Multidirectional damping hydraulic mount

Abstract

Hydraulically damping bearing (1), comprising - an axially extending inner element, - an elastomer body (3), - a cage element which is embedded at least partially in the elastomer body (3), wherein the elastomer body (3) elastically connects the cage element and the inner element; - an outer sleeve (5) encompassing the inner element, the cage element and the elastomer body (3) - at least a first and a second fluid chamber (6a, 6b, 7a, 7b) arranged between the outer sleeve and the inner element, which are connected via a fluid channel, comprising at least a third and a fourth fluid chamber, each arranged between the outer sleeve and the inner element, and the at least four fluid chambers being connected via at least one further fluid channel, wherein each of the at least four fluid chambers (6a, 6b, 7a, 7b) participates in performing damping work during a relative displacement of the inner element and the cage element in a first direction and during a relative displacement of the inner element and the cage element in a second direction, characterized in that an annular stop element (23a, 23b) is arranged axially outside the fluid chambers (6a, 6b, 7a, 7b) on the inner element at an axial end section of the bearing (1),which, in the unloaded state of the bearing (1), is located radially spaced from an elastomer section arranged on an inner surface of one of the ring elements of the cage.

Description

[0001] The invention relates to a hydraulically damping bearing comprising an axially extending inner element, an elastomer body and a cage element which is embedded at least partially in the elastomer body, wherein the elastomer body elastically connects the cage element and the inner element and an outer sleeve encompassing the inner element, the cage element and the elastomer body, wherein at least a first and a second fluid chambers are provided, each arranged between the outer sleeve and the inner element, which are connected via a fluid channel.

[0002] Such bearings are used, for example, as bushing bearings for mounting control arms of a chassis suspension or for mounting components, particularly engines in motor vehicles. To provide improved damping, especially during the operation of such motor vehicles within specific excitation frequency or amplitude ranges, compared to that achievable with pure elastomer damping, such a bearing is designed to perform hydraulic damping work in response to corresponding mechanical excitations. For this purpose, the at least two fluid chambers, connected by a fluid channel, are designed such that when the cage element is mechanically deflected relative to the inner element, the volume of one fluid chamber can decrease, while the volume of another fluid chamber associated with the first can increase, thus allowing fluid exchange between the chambers.Preferably, the fluid can be designed as a damping fluid. The fluid flows through the at least one fluid channel between the interconnected fluid chambers, thereby performing hydraulic damping work. The at least two fluid chambers connected by a damping channel can be partially delimited by at least one inflating spring section and / or at least one support spring section. Mechanical stress on the bearing, also referred to as a hydraulic bearing, causes damping fluid to flow from one chamber to the other via the at least one damping channel and / or an associated inflating spring section to expand. Such a hydraulic bearing is disclosed, for example, in German patent application DE 10 2019 007 526 A1.

[0003] Depending on the application, it may be advantageous to design a hydraulic bearing not only with respect to a single working or main damping direction, in which hydraulic damping is provided in response to mechanical excitations of specified excitation frequencies or amplitude ranges, but also in several, for example, two excitation directions, which may be arranged perpendicular to each other. DE 10 2007 016 399 A1 describes a multidirectional damping hydraulic bearing designed and configured to perform damping work in both an axial and a radial direction of the bearing. For this purpose, the known hydraulic bearing comprises a housing with an upper housing part and a lower housing part connected to the upper housing part, as well as an axially and radially acting elastomeric damping arrangement received by the housing.This damping arrangement comprises at least one pair of axially arranged chambers, connected by at least one channel and extending the entire circumference, as well as at least one pair of radially arranged chambers, distributed along the circumference of the hydraulic bearing and connected by at least one channel, for a hydraulic damping medium. The upper housing part forms a support body comprising an inner core, an outer wall of the upper housing part spaced radially from the inner core, and an elastomeric spring, bonded to the inner core and the outer wall by vulcanization and supporting the inner core axially against the outer wall.

[0004] Generic, hydraulically damping bearings are disclosed in German patent application DE 10 2013 209 990 A1 and in patents US 5 172 893 A and US 6 386 529 B2.

