Hydraulic bearing and method for manufacturing a hydraulic bearing
Patent Information
- Authority / Receiving Office
- DE · DE
- Patent Type
- Patents
- Current Assignee / Owner
- SUMITOMO RIKO CO LTD
- Filing Date
- 2019-08-27
- Publication Date
- 2026-07-23
AI Technical Summary
Existing hydraulic strut support bearings are complex in structure, leading to high manufacturing costs and negatively impacting damping performance due to the hydraulic module's limited amplitude range.
A hydraulic bearing design featuring an inner core, cage, and elastomeric body with circumferential fluid chambers and axially positioned end faces without undercuts, allowing for simplified production and improved damping capabilities.
The design results in a more affordable, compact, and effective damping solution that isolates vertical ground vibrations, with enhanced vibration damping at low frequencies and reduced noise, while maintaining structural simplicity.
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Abstract
Description
[0001] The invention relates to a hydraulic bearing, in particular a strut support bearing, and a method for manufacturing a hydraulic bearing, in particular a strut support bearing.
[0002] Hydraulic strut mounts already exist in the prior art. However, their design is very complex and therefore expensive to manufacture.
[0003] European patent 0 458 008 B1, for example, describes a strut mount bearing in which the suspension spring is located outside the hydraulic module. This negatively impacts damping performance because the hydraulic module only operates within a specific amplitude range. Furthermore, the design of this bearing is very complex and consists of many individual parts.
[0004] Therefore, the object of the present invention is to provide a hydraulic bearing that is easy and inexpensive to manufacture and requires less installation space.
[0005] This problem is solved by the independent claims. Preferred embodiments are described in the respective dependent claims.
[0006] A first aspect of the invention relates to a hydraulic bearing comprising: an inner core, a cage surrounding the inner core, an elastomer body extending between the inner core and the cage and elastically connecting them, and an outer sleeve enclosing the cage, wherein the elastomer body has a first circumferential fluid chamber recess and a second circumferential fluid chamber recess, wherein the first fluid chamber recess and the second fluid chamber recess are each radially outwardly bounded by the outer sleeve to form a first fluid chamber and a second fluid chamber, wherein the elastomer body is substantially free of undercuts in the axial direction at its axial end faces, and wherein the elastomer body and the cage in the region of the first fluid chamber recess and the second fluid chamber recess are formed in at least two predetermined,are essentially free of undercuts in opposite radial directions.
[0007] Advantageously, the bearing according to the invention is simpler, more compact, and more cost-effective to manufacture than conventional bearings of this type, particularly as strut mount bearings, while still providing good damping and isolation of vertical ground vibrations. Because the axial end faces of the elastomer body and the fluid chamber recesses of the elastomer body are essentially free of undercuts, the elastomer body of the bearing can be formed in a single step in a tool using axial and / or radial slides. The bearing can be configured to strongly dampen vibrations, especially at low frequencies. The design of the bearing is significantly simpler than that of conventional bearings, particularly strut mount bearings.
[0008] Within the scope of this application, all spatial direction designations "top," "bottom," and "vertical" refer to the z-axis of a three-dimensional coordinate system whose origin is located approximately at the center of mass of the bearing according to the invention and which is oriented such that the z-axis represents one of the principal axes of inertia of the bearing. Accordingly, the term "axial" refers, on the one hand, to the z-axis, and the term "radial" refers, on the other hand, to the xy-plane spanned by the x- and y-axes of the coordinate system, which extends orthogonally to the z-axis. That is, "radial" refers to directions perpendicular to the z-axis. The term "horizontal" also refers to the xy-plane. In the case of the bearing according to the invention, the term "transverse" refers to directions along or parallel to the xy-plane, while the term "longitudinal" denotes directions along or parallel to the z-axis.
[0009] Within the scope of this application, the term "surround" can mean that the cage of the bearing according to the invention frames, encloses, or surrounds the inner core and partially limits the inner core in the radial direction and in the circumferential direction around the z-axis. That is, in a state of the bearing without an elastomer body, the cage can constitute a radial boundary for the inner core. Conversely, within the scope of this application, the term "enclose" can mean that the outer sleeve completely limits the cage in the radial direction and in the circumferential direction for the full height of the cage in the vertical direction, thus enclosing the cage.
