阅读说明：本技术 液压轴承和制造液压轴承的方法 (Fluid bearing and method of manufacturing fluid bearing ) 是由 约瑟夫·孔多尔 丹尼斯·莱普 于 2020-07-08 设计创作，主要内容包括：本发明公开一种液压轴承(10),包括：内芯(12),围绕内芯(12)的保持架(14),弹性体(16),其在内芯(12)与保持架(14)之间延伸并将它们弹性地连接在一起,以及围绕保持架(14)的外套管(18),其中,弹性体(16)具有第一圆周流体腔凹槽(20a)和第二圆周流体腔凹槽(20b),第一流体腔凹槽(20a)和第二流体腔凹槽(20b)径向向外分别由外套管(18)界定,以形成第一流体腔(22a)和第二流体腔(22b),弹性体(16)被构造成在其轴向(AR)的轴向端面(24a、24b)上基本没有底切,并且弹性体(16)和保持架(14)被构造成在第一流体腔凹槽(20a)和第二流体腔凹槽(20b)的区域中至少在两个预设的、彼此相反的径向(VR)上基本没有底切。(The invention discloses a hydraulic bearing (10), comprising: an inner core (12), a cage (14) surrounding the inner core (12), an elastomer body (16) extending between and elastically connecting together the inner core (12) and the cage (14), and an outer sleeve (18) surrounding the cage (14), wherein the elastomer body (16) has a first circumferential fluid chamber groove (20a) and a second circumferential fluid chamber groove (20b), the first fluid chamber groove (20a) and the second fluid chamber groove (20b) being delimited radially outwards by the outer sleeve (18), respectively, to form a first fluid chamber (22a) and a second fluid chamber (22b), the elastomer body (16) being configured substantially without undercuts on axial end faces (24a, 24b) in an axial direction (AR) thereof, and the elastomer body (16) and the cage (14) being configured at least in the region of the first fluid chamber groove (20a) and the second fluid chamber groove (20b) in two predetermined positions, Mutually opposite radial directions (VR) are substantially free of undercuts.)

1. Hydrodynamic bearing (10) comprising:

an inner core (12),

a cage (14) surrounding the inner core (12),

an elastomer (16) extending between the inner core (12) and the cage (14) and resiliently connecting them together, and

an outer sleeve (18) surrounding the cage (14),

wherein the elastomer body (16) has a first fluid chamber groove (20a) and a second fluid chamber groove (20b),

wherein the first and second fluid cavity grooves (20a, 20b) are bounded radially outwardly by the outer sleeve (18), respectively, to form first and second fluid cavities (22a, 22b),

wherein the elastomer (16) is configured to be substantially free of undercuts in the axial direction (AR) on its axial end faces (24a, 24b), and

wherein the elastomer body (16) and the cage (14) are configured substantially without undercuts in the region of the first fluid chamber groove (20a) and the second fluid chamber groove (20b) at least in two predetermined, mutually opposite radial directions (VR).

2. The fluid bearing (10) of claim 1,

wherein the cage (14) has a first support ring (26a) and a second support ring (26b),

wherein the first support ring (26a) is arranged on a first axial end of the bearing (10),

wherein the second support ring (26b) is arranged on a second axial end of the bearing (10) opposite to the first axial end, and

wherein the first fluid chamber (22a) and the second fluid chamber (22b) are arranged in axial direction (AR) between the first and second support rings (26a, 26 b).

3. The fluid bearing (10) of claim 2,

wherein the cage (14) has two connecting webs (28a, 28b) which extend in the axial direction (AR) between the first and second support rings (26a, 26b) and connect them; and

wherein the two connecting webs (28a, 28b) are arranged transversely to the preset, mutually opposite radial direction (VR) at two diametrical positions of the first and second support rings (26a, 26 b).

4. The fluid bearing (10) according to claim 3, wherein the cage (14) has an intermediate ring (30) which is arranged Axially (AR) between the first and second support rings (26a, 26b) and is connected to the first and second support rings (26a, 26b) by the two connecting webs (28a, 28 b).

5. Hydrodynamic bearing (10) according to one of the preceding claims,

wherein the first and second fluid chambers (22a, 22b) are fluidly connected to each other by a fluid channel (32), and

wherein the fluid channel (32) is defined radially outwardly by the outer sleeve (18).