[0005] The design of a multidirectional damping hydraulic bearing is very complex and requires a large number of components, so there is a need to provide a hydraulic bearing that is able to perform hydraulic damping work in several working directions, which can be oriented perpendicular to each other, as well as to ensure the operation of the bearing even under high radial operating forces, and at the same time has a simple design and is therefore cost-effective to manufacture.

[0006] The present invention solves this problem with a hydraulically damping bearing having the features of claim 1.

[0007] The bearing according to the invention comprises an axially extending inner element, an elastomer body, a cage element which is embedded at least partially in the elastomer body, wherein the elastomer body elastically connects the cage element and the inner element, an outer sleeve encompassing or radially surrounding the inner element, the cage element and the elastomer body, and at least one first and one second fluid chambers, each arranged between the outer sleeve and the inner element and connected via a fluid channel.The bearing according to the invention comprises, in addition to the first and second fluid chambers, at least a third and a fourth fluid chamber, each arranged between the outer sleeve and the inner element, wherein the at least four fluid chambers are fluidly connected via at least one further fluid channel, and wherein each of the at least four fluid chambers participates in the performance of damping work during a relative displacement of the inner element and the cage element in a first principal direction and during a relative displacement of the inner element and the cage element in a second principal direction, i.e., each of the at least four fluid chambers is part of a hydraulic system in which hydraulic damping work can be performed both during a relative displacement of the inner element and the cage element in a first principal direction and during a relative displacement of the inner element and the cage element in a second principal direction.Preferably, the two main directions can be oriented perpendicular to each other, in particular an axial direction and a radial direction. In order to protect the multidirectional damping hydro bearing according to the invention against undesired force effects on elastomeric chamber wall sections of the fluid chambers under increased radial operating forces, the bearing according to the invention further comprises an annular stop element on an axial end section of the bearing, axially outside the fluid chambers on the inner element, which, in the unloaded state of the bearing, is arranged radially spaced from an elastomeric section arranged on an inner surface of an annular element of the cage element.

[0008] The invention is based on the fundamental idea of ​​designing a multidirectional damping hydraulic mount based on a known uniaxial damping hydraulic mount comprising a cage element embedded in the elastomer body, wherein, according to the invention, at least four fluid chambers are provided which are connected via fluid channels and which each of the at least four fluid chambers participates in performing hydraulic damping work, regardless of whether the hydraulic mount is loaded in a first or second direction or main direction. Such participation in performing damping work can, in particular, consist of damping fluid, especially a damping liquid, flowing out of or into a fluid chamber via an associated fluid channel, wherein hydraulic damping work can be performed essentially in the fluid channel that connects a fluid-discharging fluid chamber and a fluid-receiving fluid chamber.

[0009] The hydraulically damping bearing according to the invention, with its described design, is characterized by the fact that it provides a multidirectional damping bearing that comprises a comparatively small number of components, enables a compact design, and, moreover, allows for different damping characteristics of the bearing in two main load directions. According to the invention, the at least four fluid chambers, together with the fluid channels, are each configured to provide a hydraulic system acting and performing damping work in the first direction and a hydraulic system acting and performing damping work in the second direction. Preferably, the two main directions can be perpendicular to each other; in particular, the first main direction can represent an axial direction of the bearing and the second main direction a radial direction of the bearing.In this embodiment, the at least four fluid chambers can each be designed and configured in such a way that they act as fluid chambers of a damping system both under a radial bearing load and under an axial bearing load, cooperating with an associated fluid chamber of the other fluid chambers and a fluid channel connecting the two associated fluid chambers to perform damping work.

[0010] Further features and developments of the invention are specified in the following general description, the figures, the figure description and the dependent claims.

[0011] To provide a hydraulic bearing that operates in two directions, particularly in the main directions, the bearing according to the invention can be configured to have at least two pairs of fluid chambers arranged axially one above the other and overlapping at least in the circumferential direction of the bearing, wherein the at least two pairs are spaced apart from each other circumferentially. Preferably, the circumferential spacing of the two pairs of axially arranged fluid chambers can be between 90° and 180°, with both extremes of the circumferential spacing, i.e., 90° or 180°, being particularly possible. It can be especially advantageous to arrange the two pairs of axially arranged fluid chambers radially opposite each other, i.e., diametrically opposite each other, corresponding to a circumferential spacing of approximately 180°.