[0010] The term "circumferential" in the context of this application can mean that the fluid chamber recesses essentially follow a curved or circular path around the z-axis.
[0011] The inner core can be designed to be connected to a shock absorber rod. For this purpose, the inner core can have a mounting washer. The mounting washer can have a central recess through which a stepped, free end of the shock absorber rod can be passed to be connected to the mounting washer, for example, by means of a nut. The mounting washer can be made of a metal, such as steel. The inner core can be easily manufactured by overmolding the mounting washer with plastic. The inner core can be essentially cylindrical. The mounting washer can be angled outwards in a radial direction. The mounting washer can be bent, in particular, into a hook shape. The mounting washer can be rotationally symmetrical about an axis perpendicular to the plane in which the mounting washer essentially extends.
[0012] The cage can be made of plastic or metal, for example, aluminum. The axial end faces of the cage can be essentially completely covered by the material of the elastomer body. In particular, the cage can be essentially completely embedded in the elastomer body. However, radially outward, the cage can also be at least partially exposed to improve bonding with the outer sleeve. The cage can be essentially cylindrical.
[0013] The outer sleeve can be made of plastic or metal. The outer sleeve can have an axial extent that essentially corresponds to the axial extent of the cage and / or the elastomer body. The first and second fluid chambers can be at least partially sealed radially outwards by the outer sleeve in a fluid-tight manner. The outer sleeve can be connected to a flange to connect the hydraulic bearing, for example, to a vehicle frame. The outer sleeve can be essentially cylindrical.
[0014] The elastomer body is formed from an elastomer material. The elastomer body can be a single, continuous component or composed of individual, separate components. The elastomer body is designed without undercuts on its axial end faces, extending axially away from the body, so that after forming the elastomer body in a mold, a slide or a pair of slides can be pulled out axially, or the elastomer body can be removed axially from the mold after forming. "Designed without undercuts" means, in particular, that no undercut exists during the manufacturing process or in the unloaded state of the elastomer body.
[0015] The elastomer body and the cage are designed to be essentially free of undercuts in at least two predetermined, opposite radial directions in the region of the first and second fluid chamber recesses, so that after the elastomer body has been formed in a tool, a pair of slides can be pulled out in opposite radial directions. The elastomer body and the cage can also be designed to be essentially free of undercuts in all radial directions in the region of the first and second fluid chamber recesses. In other words, the first and second fluid chamber recesses are designed to be essentially free of undercuts in two predetermined, opposite radial directions and can also be designed to be essentially free of undercuts in all radial directions."Essentially undercut-free" means, in particular, that no undercut exists during the manufacture of the elastomer body or in its unloaded state, or that only a minimal undercut exists, especially only in easily deformable areas of the elastomer body. Furthermore, "essentially undercut-free" can mean that no undercut exists on the elastomer body in its assembled state, or that only a minimal undercut exists, especially only in easily deformable areas. "Essentially undercut-free" can also mean, in particular, that a slider can be pulled out during the manufacture of the elastomer body without damaging or destroying it.
[0016] The cage can have a first support ring and a second support ring, wherein the first support ring can be arranged at a first axial end section of the bearing, wherein the second support ring can be arranged at a second axial end section of the bearing opposite the first axial end section, and wherein the first fluid chamber and the second fluid chamber can be arranged in the axial direction between the first and the second support ring.
[0017] The cage may further have two connecting webs extending axially between the first and second support rings and connecting them, wherein the two connecting webs may be arranged at two diametrically opposed positions of the first and second support rings transverse to the predetermined, mutually opposite radial directions.
[0018] The cage can have only two connecting bars. However, the cage can also have more than two connecting bars, for example 3, 4, 5, 6, 7, 8 or more connecting bars.
[0019] 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 and second support rings via the two connecting webs.
[0020] The intermediate ring can be arranged in the axial direction between the first fluid chamber recess and the second fluid chamber recess.
[0021] The first and second fluid chambers are at least partially bounded radially outwards by the outer sleeve, while the first and second fluid chambers are at least partially bounded radially inwards by the elastomer body. The first fluid chamber is at least partially bounded axially upwards by the elastomer body. The second fluid chamber is at least partially bounded axially downwards by the elastomer body.
