding radial fluid chamber and define the relative displacement of the inner core and the cage in the radial direction. The radial stop protrusions may also be referred to as radial stops, in particular, they are opposite to each other in the radial direction, in particular they are opposite to each other in the diameter direction, and extend in opposite radial directions. The radial extension direction of the radial stop protrusions is in particular offset by about 90° relative to the radial extension direction of the thickening.

[0015] The elastomeric body is formed, for example, by an elastically deformable plastic (such as an elastomer) that can be elastically deformed under load. The elastomeric body includes a suspension spring or forms a suspension spring. The suspension spring of the elastomeric body can be substantially axially aligned and can generate a spring force that offsets the load when subjected to tensile and compressive loads in the axial and radial directions. The elastomeric body can completely or at least partially surround and / or embed an inner core and / or a cage. The elastomeric body includes two radial fluid chamber cavities and two axial fluid chamber cavities. The elastomeric body can form at least a portion of a radial fluid channel to connect the radial fluid chamber cavities, and / or can form at least a portion of an axial fluid channel to connect the axial fluid chamber cavities. In the elastomeric body, the two radial fluid chamber cavities are not connected to one or two axial fluid chamber cavities.

[0016] The basic shape of the cage can be designed as a hollow cylinder or an approximate hollow cylinder. The cage can be at least partially formed by a shape-stable material, such as plastic and / or metal, such as aluminum. In particular, the cage can be made by injection molding or casting (die casting) technology. The axial end face of the cage (i.e., the surface extending to the outside of the cage perpendicular to the longitudinal axis at both ends of the longitudinal axis) can be open or at least partially define the cage in the longitudinal direction. The axial end face of the cage can be basically completely covered by the material of the elastomer body. In particular, the cage can be basically completely embedded in the elastomer body. However, the cage can also be at least partially exposed radially to better connect to the outer sheath. The cage includes, for example, two or four windows or through-holes in the radial direction (i.e., from the inside of the cage to the outside of the cage), and these windows or through-holes are arranged to form at least two radial fluid chambers and two axial fluid chambers, each for receiving a working fluid. In addition, the cage can at least partially form a radial fluid channel and / or an axial fluid channel extending between the corresponding fluid chambers.

[0017] The outer sheath can be formed at least in part by a shape-stable material, such as metal or plastic, which is suitable for being attached to an external component, such as a vehicle body part exposed to vibration loads. The outer sheath can be designed as a hollow cylinder or is basically designed as a hollow cylinder. The axial extension of the outer sheath can correspond substantially to the axial extension of the cage and / or the elastomeric body. The fixed structure of the outer sheath can also be suitable for fixing the outer sheath to the external component. For example, the outer sheath can be connected to a flange to connect a hydraulic bearing to a vehicle frame. For example, the outer sheath can also have a sealing lip extending in a circumferential direction at its axial end. The vulcanized component can be pressed into the outer sheath and fixed in the outer sheath in a force-fitting manner. However, the axial end of the outer sheath can also form a flange after the vulcanized body has been pressed into, so that the vulcanized component is fixed in the outer sheath in a form-fitting manner.

[0018] In the assembled state of the hydraulic bearing, the vulcanized component has been pressed into the outer sheath, and the two radial fluid chamber cavities and the inner side of a part of the outer sheath together form a radial fluid chamber, which is elastic in the region of the elastomer body and is connected by a radial fluid channel, and the radial fluid system formed thereby is liquid-tight and filled with a working fluid. The first radial fluid chamber and the second radial fluid chamber can both be at least partially defined by the outer sheath in the radial outward direction, while the first radial fluid chamber and the second radial fluid chamber can be at least partially defined by the elastomer body in the radial inward direction, in two axial directions and in two circumferential directions. In particular, the radial fluid chamber can be separated from the environment by a diaphragm in both axial directions, whereby the diaphragm can be part of the elastomer body. In this case, the radial fluid chamber cavities and windows in the cage can at least partially overlap each other in the radial direction, and the radial fluid channel can be formed between the cage and the outer sheath outside the cage. Thus, the two radial fluid chambers can be fluidly connected to each other through the radial fluid channel, so that during the radial relative movement between the inner core and the cage, the volume of one radial fluid chamber in the elastic radial fluid chamber concave region decreases, while the volume of the other radial fluid chamber in the elastic radial fluid chamber concave region increases, so that the working fluid flows into the other radial fluid chamber through the radial fluid channel. The radial relative movement between the inner core and the cage can be damped by the fluid communication between the two radial fluid chambers.