6. The hydraulic bearing (10) according to claim 5, wherein the fluid channel (32) is formed at least partially on the cage (14), in particular at least partially on the first support ring (26a), on the second support ring (26b), on one or both connecting webs (28a, 28b) and/or on an intermediate ring (30).

7. The hydrodynamic bearing (10) according to claim 5, further comprising a multipart housing element (34) arranged between the elastomer body (16) and the outer sleeve (18),

wherein the fluid channel (32) is formed on the housing element (34).

8. The fluid bearing (10) of claim 5,

wherein the fluid channel (32) is formed on the elastic body (16) between the first fluid chamber groove (20a) and the second fluid chamber groove (22b),

wherein the elastomer body (16) has at least one substantially radially outwardly projecting lip (36) in the region of the fluid channel (32), which lip extends in the circumferential direction of the elastomer body (16).

9. The hydraulic bearing (10) of claim 8, wherein the elastomer body (16) is radially supported from the inside by the inner core (12) or the intermediate ring (30) in the region of the fluid channel (32).

10. Hydrodynamic bearing (10) according to one of the preceding claims,

wherein the elastomer (16) has a first membrane (38a), a second membrane (38b) and an intermediate portion (40),

wherein the first fluid chamber (22a) is bounded axially outwardly by the first diaphragm (38a),

wherein the second fluid chamber (22b) is bounded axially outwardly by the second diaphragm (38b) and

wherein the intermediate portion (40) is arranged Axially (AR) between the first fluid chamber (22a) and the second fluid chamber (22 b).

11. The fluid bearing (10) according to claim 10, wherein the first diaphragm (38a) and/or the second diaphragm (38b) is configured to be spherical.

12. The fluid bearing (10) of claim 10 or 11, wherein the first diaphragm (38a), the second diaphragm (38b) and/or the intermediate portion (40) are configured to support a suspension.

13. A method for manufacturing a fluid bearing (10), wherein the method comprises the steps of:

the inner core (12) is inserted into a mold,

inserting the cage (14) into the mold such that the cage (14) surrounds the inner core (12),

the mould is closed and the mould is closed,

at least one axial slide is inserted into the mould,

at least one pair of radial slides is inserted into the mold,

the elastomeric material is injected into the mold and,

vulcanizing an elastomeric material to form an elastomer (16) that elastically connects the inner core (12) and the cage (14), and forming a bearing component unit (46), wherein the bearing component unit (46) comprises the inner core (12), the elastomer (16), and the cage (14),

at least one axial slide and at least one pair of radial slides are extracted,

the mould is opened and the mould is opened,

removing the bearing member unit (46) from the mold, and

connecting the bearing part unit (46) to the outer sleeve (18).

Technical Field

The present invention relates to a hydrodynamic bearing, in particular a suspension support bearing, and to a method for producing a hydrodynamic bearing, in particular a suspension support bearing.

Background

Hydraulic suspension support bearings already exist in the prior art. However, they are very complicated in structure and thus expensive to manufacture.

For example, in european patent document 0458008B 1, a suspension support bearing is described in which the suspension springs are located outside the hydraulic module, which negatively affects the damping performance because the hydraulic module only works within a certain amplitude range. The manufacture of the bearing is also very complicated and consists of many separate parts.

Disclosure of Invention

It is therefore an object of the present invention to provide a hydrodynamic bearing which is simple and inexpensive to manufacture and which has a small installation space.

This task is solved by the following. Preferred embodiments result from corresponding derivations.

A first aspect of the invention relates to a fluid bearing comprising: an inner core; a cage surrounding the inner core; an elastic body extending between the core and the holder and elastically connecting them to each other; and an outer sleeve surrounding the cage, wherein the elastomer body has a first circumferential fluid chamber groove and a second circumferential fluid chamber groove, which are delimited radially outward by the outer sleeve, respectively, to form a first fluid chamber and a second fluid chamber, the elastomer body being configured to be substantially free of undercuts in the axial direction on its axial ends, and wherein the elastomer body and the cage are configured to be substantially free of undercuts in at least two predetermined, mutually opposite radial directions in the region of the first fluid chamber groove and the second fluid chamber groove.