[0012] Depending on the embodiment, the two pairs of axially stacked fluid chambers can be arranged at different axial heights within the bearing. It can be particularly advantageous to arrange the two pairs of axially stacked fluid chambers at the same axial height. The latter can result in a radial section, in particular a radial wall section of the bearing, which separates one pair of axially stacked fluid chambers, being at the same height as a radial section of the bearing that separates the other pair of axially stacked fluid chambers.

[0013] The multidirectional hydraulically damping bearing according to the invention can, in particular, be designed as a bushing bearing for arrangement in an associated bearing eye of a first component, for example, a motor vehicle component, wherein the outer surface of the outer sleeve of the bearing is designed to abut a boundary surface of the first component that defines the bearing eye and is adapted to the surface of the outer sleeve, and the inner element is designed for fastening to a second component, in particular a second component of the motor vehicle. It can be provided that the inner element of the bearing according to the invention has a through-passage extending in the axial direction for receiving a fastening bolt for fastening the bearing according to the invention to the aforementioned second component of the motor vehicle.

[0014] To provide a symmetrical response behavior of the multidirectional damping hydraulic bearing according to the invention, it can be advantageously provided that the two fluid chambers of a respective pair of axially arranged fluid chambers extend essentially over the same circumferential section.

[0015] Preferably, the at least four fluid chambers can have substantially the same extent, i.e., an identical extent in the circumferential direction of the bearing. In particular, it can be provided that two fluid chambers are arranged on the same circumferential section and axially offset, forming a first and second pair of fluid chambers, with the two pairs of fluid chambers being arranged circumferentially offset by approximately 180°.

[0016] To minimize design effort, each of the at least four fluid chambers can be fluidly connected to one of the other three fluid chambers via a fluid channel, with the interconnected fluid chambers arranged radially opposite each other and axially consecutive, i.e., one above the other. In this embodiment, each fluid chamber can have a single associated fluid chamber for exchanging damping fluid and thus a single damping channel between associated fluid chambers, so that the damping is set, for example, under both radial and axial loads with an essentially identical hydraulic damping system, since the respective damping channel or fluid channel is identical for both main load directions.

[0017] Preferably, it can be provided that each fluid channel connects exactly two of the fluid chambers encompassed by the bearing according to the invention.

[0018] To separately adjust the hydraulic damping of the bearing according to the invention in different directions, it is advantageous to provide four fluid channels between each of the at least four fluid chambers. It can be provided that two fluid channels are arranged between the at least four fluid chambers to provide damping work in a first principal direction, for example in the axial direction, and two fluid channels are arranged between the at least four fluid chambers to provide damping work in a second principal direction, for example in the radial direction.

[0019] Preferably, the fluid channels for providing damping in the first principal direction (e.g., in the radial direction) and the fluid channels for providing damping in the second principal direction (e.g., in the axial direction) can be geometrically different to define the respective damping, particularly with regard to diameter, length, and / or curvature of the respective fluid channel. In this respect, the design of the hydraulic bearing according to the invention can be such that when a load occurs on the bearing in one of the principal directions, two hydraulic systems, each comprising associated fluid chambers connected via an associated fluid channel, are always active, i.e., performing damping work.

[0020] It can be provided that each of the at least four fluid chambers is fluidly connected to an associated axially spaced first fluid chamber by means of a fluid channel, and simultaneously the first fluid chamber is connected to a circumferentially spaced second fluid chamber via another fluid channel. Advantageously, this allows the hydraulic bearing according to the invention to provide two hydraulic systems for simultaneously performing damping work under any mechanical load that leads to a relative displacement of the inner element and the cage element of the bearing. These two hydraulic systems can be provided regardless of whether the mechanical load on the hydraulic bearing acts in one of the two main directions, which are perpendicular to each other and, for example,can be an axial direction and a radial direction, or cause both a load component of the bearing in the first principal direction and a load component of the bearing in the second principal direction, wherein the two damping systems are set up to perform damping work with the participation of all four fluid chambers and with the participation of the fluid channels connecting them.