[0019] The two axial fluid chamber cavities and the inner side of a part of the outer sheath together form an axial fluid chamber, which is elastic in the region of the elastomer body and is connected by an axial fluid channel, and the axial fluid system formed thereby is liquid-tight and filled with a working fluid. The first axial fluid chamber and the second axial fluid chamber can both be at least partially defined by the outer sheath in the radially outward direction, while the first axial fluid chamber and the second axial fluid chamber can be at least partially defined by the elastomer body in the radially inward direction, in two axial directions, and in two circumferential directions. In particular, the first axial fluid chamber can be defined by a diaphragm in one axial direction and by a suspension spring in another axial direction, while the second axial fluid chamber can be defined by a diaphragm in another axial direction and by a suspension spring in one axial direction, wherein the diaphragm can be a part of the elastomer body. In this case, the axial fluid chamber cavities and windows in the cage can be at least partially overlapped with each other in the radial direction, and the axial fluid channel can be formed between the cage and the outer sheath on the outside of the cage. Thus, the two axial fluid chambers can be fluidly connected to each other through the axial fluid channel, so that during the axial relative movement between the inner core and the cage, the volume of one axial fluid chamber in the region of its elastic axial fluid chamber concave cavity decreases, while the volume of the other axial fluid chamber in the region of its elastic axial fluid chamber concave cavity increases, so that the working fluid flows into the other axial fluid chamber through the axial fluid channel. The axial relative movement between the inner core and the cage can be damped by the fluid communication between the two axial fluid chambers.

[0020] Advantageously, the damping of the bearing in the radial direction can be influenced by the geometry of the radial fluid channels, in particular by the length and / or cross section of the radial fluid channels. Similarly, the damping of the bearing in the axial direction can be influenced by the geometry of the axial fluid channels, in particular by the length and / or cross section of the axial fluid channels. For example, the damping of the bearing can be increased by increasing the length of the corresponding fluid channels and / or increasing the cross section of the bearing. The number of fluid channels can also be changed.

[0021] In a preferred embodiment of the hydraulic bearing, the axial end surface of the elastomeric body is designed to have essentially no undercuts along the axial direction, and / or the elastomeric body and the cage have essentially no undercuts in at least two predetermined opposite radial directions in the area of ​​the radial fluid chamber cavity and the axial fluid chamber cavity.

[0022] Advantageously, the vulcanized parts of the hydraulic bearing can be manufactured in one manufacturing step in an injection mold or a casting mold, so that the manufacture of the hydraulic bearing is simpler and more compact. The axial end faces of the elastomer body, its radial fluid chamber recesses and axial fluid chamber recesses and possible radial fluid channels and / or axial fluid channels can be formed without additional training steps. Specifically, the axial end faces of the elastomer body in the axial direction and the fluid chamber recesses and possible fluid channels in the radial direction are substantially free of undercuts.

[0023] "Essentially no undercut" means, in particular, that there is no undercut in the corresponding direction during the manufacture of the elastomer body or in the unloaded state of the elastomer body, or there is only a small amount of undercut, especially there is only a small amount of undercut in the micro-deformation area of ​​the elastomer body. In addition, "essentially no undercut" may mean that there is no undercut on the elastomer body in the assembled state of the bearing, or there is only a small amount of undercut on the elastomer body, especially there is only a small amount of undercut in the micro-deformation area of ​​the elastomer body. "Essentially no undercut" may especially mean that during the manufacture of the elastomer body, the slider can be pulled out along the corresponding direction without damaging or destroying the elastomer body.

[0024] In order to manufacture the elastomer body of the vulcanized component of the bearing, an injection mold can be used, which at least partially surrounds the vulcanized component during injection molding and is opened after the process is completed to remove the vulcanized component. Before the vulcanized component is pressed into the outer sheath, the inner side of the mold corresponds to a part of the required outer contour of the vulcanized component, in particular the axial end face and a part of the side surface of the vulcanized component, which are close to the inner side of the outer sheath under pressure. In the side surface area, the mold includes an opening or channel, and sliders of corresponding shapes can be introduced or passed through the opening or channel into the mold interior along two predetermined opposite radial directions. The shape of these sliders forms the shape of two radial fluid chamber cavities and the shape of two axial fluid chamber cavities when introduced into the mold interior. Some sections of the sliders also surround the cage and form the radial outer surface of the elastomer body or the vulcanized component, in particular also form radial fluid channels and / or axial fluid channels.

[0025] When manufacturing a vulcanized component with the aid of an injection mold, the core and the cage of the hydraulic bearing can first be introduced into the interior of the mold. Before injection molding, the core and the cage are placed in a predetermined position relative to each other in the mold. The predetermined position corresponds to the position of the core and the cage in the unloaded state of the hydraulic bearing. In particular, in this predetermined position, the axial direction of the core or the cage corresponds approximately to the opening or closing direction of the mold, and a radial direction of the core or the cage corresponds approximately to the push-in or push-out direction of one of the slides. In addition, the windows of the cage are arranged in the interior of the mold so that the slide can be introduced into the final position through the corresponding windows, wherein the slide corresponds to the required radial fluid chamber cavity and axial fluid chamber cavity respectively. After the slide is introduced, the elastomer material can be injected into the remaining cavity between the inner contour of the mold, the core, the cage and the slide by injection molding and vulcanized. The slide can then be removed from the interior of the mold in the opposite direction, and the vulcanized component produced can be removed from the interior of the mold and pressed into the outer sheath in the next step.