[0022] The first and second fluid chambers can be fluidically connected to each other via a fluid channel, whereby the fluid channel can be limited radially outwards by the outer sleeve.
[0023] When the bearing is under load, a damping fluid can flow from the first fluid chamber to the second fluid chamber via the fluid channel, so that vibrations can be dampened.
[0024] The fluid channel can 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.
[0025] Advantageously, the damping of the bearing can be influenced by the geometry of the fluid channel, in particular by its length and / or cross-section. For example, increasing the length of the fluid channel and / or the cross-section of the bearing can increase the damping of the bearing.
[0026] The bearing can have a multi-part shell element which is arranged between the elastomer body and the outer sleeve, wherein the fluid channel can be formed on the shell element.
[0027] Advantageously, the bearing can be manufactured more compactly and much more easily because the fluid channel geometry does not need to be incorporated into the elastomer body or the cage during production. This allows the fluid channel geometry to be easily adapted to the requirements simply by changing the shell element.
[0028] The shell element can be positioned on the elastomer body or on the cage after the elastomer body has been formed and before the outer sleeve is connected to the elastomer body. The cage can have exposed bearing edges on which the shell element rests. Alternatively, the shell element can rest directly on the elastomer body. The shell element can, for example, be made of two parts. The shell element can be made of plastic or metal. The shell element can partially define the first and second fluid chamber recesses radially outwards, and connecting sections can be formed on the shell element that fluidically connect the fluid channel to the first and second fluid chamber recesses. The shell element can substantially completely enclose the elastomer body in the circumferential direction.The axial extent of the shell element can essentially correspond to the axial extent of the elastomer body and / or the outer sleeve.
[0029] The fluid channel can alternatively or additionally be formed on the elastomer body between the first fluid chamber recess and the second fluid chamber recess, wherein the elastomer body in the region of the fluid channel can have at least one substantially radially outwardly projecting lip that can extend along a circumferential direction of the elastomer body. In particular, the elastomer body in the region of the fluid channel can have at least two axially spaced, substantially radially outwardly projecting lips that extend along a circumferential direction of the elastomer body. The lips can be lamellar or block-like. For example, the elastomer body in the region of the fluid channel can have a substantially radially outwardly projecting block that extends along a circumferential direction of the elastomer body.
[0030] Advantageously, a fluid channel designed in this way, with its lips, allows vibrations up to approximately 200 Hz, and even higher depending on the design, to be isolated while minimizing dynamic stiffness. This means the dynamic stiffness can sometimes be lower than the static stiffness. This is further enhanced by the fact that the lips can oscillate axially during bearing operation. The number of lips and the gap between them and the outer sleeve can be varied. The lips can also act as a pressure relief valve, opening at a specific pressure. Furthermore, the bearing can also be advantageously used as an acoustic bearing due to noise reduction.
[0031] The fluid channel with radially outwardly projecting lips can be formed axially between the first and second fluid chamber recesses, particularly on a radially outer section of the elastomer body. The free ends of the lips can be spaced apart from the inner surface of the outer sleeve, or at least partially in contact with the inner surface of the outer sleeve. The fluid channel can have 1, 2, 3, 4, 5, 6, 7, 8, or more lips. Increasing the number of lips reduces the stiffness of each individual lip, which promotes lip vibration.
[0032] The elastomer body can be radially supported from the inside in the area of the fluid channel by the inner core or the intermediate ring.
[0033] The elastomer body can further comprise a first membrane, a second membrane and an intermediate section, wherein the first fluid chamber can be bounded axially outwards by the first membrane, wherein the second fluid chamber can be bounded axially outwards by the second membrane, and wherein the intermediate section can be arranged in the axial direction between the first fluid chamber and the second fluid chamber.
[0034] The intermediate section of the elastomer body can act as a spring, separating the first fluid chamber from the second. This intermediate section can be designed as a V-spring (see, for example, [reference]). Fig. 2, reference numeral 40). The elastomer body is vulcanized in particular to the cage and the inner core.
[0035] The first membrane and / or the second membrane can be convex.