Advantageously, the bearing of the invention has better damping and isolation from vertical ground vibrations than conventional bearings of this type, in particular as suspension support bearings, and is therefore simpler, more compact and less expensive to produce. The fact that the axial end faces of the elastomer body are substantially free of undercuts and the fluid chamber recesses of the elastomer body are also substantially free of undercuts means that the elastomer body of the bearing can be formed in one step in one mould by means of axial slides and/or radial slides. The bearing may be configured to strongly damp vibrations, especially at low frequencies. However, the structural design of the bearing is much simpler than conventional bearings, particularly suspension support bearings.

In the context of the present application, all spatial directions "above", "below" and "vertical" refer to the z-axis of a three-dimensional coordinate system, the origin of which is located approximately at the center of gravity of the bearing of the present invention and is oriented such that the z-axis is the principal axis of inertia of the bearing. Thus, the specification "axial" relates to the z-axis on the one hand, and the specification "radial" relates to an x-y plane, which extends orthogonal to the z-axis, and which is spanned by the x-and y-axes of the coordinate system on the other hand. I.e. "radial" means a direction perpendicular to the z-axis. The indication "horizontal" also refers to the x-y plane. In the case of the bearing of the present invention, the term "transverse" refers to a direction along or parallel to the x-y plane, while the term "longitudinal" refers to a direction along or parallel to the z-axis.

In the context of the present application, the term "surround" may mean that the cage of the bearing of the present invention surrounds, encloses or encircles the inner core and partially bounds the inner core in a radial direction as well as in a circumferential direction around the z-axis. I.e. in the bearing state without elastomer, the cage may represent the radial boundary of the inner core. On the other hand, in the context of the present application, the term "closed" means that the outer sleeve confines the cage in the radial and circumferential direction entirely for the height of the cage in the vertical direction, thereby enclosing the cage.

In the context of the present application, the term "circumferential" may mean that the fluid cavity grooves extend in a curved or circular path substantially around the z-axis.

The inner core may be configured to be connected to the shock absorber rod. For this purpose, the inner core can have a fastening disk. The fastening disk may have a recess in the center, through which the stepped free end of the damper rod can be passed in order to be connected with the fastening disk, for example by means of a nut. The mounting plate may be formed of a metal such as steel. By injection-molding the fastening disc with plastic, the inner core can be easily manufactured. The inner core may be substantially cylindrical. The fastening discs may be angled radially outwardly. In particular, the mounting plate may be bent in the form of a hook. The fastening disk may be configured to be rotationally symmetric with respect to an axis perpendicular to a plane in which the fastening disk generally extends.

The holder may be formed of plastic or metal, for example, aluminum. The axial end faces of the cage may be substantially completely covered by the elastomeric material. In particular, the cage may be substantially completely embedded in the elastomer. However, the cage can also be at least partially exposed radially outwards in order to enable a better connection to the outer sleeve. The cage may be substantially cylindrical.

The outer sleeve may be molded from plastic or metal. The outer sleeve may have an axial extent which substantially corresponds to the axial extent of the cage and/or the elastomer. The first and second fluid chambers may be at least partially fluid-tightly closed radially outward by the outer sleeve. The outer sleeve may be connected to a flange for connecting, for example, a fluid bearing to a vehicle frame. The outer sleeve may be substantially cylindrical.

The elastomer is formed of an elastomeric material. The elastomer may represent a single coherent member or be composed of individual components. The elastic body is configured to have no undercut on its axial end faces in the axial direction away from the elastic body, respectively, so that one or a pair of sliders may be axially pulled out in the axial direction after the elastic body is formed in the mold, or the elastic body may be axially removed from the mold after the elastic body is formed in the mold. "undercut-free design" means in particular that no undercuts are present when the elastomer is manufactured or in the unloaded state of the elastomer.

The elastomer body and the cage are configured such that there are substantially no undercuts in at least two predetermined, mutually opposite radial directions in the region of the first and second fluid chamber grooves, so that after the elastomer body has been formed in the mold, a pair of slides can be pulled out in opposite radial directions. The elastomer body and the cage may also be configured without undercuts in substantially all radial directions in the region of the first and second fluid chamber grooves. In other words, the first and second fluid cavity grooves are substantially free of undercuts in two predetermined, mutually opposite radial directions, and may also be substantially free of undercuts in all radial directions. "substantially free of undercuts" means in particular that no undercuts, or only a small number of undercuts, are present in the production of the elastomer or in the unloaded state of the elastomer, in particular only in the easily deformable regions of the elastomer. Furthermore, "substantially no undercuts" may mean that there are no undercuts on the elastomer when the bearing is mounted, or that there are only a few undercuts on the elastomer, in particular only in regions of the elastomer which are easily deformable. "substantially without undercuts" may in particular mean that during the manufacture of the elastomer the slider may be pulled out without damaging or destroying the elastomer.