[0026] In another preferred embodiment of the hydraulic bearing, the suspension spring has a first suspension spring arm and a second suspension spring arm, and the two suspension spring arms extend from the inner core to the cage frame basically in a diametrically opposite manner, wherein the first radial fluid chamber and the second radial fluid chamber are defined in the circumferential direction by the first suspension spring arm and the second suspension spring arm, the first axial fluid chamber is defined in the axial direction by the first suspension spring arm, and the second axial fluid chamber is defined in the axial direction by the second suspension spring arm.

[0027] The advantage of two suspension spring arms being diametrically opposed is that the stability and damping degree of the hydraulic bearing in the axial direction are more uniform, and the manufacturing is simple.

[0028] The first suspension spring arm and the second suspension spring arm being substantially diametrically opposed means that the suspension spring arms are substantially symmetrically arranged about the center of the hydraulic bearing within the axial length of the hydraulic bearing on the z-axis. The center of the hydraulic bearing may also be located at its volumetric center of gravity and / or its xy plane center of gravity.

[0029] The first suspension spring arm and the second suspension spring arm are radially parted by the inner core. Preferably, the hydraulic bearing damps the radial relative movement between the inner core and the cage perpendicular to the parting surface formed by the suspension spring arm. When using the hydraulic bearing, preferably if damping is to be performed in a certain radial direction, the hydraulic bearing of the present invention can be installed in a corresponding arrangement. Conversely, in two opposite axial directions, the first radial fluid chamber and the second radial fluid chamber are only defined by the diaphragm formed by the elastomer body, rather than by the relevant first suspension spring arm or second suspension spring arm. In the circumferential direction, the first axial fluid chamber and the second axial fluid chamber and the first radial fluid chamber and the second radial fluid chamber can be respectively defined by a partition wall formed by the elastomer body, and the material thickness of the partition wall is much smaller than the material thickness of the suspension spring arm. However, the partition wall can be designed to be very stable, so that the radial fluid chamber and the axial fluid chamber do not significantly affect each other during operation. However, it is also conceivable to provide a diaphragm instead of the partition wall. In the axial direction, the radial fluid chamber and the axial fluid chamber can be designed to be basically non-overlapping, so that they do not significantly affect each other at all during the operation of the hydraulic bearing.

[0030] In another preferred embodiment of the hydraulic bearing, the first axial fluid chamber is arranged on one side of the first axial bearing end of the first suspension spring arm, and the second axial fluid chamber is arranged on one side of the second axial bearing end of the second suspension spring arm.

[0031] In other words, the first axial fluid chamber and the second axial fluid chamber are offset toward different axial ends of the bearing, respectively. The axial offset of the first axial fluid chamber and the second axial fluid chamber is substantially below one end of the corresponding first suspension spring arm and the second suspension spring arm, thereby ensuring a high level of fluid exchange between the axial fluid chambers during axial displacement, so that the axial fluid system achieves good damping characteristics.

[0032] The first axial fluid chamber and the second axial fluid chamber can again be arranged substantially diametrically opposite to each other with respect to the center of the hydraulic bearing (e.g., its volumetric center of gravity and / or its xy plane center of gravity). The respective axial fluid chamber can be arranged completely below the first suspension spring arm end of the associated suspension spring arm and / or between the first axial bearing end and the first suspension spring arm end, wherein the second suspension spring arm end of the suspension spring can be arranged at the second axial bearing end.

[0033] In another preferred embodiment of the hydraulic bearing, the inner core includes a first radially protruding thickened area and a second radially protruding thickened area, wherein the first thickened area is formed at a position corresponding to the first suspension spring arm along the circumferential direction, and the second thickened area is formed at a position corresponding to the second suspension spring arm along the circumferential direction, and the first thickened area is axially offset relative to the second thickened area in the direction of the first axial bearing end.

[0034] Due to the diametrically opposed arrangement, the second thickened region is likewise axially offset relative to the first thickened region in the direction of the second axial bearing end.

[0035] The first radially protruding thickened area and the second radially protruding thickened area of ​​the inner core can easily enhance or adjust the axial stiffness of the bearing. In particular, the thickened area is also configured to support or enhance the deformation of the axial fluid chamber when the inner core is axially displaced relative to the cage.

[0036] In another preferred embodiment of the hydraulic bearing, the first thickened area has a first pressure surface at least partially adjacent to the first axial fluid chamber in the axial direction, and the second thickened area has a second pressure surface at least partially adjacent to the second axial fluid chamber in the axial direction.