[0036] The axially outward bulging, convex shape of the first and / or second diaphragm improves the durability of the elastomer body, as the diaphragms deform by rolling during bearing operation, resulting in lower elongation. Furthermore, the convex shape prevents flat impact during operation, thus reducing noise generation.
[0037] The first membrane, the second membrane and / or the intermediate section can be designed as a supporting spring.
[0038] A second aspect of the invention relates to a method for manufacturing a hydraulic bearing, the method comprising the following steps: inserting an inner core into a tool, inserting a cage into the tool such that the cage surrounds the inner core, closing the tool, inserting at least one axial slide into the tool, inserting at least one pair of radial slides into the tool, injecting an elastomer material into the tool, vulcanizing the elastomer material to form an elastomer body that elastically connects the inner core and the cage, and to form a bearing component unit, wherein the bearing component unit comprises the inner core, the elastomer body and the cage, withdrawing the at least one axial slide and the at least one pair of radial slides, opening the tool, demolding the bearing component unit from the tool, and connecting the bearing component unit to an outer sleeve.
[0039] The above explanation regarding the hydraulic bearing also applies accordingly to the method described here.
[0040] Advantageously, the method according to the invention makes it possible to manufacture a hydraulic bearing, in particular a strut support bearing, more easily, more compactly and more cost-effectively than conventional bearings of this type.
[0041] Connecting the bearing unit to the outer sleeve can involve pressing the bearing unit into the outer sleeve so that the bearing unit and the outer sleeve are at least partially in contact, or fitting the outer sleeve over the bearing unit so that the bearing unit and the outer sleeve are at least partially in contact. Before connecting the bearing unit to the outer sleeve, the shell element can be positioned on the elastomer body or on the bearing unit.
[0042] The following is a description of the figures, which are intended to serve as examples illustrating some embodiments of the first aspect. It is understood that the subject matter of the invention is not limited to the embodiments described below. Individual features can be combined to form further embodiments.
[0043] They show: Fig. 1 an exploded view of an embodiment of the bearing according to the invention, Fig. 2 a cross-sectional view of the embodiment according to Fig. 1, Fig. 3 a cross-sectional view of a further embodiment of the bearing according to the invention, Fig. 4 a cross-sectional view of a further embodiment of the bearing according to the invention, Fig. 5 an exploded view of the embodiment according to Fig. 4, Fig. 6 a cross-sectional view of a further embodiment of the bearing according to the invention, Fig. 7 a perspective view of the embodiment of the bearing according to Fig. 6 without outer sleeve, Fig. 8 a cross-sectional view of a further embodiment of the bearing according to the invention, and Fig. 9 a perspective view of the embodiment of the bearing according to Fig. 8 without outer sleeve.
[0044] Fig. Figure 1 shows the structure of the warehouse. 10 based on an exploded view diagram. The warehouse 10 features a ring-shaped mounting disc 11 which is overmolded with a plastic to protect the inner core 12 to train. The inner core 12 including mounting washer 11 will be with the cage 14 placed in a tool. Then elastomer material is injected into the tool and around the cage. 14 and around the inner core 12injected, causing the elastomer body 16 shaped and attached to the cage 14 and to the inner core 12 is vulcanized. The elastomer body 16 It is shaped in such a way that it has no undercuts in the axial direction or in at least two opposing radial directions. After demolding, the outer sleeve 18 with the cage 14 or connected to the elastomer body. In particular, the unit is connected from the inside out, showing the mounting disc. 11 , the inner core 12 , the elastomer body 16 and the cage 14 into the outer sleeve 18 pushed in or pressed in, or the outer sleeve 18 It is placed over or pushed onto this unit, and calibrated or pressed if necessary.