[0021] To separate two fluid chambers arranged in the same circumferential section and axially spaced or consecutive, and referred to above as a pair, the cage element may advantageously have a first transverse web, which may also be called a radial web, extending radially towards the inner element in the longitudinal section of the bearing. This transverse web may be designed to provide a respective axial pumping surface for the two axially consecutive fluid chambers arranged over a predetermined circumferential section. Preferably, this first radial or transverse web may engage with or originate from radially or diametrically opposite longitudinal webs of the cage element. It should be noted that such a transverse or radial web may be covered with elastomeric material to define a respective interface between the two axially adjacent orsuccessive fluid chambers that can form a pair of axially adjacent fluid chambers.

[0022] To provide a further pair of axially successive or adjacent fluid chambers, it is advantageous to provide a second transverse or radial web of the cage element in the longitudinal section of the bearing, preferably radially opposite the first transverse or radial web. This second transverse or radial web extends radially towards the inner element, like the first, and also serves to provide an axial pumping surface for the two other axially successive fluid chambers arranged over a predetermined circumferential section, i.e., a second pair of axially successive fluid chambers. Preferably, the two transverse or radial webs are arranged at approximately the same axial height of the bearing. Furthermore, the second transverse or radial web also extends to the diametrically opposite longitudinal webs of the cage element, to which the second transverse or radial web is also attached.The radial web is attached to the cage element.

[0023] Advantageously, one of the two transverse webs, and in particular both transverse webs, may have a fork-like split in the area of ​​its transition into a respective longitudinal web of the cage element, with two axially spaced and axially opposing extensions that merge into the associated longitudinal web of the cage element or may be integrally formed with it. To achieve low radial stiffness of the hydro bearing according to the invention in a predetermined circumferential range, it may advantageously be provided that the respective transverse web or radial web runs axially spaced from the inner element between the extensions or attachments on the longitudinal webs of the cage element.It can be provided that two opposing and angled inner elastomeric chamber wall sections extend from the radial end section of the respective transverse web facing the inner element, thus axially separating the two axially successive fluid chambers. Preferably, the two elastomeric chamber wall sections are axially spaced apart from each other. To achieve particularly low radial stiffness of the bearing, a cavity formed between the two chamber wall sections and the inner element is filled with a gas medium, in particular air, to provide clearance for the elastically deformable elastomeric chamber wall sections.

[0024] Advantageously, the cage element of the hydraulic bearing designed according to the invention can have at least two axially spaced ring sections connected by at least two, in particular diametrically opposed, longitudinal webs, wherein the first and / or the second transverse web can each be connected with its longitudinal ends to both longitudinal webs of the cage element, as described above, and in particular can be integrally formed with them. Depending on the embodiment, the cage element can be formed in one piece or in multiple pieces.

[0025] Advantageously, the cage element can be designed in two parts, with corresponding contact surfaces extending along diametrically opposed or circumferentially spaced longitudinal webs. Preferably, the two parts of such a cage element can have complementary connecting elements in the area of ​​their contact surfaces, in particular those that can be engaged axially and provide positive locking sections acting radially.

[0026] Advantageously, the elastomer body can have support spring sections arranged radially between the longitudinal webs of the cage element and the inner element of the hydro bearing according to the invention. Due to the diametrical arrangement of the two longitudinal webs of the cage element in a predetermined radial direction of the bearing, these support spring sections enable high radial stiffness of the bearing. In contrast, the elastomer body can comprise two cavities, for example filled with air, extending transversely to the longitudinal direction of the inner element, in particular in a straight line and parallel to each other, and bounded by elastomeric wall sections. These cavities adjoin the inner element, thereby providing a comparatively low radial stiffness relative to the support spring section, offset in a radial direction, in particular by 90 degrees, to the diametrically opposite longitudinal webs of the cage element.It may be provided that these elastomeric wall sections are identical to the axially opposing and angled inner elastomeric chamber wall sections described above, extending from the radial end section of the respective crossbar facing the inner element.