[0037] In this case, the first pressing surface of the first thickened region may substantially face the first bearing end in the axial direction, and the second pressing surface of the second thickened region may substantially face the second bearing end in the axial direction.

[0038] The advantage of the thickened area having a pressure surface is that, in particular when the inner core performs an axial relative movement with respect to the cage, one of the two pressure surfaces improves the discharge of the working fluid from one axial fluid chamber to the other axial fluid chamber via the axial fluid channel, depending on the axial direction of the relative movement. It is also advantageous that the pressure surface of the thickened area is made of a non-elastic material and does not deform during the discharge of the working fluid.

[0039] In another preferred embodiment of the hydraulic bearing, the cage has a first support protrusion at the second axial bearing end and a second support protrusion at the first axial bearing end, wherein the position of the first support protrusion in the circumferential direction corresponds to the first suspension spring arm, and the position of the second support protrusion in the circumferential direction corresponds to the second suspension spring arm.

[0040] The first support protrusion and the second support protrusion of the cage can both extend radially inward from the radial inner side of the cage. The first support protrusion and the second support protrusion have a substantially wedge-shaped cross section along the z-axis and protrude radially inward toward the axial end of the cage. In addition, the first thickened area or the second thickened area of ​​the inner core and the first support protrusion or the second support protrusion of the cage can at least sectionally clamp or squeeze the first suspension spring arm or the second suspension spring arm therebetween, thereby enhancing the axial stiffness of the bearing.

[0041] In order to solve the above technical problems, the second aspect of the present invention relates to a method for manufacturing a hydraulic bearing, which comprises the following steps: embedding an inner core into a mold; embedding a cage into the mold so that the cage surrounds the inner core; closing the mold; introducing a radial slider into the mold; injecting an elastomeric material into the mold; vulcanizing the elastomeric material to form an elastomeric body and molding a vulcanized component, wherein the elastomeric body elastically connects the inner core to the cage and comprises a suspension spring, a first radial fluid chamber cavity and a second radial fluid chamber cavity, and a first axial fluid chamber cavity and a second axial fluid chamber cavity, the vulcanized component comprising an inner core, an elastomeric body and a cage; pulling out the radial slider; opening the mold; removing the vulcanized component from the mold; and connecting the vulcanized component to the outer sheath, wherein the first radial fluid chamber cavity and the second radial fluid chamber cavity are The first axial fluid chamber cavity and the second axial fluid chamber cavity are each filled with a working fluid and are radially outwardly bounded by the outer sheath to form a first radial fluid chamber and a second radial fluid chamber and a first axial fluid chamber and a second axial fluid chamber, respectively; wherein the first radial fluid chamber and the second radial fluid chamber are fluidically connected to each other via a radial fluid channel, and are designed so that during the radial relative movement between the inner core and the cage, fluid exchange occurs between the first radial fluid chamber and the second radial fluid chamber via the radial fluid channel along a predetermined radial direction; wherein the first axial fluid chamber and the second axial fluid chamber are fluidically connected to each other via an axial fluid channel, and are designed so that during the axial relative movement between the inner core and the cage, fluid exchange occurs between the first axial fluid chamber and the second axial fluid chamber via the axial fluid channel.

[0042] For the above aspects, especially the preferred embodiments related to each aspect, the contextual content is also applicable to the embodiments of other aspects.

[0043] Various embodiments for solving the above-mentioned technical problems are described below in conjunction with the accompanying drawings. In some cases, the features of the embodiments are not absolutely necessary for realizing the subject matter claimed in this application, but provide advantageous properties in certain applications. Therefore, embodiments that do not have all the features of the following embodiments should also be deemed to belong to the scope of protection of the technical solution described herein. In addition, to avoid redundancy, only certain features are mentioned in the following individual embodiments. It should be noted that each embodiment should not only be considered individually, but also in combination. Based on the combined considerations, those skilled in the art will recognize that each embodiment can also be modified by combining single or multiple features of other embodiments. It should be noted that it may be reasonable to systematically combine each embodiment with one or more features described in relation to other embodiments, so it should be considered and included in the specification. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] Figure 1A A perspective view showing an inner core of a hydraulic bearing according to the present invention is shown.

[0045] Figure 1B A perspective view of a cage of a hydrostatic bearing according to the present invention is shown.

[0046] Figure 1C A perspective view is shown of the elastomeric body of the hydraulic bearing of the present invention.

[0047] Figure 2A A perspective view showing a vulcanized component of a hydraulic bearing according to the present invention with the inner core, the cage and the elastomer body connected.

[0048] Figure 2B A perspective view of the outer sheath of a fluid bearing according to the present invention is shown.

[0049] Figure 2C A perspective view of the hydraulic bearing of the present invention is shown in a state where the vulcanized component is connected to the outer sheath.