[0045] Fig. 2 shows the warehouse 10 out of Fig. 1 in cross-section along a central axis of the bearing 10For the sake of simplicity, the camp was 10 oriented in space such that the cross-section is symmetrical to the z-axis of the depicted coordinate system. Furthermore, the bearing 10 oriented so that the predetermined, mutually opposite radial directions VR 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 run along or parallel to the z-axis of the specified coordinate system. From the inside out, it points Fig. 2 the from the warehouse 10 included inner core 12 with mounting disc 11 , the elastomer body 16 and the cage 14 The elastomer body 16 is in the radial direction or in the x and y direction, in the cross-section shown in the x direction, between the inner core 12 and the cage 14arranged. The elastomer body 16 is attached to the inner core with its radial inner surface 12 and with its radial outer side against the cage 14 vulcanized. Fig. Figure 2 shows, by way of example, that the front faces 24a , 24b of the elastomer body 16 in axial direction AR , here in the z-direction or against the z-direction, are designed without undercuts. In the axial direction, i.e., along the z-axis, they extend from the intermediate section. 40 downwards as well as upwards the first membrane 38a and the second membrane 38b . On the lower axial end face 24a and the upper axial face 24b of the elastomer body 16 indicate the lower membrane 38a and the upper membrane 38b each at least one radially inner core, axially separated from the inner core 12 protruding bulge 39a and 39bon, which also act as impact dampers in the operation of the bearing 10 serve. The elastomer body 16 is on its axial end faces 24a and 24b funnel-shaped, and in particular free of undercuts in the axial direction.
[0046] The cage 14 has a support ring in the axial direction from bottom to top 26a , an intermediate ring 30 and a support ring 26b up. In the intermediate ring 30 is on the intermediate section 40 of the elastomer body 16 pioneering side of the intermediate ring 30 a ring-shaped recess is formed, which is limited by the intermediate ring 30 of the cage 14 and the outer sleeve 18 the fluid channel 32 forms the support ring 26a , the intermediate ring 30 and the support ring 26b are by means of the connecting bridges shown 28a and 28bconnected to each other, with the connecting bridges 28a and 28b part of the cage 14 are. The membrane 38a and the membrane 38b are each attached to the support ring 26a and to the support ring 26b vulcanized. In this case, the two predetermined, opposite radial directions correspond to the positive and negative y-directions.
[0047] By the arrangement of the elastomer body 16 , of the cage 14 and the outer sleeve 18 This creates fluid chambers that are essentially parallel to each other and run around the z-axis. 22a and 22b , which via the fluid channel 32 are fluidically connected to each other, i.e., damping fluid can flow when the bearing is loaded. 10 from the first fluid chamber 22a into the second fluid chamber 22b or vice versa, flow. The fluid chamber 22a and 22bare radially from the outer sleeve 18 and the membranes 38a or 38b of the elastomer body 16 limited and axially from the intermediate ring 30 of the cage 14 , the intermediate section 40 of the elastomer body 16 and the support rings 26a , 26b as well as the membranes 38a , 38b limited.
[0048] Fig. Figure 3 shows another embodiment of the bearing. 10 , where the camp 10 on a shock absorber 42 was mounted and into a flange 44 was pressed in. The cross-section shown is in comparison to the one in Fig. The cross-section shown in section 2 is rotated 90° around the z-axis so that the predetermined, opposite radial directions are aligned. VR now run in the drawing plane. The mounting washer 11 is in the radial, edge area that is in contact with the plastic material of the inner core12 is overmolded, angled, hook-shaped, or L-shaped. A difference from the one in Fig. 1 and Fig. 2 shown embodiment of the bearing 10 is that the lower membrane 38a of the elastomer body 16 is designed as a support spring and the cage 14 no intermediate ring 30 features the support ring 26a has a recess that extends radially outwards through the outer sleeve 18 limits the fluid channel 32 forms. The fluid chamber 22a is passed through the membrane 38a , the intermediate section 40 and the outer sleeve 18 limited. The fluid chamber 22b is through the intermediate section 40 , the membrane 38b , the outer sleeve 18 and the support ring 26b of the cage 14 limited.
[0049] In the embodiment shown, the elastomer body 16designed in such a way that on the axial end faces 24a and 24b of the elastomer body 16 no undercut in the axial direction AR exists. In a radial direction VR The elastomer body appears 16 in the area of the intermediate section 40 not completely free of undercuts. The apparent undercut arises because the bearing 10 in the mounted state shown, into the flange 44 It was pressed in. The pressing process deforms the intermediate section. 40 of the elastomer body 16 , so that it appears that the elastomer body 16 in a radial direction VR is not free of undercuts. In the unloaded state of the bearing. 10 after the production of the bearing 10 is the elastomer body 16 however, completely free of undercuts.