The cage may have a first support ring disposable on a first axial end of the bearing and a second support ring disposable on a second axial end of the bearing opposite the first axial end, and wherein the first and second fluid chambers may be disposed axially between the first and second support rings.

The cage may also have two connecting webs which extend in the axial direction between the first and second support rings and are connected, which webs can be arranged transversely to the intended, mutually opposite radial direction at two diametral positions of the first and second support rings.

In particular, the cage can have only two connecting webs. However, the cage can also have more than two connecting webs, for example 3, 4, 5, 6, 7, 8 or more connecting webs.

The cage may also have an intermediate ring which may be arranged axially between the first and second support rings and may be connected to the first support ring and the second support ring by two connecting webs.

The intermediate ring may be disposed axially between the first and second fluid cavity grooves.

The first and second fluid chambers are defined radially outward at least in part by the outer sleeve, and the first and second fluid chambers are defined radially inward at least in part by the elastomeric body. The first fluid chamber is at least partially bounded axially upward by an elastomer. The second fluid chamber is at least partially bounded axially downward by the elastomer.

The first and second fluid chambers may be fluidly connected to each other via a fluid channel, wherein the fluid channel may be defined radially outward by the outer sleeve.

When the bearing is loaded, the damping fluid may flow from the first fluid chamber into the second fluid chamber through the fluid passage, thereby enabling damping of vibrations.

The fluid channel may be formed at least partially on the cage, in particular at least partially on the first support ring, on the second support ring, on one or both connecting webs and/or on the intermediate ring.

Advantageously, the damping of the bearing may be influenced by the geometry of the fluid passage, in particular by the length and/or cross-section of the fluid passage. For example, the damping of the bearing may be increased by increasing the length of the fluid passage and/or increasing the cross-section of the bearing.

The bearing may have a multi-part housing element arranged between the elastomer body and the outer sleeve, wherein the fluid channel may be formed on the housing element.

Advantageously, the bearing can be manufactured much more compactly and simply, since the geometry of the fluid channels does not have to be machined in the elastomer or the cage during manufacturing. Thus, the geometry of the fluid channel can be easily adapted to the requirements by merely changing the housing element.

The housing element may be arranged on the elastomer body or on the holder after the elastomer body has been formed and before the outer sleeve is connected to the elastomer body. The holder may have an exposed contact edge on which the housing element is placed. However, the housing element may also rest on the elastomer. The housing element may for example be divided into two parts. The housing element may be moulded from plastic or metal. The housing element may partially define radially outwardly a first fluid chamber groove and a second fluid chamber groove, wherein a connection portion may be formed on the housing element that fluidly connects the fluid passage to the first fluid chamber groove and the second fluid chamber groove. The housing element may substantially completely surround the elastomer in the circumferential direction. The axial extension of the housing element may substantially correspond to the axial extension of the elastomer body and/or the outer sleeve.

Alternatively or additionally, the fluid channel may be formed on the elastomer between the first and second fluid chamber grooves, wherein the elastomer may have at least one substantially radially outwardly projecting lip in the region of the fluid channel, which lip may extend in the circumferential direction of the elastomer. In particular, the elastomer body can have at least two axially spaced, substantially radially outwardly projecting lips in the region of the fluid channel, which lips extend in the circumferential direction of the elastomer body. The lip may be configured as a sheet or block. For example, the elastomer body can have, in the region of the fluid channel, blocks which project substantially radially outwards and extend in the circumferential direction of the elastomer body.

Advantageously, a fluid channel designed in this way can isolate vibrations up to about 200Hz according to design by means of the lips and dynamic stiffening occurs as little as possible, so that the dynamic stiffness can be partially smaller than the static stiffness. This is beneficial because the lip may vibrate in the axial direction during operation of the bearing. The number of lips and the size of the gap with the outer sleeve can be designed variably. The lip may also act as a pressure relief valve that opens under pressure. Furthermore, the bearing can advantageously also be used as an acoustic bearing by means of the lip, since this plays a noise-reducing role.