[0050] Figure 3 It is a front view of the axial end surface of the vulcanized component of the hydraulic bearing of the present invention.

[0051] Figure 4 A first side view of a vulcanized component of a fluid bearing according to the present invention is shown.

[0052] Figure 5 Shows Figure 4 A cross-sectional view of a vulcanized component of a hydraulic bearing according to the present invention is shown.

[0053] Figure 6 A second side view of the vulcanized component of the hydraulic bearing of the present invention is shown.

[0054] Figure 7 Shows Figure 6 A cross-sectional view of a vulcanized component of a hydraulic bearing according to the present invention is shown.

[0055] Figure 8 A schematic cross-sectional view of a vulcanized component of a hydraulic bearing according to the present invention under an axial load is shown.

[0056] Reference numerals

[0057] 10: hydraulic bearing; 12: first axial bearing end; 14: second axial bearing end; 20: inner core; 21: axial through hole; 22: radial stopper; 24: first radial protruding thickened area; 25: second radial protruding thickened area; 26: first pressing surface; 27: second pressing surface; 30: cage; 32: first supporting protrusion; 34: second supporting protrusion; 36: through opening; 40: elastic body; 50: outer sheath; 60: suspension spring; 62: first suspension spring arm; 64: second suspension spring arm; 70: first radial fluid chamber concave cavity; 72: second radial fluid chamber concave cavity; 74: first radial fluid chamber; 76: second radial fluid chamber; 78: radial fluid channel; 80: first axial fluid chamber concave cavity; 82: second axial fluid chamber concave cavity; 84: first axial fluid chamber; 86: second axial fluid chamber; 88: axial fluid channel; 90: working fluid; 100: vulcanization component; VR: predetermined radial direction; A: axial direction. DETAILED DESCRIPTION

[0058] Figures 1A to 1C The individual components of a vulcanized component 100 of a generally cylindrical fluid bearing 10 of the present invention are shown in an unassembled state.

[0059] Figure 1A A perspective view of the inner core 20 of the hydraulic bearing 10 of the present invention is shown. The inner core is made of a shape-stable material such as metal or plastic, the basic shape of the inner core is cylindrical in the axial direction AR, and the inner core has an axial through hole 21 used as an assembly groove. The hydraulic bearing can be fixed to the component by inserting a part such as a screw into the assembly groove. The inner core 20 has a first radially protruding thickened area 24 and a second radially protruding thickened area 25 diametrically opposite to the center of the hydraulic bearing 10 in the axial direction AR. Here, the center of the hydraulic bearing can be regarded as the volume centroid and / or the xy plane centroid. In addition, as in the present embodiment, the inner core 20 can have two radial stops 22, which protrude into the first radial fluid chamber 74 and the second radial fluid chamber 76 in the assembled state of the hydraulic bearing 10, and when the inner core 20 of the hydraulic bearing 10 moves relative to the cage 30, the radial stops 22 limit the movement to the maximum possible radial movement path.

[0060] Figure 1BThe perspective view of the cage 30 of the hydraulic bearing 10 of the present invention is shown. The cage 30 is made of a shape-stable material such as plastic, and its basic shape is approximately a hollow cylinder. The axial end face of the cage 30 is open, and the cage 30 has six through-holes 36 in the radial direction, which cooperate with the elastomer body 40 and the outer sheath 50 to form two radial fluid chambers 74, 76 and two axial fluid chambers 84, 86, each for receiving a working fluid 90.

[0061] In this case, the through-opening 36 is arranged such that in the injection molding process for manufacturing the vulcanized component 100, the through-opening 36 allows the slider to be introduced or passed through in a predetermined radial direction to form the first radial fluid chamber cavity 70 and the second radial fluid chamber cavity 72 in the elastomer body 40. Preferably, the two sliders are used to form the radial fluid chamber cavities 70 and 72, wherein the two sliders can be introduced into the through-opening 36 in opposite radial directions. The through-opening 36 is also arranged such that in the elastomer body 40, a first axial fluid chamber cavity 80 is formed in the radial direction by introducing or passing through one of the sliders, and a second axial fluid chamber cavity 82 is formed in the radial direction by introducing or passing through the other slider in the opposite direction.

[0062] The cage has grooves or recesses on its outer side to form radial fluid passages 78 between radial fluid chambers 74 and 76, through which radial fluid chambers 74 and 76 can be in fluid communication. Similarly, the cage has grooves or recesses on its outer side to form axial fluid passages 88 between axial fluid chambers 84 and 86, through which axial fluid chambers 84 and 86 can be in fluid communication. In contrast, radial fluid chambers 74, 76 are not in fluid communication with axial fluid chambers 84, 86.