[0050] Fig. Figure 4 shows another embodiment of the bearing. 10 The setup shown is similar to the one in Fig. 2 shown embodiment of the bearing 10 As in Fig. 3 is the cross-section shown rotated 90° around the z-axis relative to the one in Fig. The cross-section shown in section 2 is rotated. One difference is that the cage 14 , especially the intermediate ring 30 , no recess for the fluid channel 32 exhibits, but the elastomer body 16 is shaped in such a way that fingers, lamellae or lips 36 in a radial direction outwards from the elastomer body and essentially from the intermediate ring 30 protrudes. The fluid channel 32 runs vertically parallel to the z-axis and perpendicular to the lips 36 along the radial inner side of the outer sleeve 18 and is routed radially from the outside through the outer sleeve 18 limited. The lips 36They can 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, the fluid channel 32 in a cross-section through the warehouse 10 perpendicular to the flow direction of the damping fluid, i.e., in a section perpendicular to the z-axis, thus a longitudinal section of the bearing. 10 , ring-shaped. Similar to in Fig. The membranes shown in 2 38a and 38b each at least one in the area of the inner core 12 located and from the inner core 12 axially projecting bulge 39a and 39b The bulges 39a and 39b At their ends, which point away from the inner core, they taper to a cuboid, pyramidal or prismatic shape.
[0051] The elastomer body 16 of the camp shown 10 is both on its front sides24a and 24b in axial direction AR and in a radial direction VR Designed without undercuts.
[0052] Fig. Figure 5 shows an exploded view of the warehouse. 10 according to the in Fig. 4 shown structures. The lips 36 of the elastomer body 16 They essentially run in a ring shape around the intermediate ring 30 of the cage 14 and thus around the z-axis of the coordinate system shown. The one in Fig. 5 cages shown 14 It also points approximately at the level of the intermediate ring. 30 radially outwardly projecting knobs or support nubs 50 on, which in the fully assembled state of the bearing 10 into a designated recess or step in the outer sleeve 18 intervene or are deployed and thus serve as support when force is applied to the bearing 10is initiated by the geometry of the elastomer body shown. 16 The damping fluid can flow axially, i.e., along the z-axis, along the outer sleeve. 18 when the bearing is under load 10 flow from one fluid chamber to the other fluid chamber by forming the lips 36 happened.
[0053] Fig. Figure 6 shows a similar setup of the warehouse. 10 as in the Fig. 4 and Fig. 5 shown. The camp 10 is like in Fig. 3 shown on a shock absorber 42 mounted and into a flange 44 pressed in. The mounting washer 11 is in the radial edge region that is connected to the inner core 12 is overmolded, angled, hook-shaped, or L-shaped. A difference from the one in Fig. 4 and Fig. 5 embodiment of the bearing 10 is that the lower membrane 38a of the elastomer body 16is designed as a support spring and the cage 14 no intermediate ring 30 exhibits. The lips 36 of the elastomer body 16 essentially jump from the inner core 12 in a radial direction outwards.
[0054] Similar to Fig. 3 is the one in Fig. 6 elastomer bodies shown 16 designed in such a way that on the axial end faces 24a and 24b of the elastomer body 16 There is essentially no undercut. In the radial direction VR The elastomer body appears 16 in the area of the lips 36 not completely free of undercuts. The apparent undercut can occur because the bearing 10 in the mounted state shown, into the flange 44 is pressed in. The pressing process deforms the easily deformable and vibrating lips. 36 of the elastomer body 16, so that it appears that the elastomer body 16 is not free of undercuts in the radial direction. In the unloaded state of the bearing. 10 after the production of the bearing 10 can the elastomer body 16 However, it must be completely free of undercuts. Alternatively, the elastomer body can be 16 but also with a slight degree of undercut in the radial direction VR in the area of the lips 36 can be produced because the elastomer body 16 during manufacturing in the radial direction VR due to the slight malleability of the lips 36 nevertheless, it can be easily demolded or a slide can be pulled out in a radial direction. VR which is easily possible during production. The lips 36 They can, for example, be bent or curved radially outwards and axially. Essentially, the elastomer body is... 16nevertheless in a radial direction VR undercut-free, as there is only a slight undercut in the area of the easily deformable lips. 36 is available.