A fluid passage with a radially outwardly projecting lip may be formed axially between the first and second fluid cavity grooves, particularly radially outward of the elastomer. The free end of the lip may be arranged at a distance from the inner surface of the outer sleeve or may at least partly contact the inner surface of the outer sleeve. The fluid channel may have 1, 2, 3, 4, 5, 6, 7, 8 or more lips. The stiffness of each lip may decrease with the number of lips, thereby facilitating the vibration of the lips.

The elastomer may be supported from the inside radially in the region of the fluid channel by an inner core or intermediate ring.

The elastomeric body may further include a first diaphragm, a second diaphragm, and an intermediate portion, wherein the first fluid chamber is bounded axially outward by the first diaphragm, the second fluid chamber is bounded axially outward by the second diaphragm, and wherein the intermediate portion is disposed axially between the first fluid chamber and the second fluid chamber.

Here, the intermediate portion of the elastomer may act as a spring and separate the first fluid chamber from the second fluid chamber. The middle portion may be configured as a V-spring (see, e.g., fig. 2, reference numeral 40). In particular, the elastomer is vulcanized with the cage and the core.

The first diaphragm and/or the second diaphragm may be spherical.

Due to the axially outwardly convex spherical shape of the first and/or second membrane, the durability of the elastomer is improved, since the membrane is deformed in a rolling manner during operation of the bearing, resulting in less stretching. In addition, the spherical shape avoids flat impacts during operation, which reduces noise during operation.

The first diaphragm, the second diaphragm, and/or the intermediate portion may be configured to support a suspension.

A second aspect of the invention relates to a method for manufacturing a fluid bearing, wherein the method comprises the steps of: inserting the inner core into a mold, inserting the cage into the mold such that the cage surrounds the inner core, closing the mold, introducing at least one axial slider into the mold, introducing at least one pair of radial sliders into the mold, injecting an elastomer material into the mold, vulcanizing the elastomer material to form an elastomer elastically connecting the inner core and the cage, and forming a bearing component unit, wherein the bearing component unit includes the inner core, the elastomer and the cage, pulling out the at least one axial slider and the at least one pair of radial sliders, opening the mold, demolding the bearing component unit from the mold, and connecting the bearing component unit to the outer sleeve.

The above description of the hydrodynamic bearing applies correspondingly to the method described here.

Advantageously, the method of the present invention makes fluid bearings, particularly suspension support bearings, simpler than conventional bearings of this type, and more advantageous for cost reduction.

Connecting the bearing part unit to the outer sleeve may comprise pressing the bearing part unit into the outer sleeve such that the bearing part unit is at least partially in contact with the outer sleeve, or such that the outer sleeve covers the bearing part unit such that the bearing part unit and the outer sleeve are at least partially in contact. The housing element can be arranged on the elastomer body or on the bearing part unit before the bearing part unit is connected to the outer sleeve.

The following is a description of the drawings, whose main purpose is to adopt examples to illustrate some embodiments of the first aspect. It should be understood that the subject matter of the present invention is not limited to the embodiments described below. Various features may be combined to form further embodiments.

Drawings

Figure 1 shows an exploded view of an embodiment of the bearing of the present invention,

figure 2 shows a cross-sectional view of the embodiment according to figure 1,

figure 3 shows a cross-sectional view of another embodiment of the bearing of the present invention,

figure 4 shows a cross-sectional view of another embodiment of the bearing of the present invention,

figure 5 shows an exploded view of the embodiment according to figure 4,

figure 6 shows a cross-sectional view of another embodiment of the bearing of the present invention,

fig. 7 shows a perspective view of an embodiment of the bearing according to fig. 6, the bearing having no outer sleeve,

FIG. 8 shows a cross-sectional view of another embodiment of the bearing of the present invention, and

fig. 9 shows a perspective view of an embodiment of the bearing according to fig. 8, the bearing not having an outer sleeve.