[0063] The cage 30 also has a first support protrusion 32 at the second axial bearing end 14 and a second support protrusion 34 at the first axial bearing end 12 ( Figure 1B The first support protrusion 32 and the second support protrusion 34 both extend in the radial direction toward the z-axis. The support protrusions 32, 34, the thickened areas 24, 25 of the inner core 20, and the suspension spring arms 62, 64 of the suspension spring 60 of the elastomeric body 40 together enhance the axial rigidity of the hydraulic bearing 10.

[0064] Figure 1C FIG. 4 is a perspective view of the elastomeric body 40 of the hydraulic bearing 10 of the present invention. The elastomeric body 40 is shown separated from the inner core 20 and the cage 30 for reference only. Specifically, Figure 1CThe first radial fluid chamber cavity 70 and the first axial fluid chamber cavity 80 in the injection-molded elastomer body 40 can be seen in the perspective view, while the second radial fluid chamber cavity 72 and the second axial fluid chamber cavity 82 cannot be seen in the perspective view.

[0065] Figure 2A The perspective view of the vulcanized component 100 of the hydraulic bearing 10 of the present invention is shown in the state where the inner core 20, the cage 30 and the elastomeric body 40 are connected. In this figure, the first radial fluid chamber cavity 70, the first axial fluid chamber cavity 80, the radial fluid channel 78 and the axial fluid channel 88 can be seen.

[0066] Figure 2B A perspective view of the outer sheath 50 of the hydraulic bearing 10 according to the invention is shown. The outer sheath 50 is designed as a hollow cylinder made of a dimensionally stable material, wherein the outer contour of the outer sheath 50 can be connected to other components. The axial extension of the inner core can be substantially equal to the axial extension of the vulcanized component 100. The inner diameter of the outer sheath 50 is selected such that the vulcanized component 100 can be pressed into it up to the axial stop flange at the second axial bearing end 14.

[0067] Figure 2C The perspective view of the hydraulic bearing 10 of the present invention is shown in a state where the vulcanized component 100 is connected to the outer sheath 50. After the vulcanized component 100 is pressed into the outer sheath 50, a portion of the inner side of the outer sheath 50 is positioned toward the outside in the radial direction and liquid-tightly closes the first radial fluid chamber cavity 70 and the second radial fluid chamber cavity 72, the first axial fluid chamber cavity 80 and the second axial fluid chamber cavity 82, the radial fluid channel 78, and the axial fluid channel 88. Before and / or during the pressing of the vulcanized component 100 into the outer sheath 50, the radial fluid chamber cavities 70 and 72, the axial fluid chamber cavities 80 and 82, the radial fluid channel 78, and the axial fluid channel 88 are filled with working fluid 90. By connecting the vulcanized component 100 to the outer sheath 50, an independent radial fluid system having the first radial fluid chamber 74, the second radial fluid chamber 76, and the radial fluid channel 78 and an independent axial fluid system having the first axial fluid chamber 84, the second axial fluid chamber 86, and the axial fluid channel 88 are formed in the hydraulic bearing 10, and the two fluid systems are not connected to each other.

[0068] Figure 3 The axial end face of the vulcanized component 100 of the hydraulic bearing 10 according to the invention is shown. In the figure, the second axial bearing end 14 can be seen, which is closed liquid-tightly by the elastomer body in the axial direction. The first support projection 32 is covered by the elastomer material of the elastomer body 40. The axial through hole 21 and the second radially protruding thickened area 24 can be seen from the inner core 20.

[0069] Figure 4A first side view of a vulcanized component 100 of a hydrostatic bearing 10 according to the invention is shown. In particular, the figure provides a view of the first radial fluid chamber cavity 70 and the second radial fluid chamber cavity 72 through two through-openings 36, wherein the radial stop 22 protrudes into the cavity, and through the other through-opening 36, the first axial fluid chamber cavity 80 can be seen. Furthermore, as shown in the figure, the axial fluid channel 88 leads to the first axial fluid chamber cavity 80 and connects the first axial fluid chamber cavity 80 with the second axial fluid chamber cavity 82 (not visible in the figure) in the circumferential direction at the outer edge of the cage 30. As shown in the figure, the radial fluid channel 78 leads to the first radial fluid chamber cavity 70 and connects the first radial fluid chamber cavity 70 with the second radial fluid chamber cavity 72 in the circumferential direction at the outer edge of the cage 30. The inlet to the second radial fluid chamber cavity 72 cannot be seen in the figure. As the inner core 20 moves radially relative to the cage 30 in a direction corresponding to the predetermined radial direction VR under the load on the hydraulic bearing, the elastic first radial fluid chamber cavity 70 is compressed and the working fluid 90 is pressed into the elastic second radial fluid cavity 72 via the radial fluid passage 78. This dampens the radial relative motion.

[0070] Figure 5 Shows Figure 4 The vulcanized component 100 of the hydraulic bearing 10 of the present invention is shown along its longitudinal axis ( Figure 3 In this sectional view, the arrangement of the inner core 20 with the axial through hole 21 and its radial stop 22 in the two radial fluid chamber cavities 70, 72 can be seen in particular.