[0055] Fig. Figure 7 shows a perspective view of the composite warehouse. 10 according to the in Fig. 6 shown embodiment, but without outer sleeve 18 As part of this registration, the camp 10 without outer sleeve 18 as a bearing component unit 46 designated.
[0056] The depicted bearing component unit 46 is in an unaffected state. The lips 36 They exhibit a slight curvature. Fig. Figure 7 therefore shows the one described in the explanations for Fig. 6 mentioned case, in which the elastomer body 16 a slight degree of undercut in the radial direction due to the curvature of the lips 36 exhibits the elastomer body 16in a radial direction, but is essentially free of undercuts, since the lips 36 easily deformable and the elastomer body 16 thus simply in a radial direction VR can be demolded.
[0057] Fig. Figure 8 shows another embodiment of the bearing. 10 . Fig. Figure 8 shows a similar setup of the bearing. 10 in cross-section as in the Fig. 3 and Fig. 6 shown. The camp 10 is like in Fig. 3 shown on a shock absorber 42 mounted and into a flange 44 pressed in. The mounting washer 11 is in the radial edge region that is connected to the inner core 12 The overmolded part is angled, hook-shaped, or L-shaped. The lower membrane 38a of the elastomer body 16 It is designed here as a supporting spring. Furthermore, the lower diaphragm features 38a and the upper membrane 38beach with at least one pyramidal or prismatic bulge 39a and 39b on, which from the lower and upper axial edge of the inner core 12 protrudate. According to this embodiment, the bearing has 10 additionally a multi-part shell element 34 on, which is between the elastomer body 16 and the outer sleeve 18 is arranged. The fluid channel 32 is attached to the shell element 34 formed. The shell element 34 It is made of plastic. Using the support rings. 26a and 26b , which can also be called retaining rings, is the multi-part shell element 34 on the cage 14 attached. In particular, the support rings can 26a and 26b stepped support edges 48a and 48b exhibiting the shell element 34can be arranged and thus spread or clamped in the axial direction between the retaining rings and radially from the inside through the intermediate section 40 of the elastomer body 16 and radially from the outside through the outer sleeve 18 It can be held between the retaining rings. The fluid channel 32 , which is in the shell element 34 It is designed in such a way that the lower fluid chamber 22a and the upper fluid chamber 22b are fluidically connected, i.e., damping fluid can pass through the fluid channel 32 in the shell element 34 from one fluid chamber 22a into the other fluid chamber 22b or conversely, when the bearing is under load 10 flow. The fluid chambers 22a and 22b are each by the elastomer body 16 , the support ring 26a or 26b and the outer sleeve 18 limited.
[0058] The elastomer body 16 is in the radial direction VR as well as in the axial direction AR on its foreheads 24a and 24b Completely free of undercuts.
[0059] Fig. Figure 9 shows a perspective view of the camp. 10 without outer sleeve 18 , i.e. the bearing component unit 46 , according to the as in Fig. The assembly shown in section 8. The bearing component unit 46 is related to the cross-section in Fig. 8 rotated approximately 45° around the z-axis. Reference symbol list 10 Hydraulic bearing 11 Mounting washer 12 inner core 14 Cage 16 elastomer bodies 18 Outer sleeve 20a, 20b Fluid chamber recess 22a, 22b Fluid chamber 24a, 24b axial end face 26a, 26b Support ring 28a, 28b Connecting bridge 30 Intermediate ring 32 Fluid channel 34 shell elements 36 lips 38a, 38b Membran 39a, 39b Bulges 40 Intermediate section 42 shock absorbers 44 flange 46 Bearing component unit 48a, 48b Support edges 50 support studs VR predetermined radial direction AR axial direction QUOTES INCLUDED IN THE DESCRIPTION
[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature
[0000] EP 0458008 B1
[0003]
Claims