List of reference numerals

10 fluid bearing

11 fastening disc

12 inner core

14 holder

16 elastomer

18 outer sleeve

20a, 20b fluid chamber recesses

22a, 22b fluid chamber

24a, 24b axial end faces

26a, 26b support ring

28a, 28b connecting webs

30 intermediate ring

32 fluid channel

34 housing element

36 lip

38a, 38b diaphragm

39a, 39b protrusions

40 middle part

42 shock absorber

44 Flange

46 bearing member unit

48a, 48b support edge

50 support block

VR Preset radial

Axial direction of AR

Detailed Description

Fig. 1 shows the structure of a bearing 10 in an exploded view. The bearing 10 has an annular fastening disc 11, which annular fastening disc 11 is injection-moulded in plastic to form an inner core 12. The core 12 together with the fastening disk 11 is inserted into a mold together with the holder 14. Thereafter, the elastomer material is injected into the mold and around the cage 14 and the core 12, thereby molding and vulcanizing the elastomer 16 with the cage 14 and the core 12. The elastomer 16 is constructed such that it is free of undercuts in the axial direction and at least two opposing radial directions. After demolding, the outer sleeve 18 is attached to the cage 14 or elastomer. In particular, the unit with the fastening disk 11, the inner core 12, the elastomer body 16 and the holder 14 is pushed or pressed from the inside out into the outer sleeve 18, or the outer sleeve 18 is slid or pushed over the unit and, if necessary, calibrated or pressed.

Fig. 2 shows the bearing 10 of fig. 1 in a cross-section along the central axis of the bearing 10. For simplicity, the bearing 10 is spatially oriented such that the cross-section is symmetrical with respect to the z-axis of the coordinate system shown. In addition, the bearing 10 is oriented such that the predetermined, mutually opposite radial directions VR extend along or parallel to the y-axis of the auxiliary coordinate system, i.e. into or out of the drawing plane, and the axial directions AR extend along or parallel to the z-axis of the specified coordinate system. From the inside to the outside, fig. 2 shows an inner core 12 with a fastening disc 11, an elastomer body 16 and a cage 14 surrounded by a bearing 10. The elastomer 16 is arranged between the inner core 12 and the cage 14 in the radial direction or in the x and y directions (in the x direction in the cross-section shown). The radially inner side of the elastomer 16 is vulcanized to the inner core 12 and the radially outer side is vulcanized to the cage 14. In fig. 2, the end faces 24a, 24b of the spring body 16 are designed without undercuts in the axial direction AR (here in the z direction or in the direction opposite to the z direction), as is shown by way of example. In the axial direction (i.e., along the z-axis), the first and second diaphragms 38a, 38b extend downward and upward from the intermediate portion 40. On the lower and upper axial end faces 24a, 24b of the elastomer body 16, the lower and upper diaphragms 38a, 38b have at least one radially inner projection 39a, 39b, respectively, projecting axially from the inner core 12, which also acts as a stop damper during operation of the bearing 10. The elastomer 16 is funnel-shaped on its axial end faces 24a and 24b, in particular is configured without undercuts in the axial direction.

The cage 14 has, from bottom to top in the axial direction, a support ring 26a, an intermediate ring 30 and a support ring 26 b. In the intermediate ring 30, an annular groove is formed on the side of the intermediate ring 30 facing away from the intermediate portion 40 of the elastomer 16 and forms the fluid channel 32 bounded by the intermediate ring 30 of the cage 14 and the outer sleeve 18. The support ring 26a, the intermediate ring 30 and the support ring 26b are connected to one another by connecting webs 28a and 28b as shown, wherein the connecting webs 28a and 28b are part of the cage 14. The diaphragms 38a and 38b are vulcanized to the support rings 26a and 26b, respectively. In the present case, two preset, mutually opposite radial directions correspond to the positive and negative y-directions, respectively.

Fluid chambers 22a and 22b are formed by the arrangement of elastomer 16, cage 14, and outer sleeve 18, extend substantially parallel to one another about the z-axis, and are fluidly connected to one another via a fluid passage 32. That is, when the bearing 10 is loaded, the damping fluid may flow from the first fluid chamber 22a into the second fluid chamber 22b, and vice versa. The fluid chambers 22a and 22b are radially bounded by the outer sleeve 18 and the diaphragms 38a and 38b of the elastomer 16, and axially bounded by the intermediate ring 30 of the cage 14, the intermediate portion 40 of the elastomer 16, the support rings 26a, 26b, and the diaphragms 38a, 38 b.