[0071] Figure 6 FIG. 1 shows a second side view of the vulcanized component 100 of the hydraulic bearing 10 of the present invention. The figure particularly provides another perspective (relative to FIG. 1 ) of observing the second radial fluid chamber cavity 72 through the two through-holes 36. Figure 4 90° circumferential rotation of the first perspective in the figure). Furthermore, as shown in the figure, the axial fluid channel 88 leads to the first axial fluid chamber cavity 80 and the second axial fluid chamber cavity 82, and connects the first axial fluid chamber cavity 80 with the second axial fluid chamber cavity 82 along the circumferential direction at the outer edge of the cage 30. The radial fluid channel 78 can also be seen in the figure, but the entrance to the first radial fluid chamber cavity 70 and the second radial fluid chamber cavity 72 cannot be seen.

[0072] Figure 7 Shows Figure 6 Another cross-sectional view of the vulcanized component 100 of the hydraulic bearing 10 of the present invention ( Figure 3The cross-sectional view provides a perspective for observing the first axial fluid chamber cavity 80 and the second axial fluid chamber cavity 82 of the elastomer body 40. The figure also shows the first radially protruding thickened area 24 and the second radially protruding thickened area 25 of the inner core 20, the first supporting protrusion 32 and the second supporting protrusion 34 of the cage 30, and the first suspension spring arm 62 and the second suspension spring arm 64 of the suspension spring 60 formed by the elastomer body. Figure 7 The first thickened area 24 and the first support projection 32 at least partially surround the first suspension spring arm 62 in a generally axial direction. The arrangement on the first radial side is also diametrically opposed to the opposite second radial side (eg, its volumetric center of gravity and / or its xy plane center of gravity) with respect to the center of the hydraulic bearing (eg, its volumetric center of gravity and / or its xy plane center of gravity). Figure 7 The second thickened area 25 and the second support protrusion 34 at least partially surround the second suspension spring arm 64 in a substantially axial direction. This will enhance the axial rigidity of the hydraulic bearing 10.

[0073] Figure 8 A schematic axial cross-sectional view of a vulcanized component 100 of a hydraulic bearing 10 according to the present invention under an axial load is shown. Figure 8 The schematic diagram corresponds to Figure 7 Arrangement. In the assembled state of the hydraulic bearing 10, as the inner core 20 performs axial relative movement relative to the cage 30 along the corresponding direction of the axial direction AR under the action of the load Fz of the hydraulic bearing, the first axial fluid chamber cavity 80 (forming the first axial fluid chamber 84 in the assembled state) is compressed by the first suspension spring arm 62 to the first pressure surface 26 of the first radially protruding thickened area 24, and the working fluid 90 is pressed into the elastic second axial fluid chamber cavity 82 (forming the second axial fluid chamber 86 in the assembled state) through the axial fluid channel 88. This will damp the axial relative movement. Subsequently, the inner core 20 performs an opposite axial relative movement relative to the cage 30 along the corresponding direction of the negative axial direction AR under the action of the load Fz of the hydraulic bearing, and the second axial fluid chamber cavity 82 is compressed by the second suspension spring arm 64 to the second pressure surface 27 of the radially protruding thickened area 25, and the working fluid 90 is pressed into the elastic first axial fluid chamber cavity 80 through the axial fluid channel 88.

Claims

1. A hydraulic bearing (10), comprising: Inner core (20); A cage (30) surrounding the inner core (20); an elastic body (40) extending between the inner core (20) and the cage (30) and elastically connecting the inner core (20) and the cage (30) to each other; and an outer sheath (50) surrounding the cage (30), Wherein, the elastic body (40) comprises: Suspension spring (60); a first radial fluid chamber cavity (70) and a second radial fluid chamber cavity (72); and a first axial fluid chamber cavity (80) and a second axial fluid chamber cavity (82), wherein the first radial fluid chamber cavity (70) and the second radial fluid chamber cavity (72) and the first axial fluid chamber cavity (80) and the second axial fluid chamber cavity (82) are each filled with a working fluid (90) and are radially outwardly bounded by the outer sheath (50) to form a first radial fluid chamber (74) and a second radial fluid chamber (76) and a first axial fluid chamber (84) and a second axial fluid chamber (86); wherein the first radial fluid chamber (74) and the second radial fluid chamber (76) are in fluid communication with each other via a radial fluid passage (78), and are designed so that during radial relative movement between the inner core (20) and the cage (30), fluid exchange occurs between the first radial fluid chamber (74) and the second radial fluid chamber (76) via the radial fluid passage (78) along a predetermined radial direction (VR); and The first axial fluid chamber (84) and the second axial fluid chamber (86) are fluidically connected to each other via an axial fluid channel (88), and are designed so that during the axial relative movement between the inner core (20) and the cage (30), fluid exchange occurs between the first axial fluid chamber (84) and the second axial fluid chamber (86) via the axial fluid channel (88).