[0027] In particular, to provide radially acting pumping surfaces for the at least four fluid chambers and to provide the fluid channels, the multidirectional damping hydraulic bearing according to the invention can have, for example, a two-part channel shell which is arranged axially between the ring sections of the cage element and closes off the fluid chambers to the outer sleeve, and can have radial grooves to provide at least two, in particular at least four, fluid channels, which can be formed at least partially by the radial grooves of the channel shell and associated inner wall sections of the outer sleeve.

[0028] Depending on the number of fluid channels emanating from a fluid chamber, the specified radial recesses can be designed differently. In embodiments where only two fluid channels are formed between the at least four fluid chambers, the two channel halves of a two-part channel shell each have radial grooves for the partial formation of the two fluid channels. In an embodiment where four fluid channels are provided for fluidly connecting the four fluid chambers, each of the two channel halves can form a complete fluid channel or a radial groove associated with a complete fluid channel to provide a fluid connection between a pair of axially adjacent orThe channel halves have spaced-apart fluid chambers and, furthermore, two radial, in particular axially spaced and circumferentially extending groove sections which, in the assembled state of the two channel halves, correspond to two radial grooves of the other channel half and merge into one another to provide two fluid channels for forming a fluid connection between each pair of circumferentially spaced fluid chambers. To provide a fluid connection between each radial groove and the two associated fluid chambers, the radial grooves can each have a radial opening or passage through the respective half-shell at their longitudinal ends or at one of their longitudinal ends.

[0029] To increase the stability of the hydraulic bearing according to the invention against external operating forces, it can advantageously be provided that the channel shell has a radial passage in the form of a receptacle into which, in the assembled state of the bearing, a radially extending section of a transverse web of the cage element extends, which, as described above, separates the two axially spaced fluid chambers of a pair of fluid chambers.

[0030] Advantageously, the inner element of the hydro bearing according to the invention may have an approximately rectangular cross-section in an axial section over which the fluid chambers extend. This design of the inner element allows, on the one hand, a simple design of support spring sections on opposite sides of the approximately rectangular cross-section of the inner element and, on the other two sides of the rectangular cross-section, the provision of elastomeric chamber wall sections extending from the respective radial end section of a transverse web facing the inner element to the inner element. These sections separate the axially adjacent fluid chambers and provide the described low radial stiffness of the bearing in a direction approximately perpendicular to the two aforementioned side faces of the rectangular cross-section within the axial extent of the fluid chambers of the bearing.The aforementioned comparatively high radial stiffness of the bearing can thus be provided approximately perpendicular to the diametrically opposite side surfaces of the inner element, on which spring sections of the elastomer body are arranged.

[0031] To provide an inner surface for an outer elastomeric chamber membrane wall and to increase axially effective pumping areas, it is advantageous for the inner element to have a collar-like flange. Preferably, the inner element may include such a collar-like flange at both axial end sections of the fluid chambers of a pair of fluid chambers. Depending on the embodiment, this flange may be circular; however, particularly in an embodiment where the inner element has an approximately rectangular cross-section in the axial section of the fluid chambers, it is also possible to design this collar-like flange as a square.

[0032] The inner element can be made of a plastic or metal material, for example. However, it is also possible for the inner element to comprise a metal core with an attached, particularly injection-molded, plastic shell, which defines at least the overall shape of the inner element in sections.

[0033] The outer sleeve can be made of a plastic material or a metal material, such as aluminum or steel. The same applies to the cage element and the channel shell; preferably, these can be made of a plastic material, in particular a fiber-reinforced plastic material.

[0034] As explained at the outset, the invention provides that an annular stop element is arranged axially outside the fluid chambers on the inner element at an axial end section of the bearing. In the bearing's unloaded state, this stop element is radially spaced from an elastomer section provided on an inner surface of a ring element of the cage element. This is intended to protect the multidirectional damping hydraulic bearing according to the invention against undesired forces acting on the elastomeric chamber wall sections of the fluid chambers under increased radial operating forces. Furthermore, radial circumferential sections of the stop element can be configured to contact associated elastomer sections of the cage's ring element under increased radial mechanical load, thereby preventing further relative movement of the inner element to the cage element or to the outer sleeve of the bearing.In this respect, a radial limitation of the displacement of the inner element and cage element can be provided. Advantageously, the elastomer section of the ring element that interacts with the stop element can be designed as an axial extension of an outer chamber membrane wall. In one embodiment, the annular stop element can also be formed integrally with the inner element.