Fig. 3 shows another embodiment of the bearing 10, wherein the bearing 10 is mounted on a damper 42 and pressed into a flange 44. Compared to the cross section shown in fig. 2, the cross section shown is rotated by 90 ° about the z axis, so that the predetermined, mutually opposite radial directions VR now extend in the drawing plane. The fastening disk 11 is bent in an angled or hook-shaped or L-shaped manner in a radial edge region which is injection-molded over with the plastic material of the inner core 12. The difference from the embodiment of the bearing 10 shown in fig. 1 and 2 is that the lower diaphragm 38a of the elastomer body 16 is configured as a suspension spring, while the cage 14 does not have the intermediate ring 30. The support ring 26a has a groove which is delimited radially outwards by the outer sleeve 18, so that a fluid channel 32 is formed. Fluid chamber 22a is defined by diaphragm 38a, intermediate portion 40, and outer sleeve 18. The fluid chamber 22b is defined by the intermediate portion 40 of the cage 14, the diaphragm 38b, the outer sleeve 18, and the support ring 26 b.

In the illustrated embodiment, the elastic body 16 is configured such that there is no undercut in the axial direction AR on the axial end faces 24a and 24b of the elastic body 16. In the radial direction VR, the elastomer 16 does not seem to be completely free of undercuts in the region of the intermediate portion 40. The reason why the so-called undercut occurs is that the bearing 10 is pressed into the flange 44 in the illustrated assembled state. The intermediate portion 40 of the elastomer 16 deforms as a result of the pressing in, so that it appears that the elastomer 16 is not undercut-free in the radial direction VR. However, after the bearing 10 is manufactured, the elastic body 16 is completely free from undercuts in the unloaded state of the bearing 10.

Fig. 4 shows another embodiment of the bearing 10. The illustrated construction is similar to the embodiment of the bearing 10 shown in fig. 2. Similar to fig. 3, the cross-section shown is rotated 90 about the z-axis compared to the cross-section shown in fig. 2. The difference is that the cage 14 (and in particular the intermediate ring 30) does not have a recess for the fluid passage 32, but rather the shape of the elastomer 16 is such that the fingers, tabs or lips 36 project radially outwardly from the elastomer and substantially from the intermediate ring 30. The fluid channel 32 extends along the radially inner side of the outer sleeve 18 in a vertical direction parallel to the z-axis and perpendicular to the lip 36, and is bounded radially from the outside by the outer sleeve 18. The lip 36 may act as a pressure relief valve and regulate the flow of damping fluid from the fluid chamber 22a into the fluid chamber 22b, and vice versa. In other words, in a cross section through the bearing 10, the fluid channel 32 is annular in shape perpendicular to the flow direction of the damping liquid, i.e. in a cross section perpendicular to the z-axis, i.e. in a longitudinal cross section of the bearing 10. Similar to fig. 2, the diaphragms 38a and 38b have at least one protrusion 39a and 39b, respectively, in the region of the inner core 12 and projecting axially from the inner core 12. The protrusions 39a and 39b are cuboid, pyramidal or prismatic at their ends remote from the core.

The elastomer 16 of the illustrated bearing 10 is configured without undercuts on its end faces 24a and 24b, both in the axial direction AR and in the radial direction VR.

Fig. 5 shows an exploded view of the bearing 10 according to the structure shown in fig. 4. The lip 36 of the elastomer 16 extends substantially annularly around the intermediate ring 30 of the cage 14 and thus around the z-axis of the coordinate system shown. The cage 14 shown in fig. 5 also has radially outwardly projecting blocks or support blocks 50 at about the level of the intermediate ring 30, which blocks or support blocks 50 engage or are inserted into grooves or steps of the outer sleeve 18 provided for assembly when the bearing 10 is completely assembled, so that they act as a support when a force is applied to the bearing 10. Due to the geometry of the elastomer 16 shown, when the bearing 10 is loaded, damping fluid may flow axially (i.e., along the z-axis), along the outer sleeve 18 from one fluid chamber to another, and thus through the lip 36.

Fig. 6 shows a similar construction of the bearing 10 as shown in fig. 4 and 5. As shown in fig. 3, the bearing 10 is mounted on a damper 42 and pressed into a flange 44. The fastening disk 11 is bent in an angled or hook-shaped or L-shaped manner in a radial edge region which is injection-molded over the inner core 12. The difference from the embodiment of the bearing 10 shown in fig. 4 and 5 is that the lower diaphragm 38a of the elastomer 16 is configured to support the suspension, while the cage 14 lacks the intermediate ring 30. The lip 36 of the elastomer 16 projects substantially radially outwardly from the inner core 12.