2. The hydraulic bearing (10) according to claim 1, wherein: The elastomeric body (40) is designed to have substantially no undercut along the axial direction (AR) on its axial end face; and / or The elastomeric body (40) and the cage (30) are constructed in the region of the radial fluid chamber recess (70, 72) and the axial fluid chamber recess (80, 82) to be substantially free of undercuts at least in two opposite predetermined radial directions (VR, -VR).

3. The hydraulic bearing (10) according to claim 1 or 2, wherein: The suspension spring (60) has a first suspension spring arm (62) and a second suspension spring arm (64), wherein the first suspension spring arm (62) and the second suspension spring arm (64) each extend from the inner core (20) to the cage (30) at a substantially diagonal position; wherein, in the circumferential direction, the first radial fluid chamber (74) and the second radial fluid chamber (76) are defined by the first suspension spring arm (62) and the second suspension spring arm (64); and Wherein, in the axial direction (AR), the first axial fluid chamber (84) is defined by the first suspension spring arm (62), and the second axial fluid chamber (86) is defined by the second suspension spring arm (64).

4. The hydraulic bearing (10) according to claim 3, wherein: The first axial fluid chamber (84) is arranged on one side of the first axial bearing end (12) of the first suspension spring arm (62), and the second axial fluid chamber (86) is arranged on one side of the second axial bearing end (14) of the second suspension spring arm (64).

5. The hydraulic bearing (10) according to claim 4, wherein: The inner core (20) has a radially protruding first thickened area (24) and a radially protruding second thickened area (25); wherein the first thickened area (24) is formed at a position corresponding to the first suspension spring arm (62) in the circumferential direction, and the second thickened area (25) is formed at a position corresponding to the second suspension spring arm (64) in the circumferential direction; and The first thickened region (24) is offset in the axial direction (AR) relative to the second thickened region (25) in the direction of the first axial bearing end (12).

6. The hydraulic bearing (10) according to claim 5, wherein: The first thickened region (24) has a first pressure surface (26), which at least partially adjoins the first axial fluid chamber (84) in the axial direction (AR), and the second thickened region (25) has a second pressure surface (27), which at least partially adjoins the second axial fluid chamber (86) in the axial direction (AR).

7. The hydraulic bearing (10) according to any one of claims 4 to 6, wherein: The cage (30) has a first support protrusion (32) at the second axial bearing end (14) and a second support protrusion (34) at the first axial bearing end (12); The first support protrusion (32) is formed at a position corresponding to the first suspension spring arm (62) in the circumferential direction, and the second support protrusion (34) is formed at a position corresponding to the second suspension spring arm (64) in the circumferential direction.

8. A method for manufacturing a hydraulic bearing (10), wherein: The method comprises the following steps: Inserting the inner core (20) into the mold; Inserting a cage (30) into the mold so that the cage (30) surrounds the inner core (20); closing the mold; introducing a radial slide into the mold; injecting an elastomeric material into the mold; vulcanizing the elastomeric material to form an elastomeric body (40) and to mold a vulcanized component (100), wherein the elastomeric body (40) elastically connects the inner core (20) to the cage (30) and comprises a suspension spring (60), a first radial fluid chamber cavity (70) and a second radial fluid chamber cavity (72) and a first axial fluid chamber cavity (80) and a second axial fluid chamber cavity (82), and the vulcanized component (100) comprises the inner core (20), the elastomeric body (40) and the cage (30); Pull out the radial slider; opening the mold; removing the vulcanized part (100) from the mold; and connecting the vulcanized component (100) to the outer sheath (50), wherein the first radial fluid chamber cavity (70) and the second radial fluid chamber cavity (72) and the first axial fluid chamber cavity (80) and the second axial fluid chamber cavity (82) are each filled with a working fluid (90) and are radially outwardly bounded by the outer sheath (50) to form a first radial fluid chamber (74) and a second radial fluid chamber (76) and a first axial fluid chamber (84) and a second axial fluid chamber (86); wherein the first radial fluid chamber (74) and the second radial fluid chamber (76) are in fluid communication with each other via a radial fluid passage (78), and are designed so that during radial relative movement between the inner core (20) and the cage (30), fluid exchange occurs between the first radial fluid chamber (74) and the second radial fluid chamber (76) via the radial fluid passage (78) along a predetermined radial direction (VR); and The first axial fluid chamber (84) and the second axial fluid chamber (86) are fluidically connected to each other via an axial fluid channel (88), and are designed so that during the axial relative movement between the inner core (20) and the cage (30), fluid exchange occurs between the first axial fluid chamber (84) and the second axial fluid chamber (86) via the axial fluid channel (88).

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