[0035] Preferably, the multidirectional damping hydraulic bearing according to the invention can also be protected against excessive axial displacement of the inner element and cage element or outer sleeve. For this purpose, an axial end face of the cage can be covered with an elastomer buffer located axially below an end face of the inner element, so that when the end face of the inner element rests against a contact surface of another component extending radially beyond the inner element in an installed position of the bearing, any relative displacement of the inner element and cage element or outer sleeve is limited to the projection of the end face of the inner element relative to the associated contact surface of the elastomer buffer on the axial end face of the cage.

[0036] The invention is explained below by describing an embodiment of the multidirectional damping hydraulic bearing according to the invention, including modifications, with reference to the accompanying drawings, wherein Fig. 1: a multidirectional damping hydro bearing according to the invention in a perspective half-section view with two mutually perpendicular section planes; Fig. 2: the inner element of the hydro bearing according to the invention Fig. 1 in a perspective view; Fig. 3: the cage element of the hydro bearing according to the invention Fig. 1 in a perspective view Fig. 4: one of the two channel half-shells of the hydro bearing according to the invention Fig. 1 Fig. 5: the in Fig. 1 hydraulic bearing shown in a (partial) exploded view; Fig. 6: the in Fig. 1 hydraulic bearings shown in a first full-section view, and Fig. 7: the hydraulic bearing of the Fig. 1 in a second full-section view shows.

[0037] The invention is explained below using an example of a multidirectional hydraulically damping bearing, such as can be used for mounting components in the automotive sector, in particular for mounting the engine within the vehicle body. Fig. Figure 1 shows the inventive, multidirectionally hydraulically damping bearing in a perspective half-section view with two section planes, both parallel to the bearing axis A and perpendicular to each other. The hydraulic bearing 1 is designed as a bushing bearing with an inner element 2, which in the described embodiment may have a bore 20 for receiving a fastening bolt for attachment to a first component of a motor vehicle. The hydraulic bearing 1 is radially closed over a predominant portion of its axial extent by an outer sleeve 5, which, in the installed position, is pressed against a boundary surface of a bearing eye receiving the hydraulic bearing 1, for example by press-fitting, with its outer surface 50, which may be cylindrical in the standard form.These boundary surfaces can be designed as part of a second KFT component, so that the hydro bearing 1 according to the invention can be designed to support the two KFT components mentioned.

[0038] The bearing has an elastomer body arranged between the inner element 2 and the outer sleeve 5, which in the described embodiment can have two diametrically opposed support spring sections 31a, 31b, of which only the support spring section 31a, extending substantially over the entire axial extent of the bearing, is visible in the described illustration. Both support spring sections 31a, 31b can be identical in design.

[0039] Approximately 90° to the diametrical arrangement of the support spring sections 31a, 31b, two axially consecutive or axially adjacent fluid chamber pairs 6a, 6b; 7a, 7b can be arranged diametrically opposite each other, of which, in turn, based on the described representation of the Fig. 1. Only the fluid chambers 6a, 6b are visible as a chamber pair. To form these fluid chambers 6a, 6b, 7a, 7b, the hydro bearing 1 according to the invention has a cage element, which is explained in more detail below and which is embedded at least partially in the elastomer body, so that the elastomer body connects the cage element and the inner element 2. For example, it can be provided that the inner element 2 and cage element are elastically connected to each other by means of a plurality of elastomer sections, such as the described support spring sections 31a, 31b and chamber wall sections for delimiting the respective fluid chambers 6a, 6b, 7a, 7b, via an electroplating process through the described elastomer sections.