Similar to fig. 3, the elastomer 16 shown in fig. 6 is configured such that there are substantially no undercuts on the axial end faces 24a and 24b of the elastomer 16. At radial VR, the elastomer 16 does not appear to be completely free of undercuts in the region of the lip 36. Since the bearing 10 is pressed into the flange 44 in the illustrated assembled state, a so-called undercut can occur. By pressing in, the easily deformable and vibratable lip 36 of the elastomer 16 is deformed, so that it appears that the elastomer 16 is not undercut-free in the radial direction. However, after the bearing 10 is manufactured, the elastomer 16 may be completely free of undercuts in the unloaded state of the bearing 10. Alternatively, the elastomer 16 can also be produced with a small amount of undercut in the radial VR in the region of the lip 36, since, due to the deformability of the lip 36 or of the lip 36, the elastomer 16 can still be easily removed from the mold in the radial VR during production and the slide can easily be pulled out in the radial VR during production. For example, the lip 36 may be curved or bowed radially outward and in an axial direction. However, the elastomer 16 is substantially free of undercuts in the radial direction VR, since only a small amount of undercuts are present in the region of the yielding lip 36.

Fig. 7 shows a perspective view of the assembled bearing 10 according to the embodiment shown in fig. 6, but without the outer sleeve 18. In the context of the present application, the bearing 10 without the outer sleeve 18 is referred to as a bearing component unit 46.

The bearing member unit 46 is shown in an unloaded state. The lip 36 is slightly curved. Thus, fig. 7 shows the situation mentioned in the description of fig. 6, in which the elastomer 16 has a small amount of undercuts in the radial direction due to the bending of the lip 36, but the elastomer 16 is configured to have substantially no undercuts in the radial direction, because the lip 36 is easily deformed, so that the elastomer 16 can be easily removed from the mold in the radial direction VR.

Fig. 8 shows another embodiment of the bearing 10. Fig. 8 shows a similar structure of the bearing 10 in cross section as shown in fig. 3 and 6. As shown in fig. 3, the bearing 10 is mounted on a damper 42 and pressed into a flange 44. The fastening disk 11 is bent in an angled or hook-shaped or L-shaped manner in a radial edge region which is injection-molded over the inner core 12. The lower diaphragm 38a of the elastic body 16 is configured here to support a suspension. In addition, the lower and upper diaphragms 38a and 38b have at least one pyramid-shaped or prism-shaped protrusion 39a and 39b, respectively, protruding from the lower and upper axial edges of the core 12. According to this embodiment, the bearing 10 additionally has a multi-part housing element 34 which is arranged between the elastomer body 16 and the outer sleeve 18. The fluid passage 32 is formed in the housing member 34. The housing element 34 is made of plastic. The multipart housing element 34 is attached to the cage 14 by means of the support rings 26a and 26b, which support rings 26a and 26b may also be referred to as retaining rings. In particular, the support rings 26a and 26b can have stepped support edges 48a and 48b, on which the housing element 34 can be arranged and can thus be tensioned or clamped in the axial direction between the retaining rings and can be held radially from the inside by the intermediate portion 40 of the elastomer body 16 and radially from the outside by the outer sleeve 18. The fluid passages 32 formed in the housing member 34 place the lower and upper fluid chambers 22a and 22b in fluid communication, i.e., damping fluid may flow from one fluid chamber 22a to the other fluid chamber 22b and vice versa via the fluid passages 32 in the housing member 34 when the bearing 10 is loaded. The fluid chambers 22a and 22b are defined by the elastomer 16, the support ring 26a or 26b, and the outer sleeve 18, respectively.

The elastomer 16 is completely free of undercuts on its end faces 24a and 24b in the radial direction VR and in the axial direction AR.

Fig. 9 shows a perspective view of the bearing 10 without the outer sleeve 18, i.e. the bearing component unit 46, as in the configuration shown in fig. 8. The bearing member unit 46 is rotated about the z-axis by approximately 45 deg. relative to the cross-section in fig. 8.