[1] Hydraulic bearing (10), comprising: an inner core (12), a cage (14) surrounding the inner core (12), an elastomeric body (16) extending between the inner core (12) and the cage (14) and elastically connecting them, and an outer sleeve (18) that encloses the cage (14), wherein the elastomer body (16) has a first circumferential fluid chamber recess (20a) and a second circumferential fluid chamber recess (20b), wherein the first fluid chamber recess (20a) and the second fluid chamber recess (20b) are each radially outwardly limited by the outer sleeve (18) to form a first fluid chamber (22a) and a second fluid chamber (22b), wherein the elastomer body (16) is essentially free of undercuts in the axial direction (AR) at its axial end faces (24a, 24b), and wherein the elastomer body (16) and the cage (14) are formed in the area of the first fluid chamber recess (20a) and the second fluid chamber recess (20b) in a substantially undercut-free manner in at least two predetermined, mutually opposite radial directions (VR). [2] Hydraulic bearing (10) according to 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 at a first axial end section of the bearing (10), wherein the second support ring (26b) is arranged on a second axial end section of the bearing (10) opposite the first axial end section, and wherein the first fluid chamber (22a) and the second fluid chamber (22b) are arranged in the axial direction (AR) between the first and the second support ring (26a, 26b). [3] Hydraulic bearing (10) according to claim 2, wherein the cage (14) has two connecting webs (28a, 28b) which extend in the axial direction (AR) between the first and the second support ring (26a, 26b) and connect them, and wherein the two connecting webs (28a, 28b) are arranged at two diametrical positions of the first and second support ring (26a, 26b) transverse to the predetermined, mutually opposite radial directions (VR). [4] Hydraulic bearing (10) according to claim 3, wherein the cage (14) has an intermediate ring (30) which is arranged in the axial direction (AR) between the first and the second support ring (26a, 26b) and is connected to the first and the second support ring (26a, 26b) via the two connecting webs (28a, 28b). [5] Hydraulic bearing (10) according to any one of the preceding claims, wherein the first and second fluid chambers (22a, 22b) are fluidically connected to each other via a fluid channel (32), and wherein the fluid channel (32) is limited radially outwards by the outer sleeve (18). [6] 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 the intermediate ring (30). [7] Hydraulic bearing (10) according to claim 5, further comprising a multi-part shell element (34) which is arranged between the elastomer body (16) and the outer sleeve (18), wherein the fluid channel (32) is formed on the shell element (34). [8] Hydraulic bearing (10) according to claim 5, wherein the fluid channel (32) is formed on the elastomer body (16) between the first fluid chamber recess (20a) and the second fluid chamber recess (22b), wherein the elastomer body (16) in the region of the fluid channel (32) has at least one substantially radially outwardly projecting lip (36) which extends along a circumferential direction of the elastomer body (16). [9] Hydraulic bearing (10) according to claim 8, wherein the elastomer body (16) is supported radially from the inside in the area of the fluid channel (32) by the inner core (12) or the intermediate ring (30). [10] Hydraulic bearing (10) according to any one of the preceding claims, wherein the elastomer body (16) comprises a first membrane (38a), a second membrane (38b) and an intermediate section (40), wherein the first fluid chamber (22a) is bounded axially outwards by the first membrane (38a), wherein the second fluid chamber (22b) is bounded axially outwards by the second membrane (38b), and wherein the intermediate section (40) is arranged in the axial direction (AR) between the first fluid chamber (22a) and the second fluid chamber (22b). [11] Hydraulic bearing (10) according to claim 10, wherein the first diaphragm (38a) and / or the second diaphragm (38b) are convex. [12] Hydraulic bearing (10) according to claim 10 or 11, wherein the first diaphragm (38a), the second diaphragm (38b) and / or the intermediate section (40) is designed as a support spring. [13] Method for manufacturing a hydraulic bearing (10) wherein the method comprises the following steps: Inserting an inner core (12) into a tool, Inserting a cage (14) into the tool such that the cage (14) surrounds the inner core (12), Closing the tool, Inserting at least one axial slide into the tool, Introducing at least one pair of radial slides into the tool, Injecting an elastomer material into the tool, Vulcanizing the elastomer material to form an elastomer body (16) which elastically connects the inner core (12) and the cage (14), and to form a bearing component unit (46), wherein the bearing component unit (46) comprises the inner core (12), the elastomer body (16) and the cage (14), Pulling out at least one axial slide and at least one pair of radial slides, Opening the tool, Demolding of the bearing component unit (46) from the tool, and Connecting the bearing component unit (46) to an outer sleeve (18).