[0040] In the presentation of the Fig. In Figure 1, two axially superimposed fluid chambers 6a, 6b are designated, which are separated in the horizontal direction by a transverse web 44, wherein the transverse web 44, which extends substantially perpendicular to a bearing axis A of the inner element 2, is spaced apart from the inner element 2. Two axially opposing and angled inner elastomeric chamber wall sections 33a, 33b extend from the radial end section of the transverse web 44 to the outer surface of the inner element 2 and adhere to it, thereby forming a cavity between the two chamber wall sections 33a, 33b and an outer surface of the inner element 2. Both inner chamber wall sections 33a, 33b are also arranged in an adhering manner to the aforementioned radial end section of the transverse web 44 of the cage element. In the axial direction, the Fig. 1 visible fluid chambers 6a, 6b arranged axially one above the other and in the same circumferential section of the bearing are closed off by chamber wall sections 35a, 35b acting as inflating membrane sections, which in turn are arranged adhering to the inner element 2 and to the cage element and thus extend radially between them.

[0041] In the described embodiment, a further pair of axially spaced fluid chambers 7a, 7b, not visible in the figure, can be formed diametrically opposite the two fluid chambers 6a, 6b. These can be designed and arranged in the same way as the fluid chambers 6a, 6b described above. The two pairs of hydraulic bearings or fluid chambers 6a, 6b and 7a, 7b do not extend completely around the core, i.e., the inner element 2 of the hydraulic bearing 1 according to the invention, but rather over a predetermined circumferential section and are each separated circumferentially by means of a support spring section 31a, 31b of the hydraulic bearing 1.

[0042] The hydro bearing 1 according to the invention can have a ring plate 9 on an axial end face, which is stepped and provides contact surfaces for associated end faces of the inner element 2 and the cage element or the elastomer body.

[0043] The in Fig. The hydro bearing 1 shown in Figure 1 according to the invention is designed to perform damping work in two mutually perpendicular main working directions, "radial / axial," whereby the response behavior of the hydro bearing 1 can be configured to be highly dependent. The damping behavior is determined, firstly, by the arrangement of the elastomer sections of the elastomer body and, secondly, by the arrangement of the fluid chambers 6a, 6b, 7a, 7b, which are fluid-connected via fluid channels. A first main working direction relates to a relative displacement of the inner element 2 and the cage element in the direction of the bearing axis A of the hydro bearing 1; a second main working direction relates to a relative radial displacement of the inner element 2 towards the cage element, whereby the response behavior in the radial direction is described in Figure 1. Fig. The intersecting planes specified in section 1, which are oriented perpendicular to each other, can themselves be designed very differently. While the hydro bearing 1, under radial loads within the area specified in Fig. The hydro bearing 1 of the [unclear text] shows that the plane shown in 1, which includes the support spring section 31a and the diametrically opposite support spring section 31b (not visible in the illustration), has high radial stiffness. Fig. 1 in the case of a radial deflection, i.e. a displacement of the inner element 2 towards the cage element in the Fig. The section plane shown in Figure 1, which includes the cross web 44 with the chamber wall sections 33a, 33b extending from its ends towards the inner element 2, exhibits low radial stiffness, which is essentially determined by the specified elastomeric chamber walls 35a, 35b and 33a, 33b as well as the damping behavior of the fluid-connected pairs of elastomeric fluid chambers 6a, 6b and 7a, 7b. The operation of the inventive, multidirectionally hydraulically damping hydro-mount 1 is discussed below, after the basic structure of the hydro-mount 1 has been explained in more detail with reference to individual components.

[0044] Fig. Figure 2 shows a perspective view of the inner element 2 for the design of the hydraulic bearing 1 according to the invention. In the described embodiment, the hydraulic bearing 1 has an inner core section 21 and an outer section 22, the latter essentially providing the outer boundary surface, at least over the predominant part of the axial extent of the inner element 2. The core section 21 can be made of a metallic material, for example aluminum or steel, and the outer section 22 can consist of an injection-molded section 26 onto the core section 21, for example comprising a plastic material, which is metallurgically bonded to the core section 21.

[0045] As from Fig. As can be seen in Figure 2, the inner element 2 can have an approximately rectangular interface in an axial section, with two opposing, approximately parallel side surfaces 24a, 24b and 25a, 25b. In the described embodiment, the two interface surfaces 24a, 24b can be fully assigned to a respective pair of fluid chambers 6a, 6b and 7a, 7b, or essentially define their extent perpendicular to the bearing axis A. Similarly, the opposing side surfaces 25a, 25b can be assigned to or define a respective extent perpendicular to the bearing axis A of the hydraulic bearing 1 of the support spring sections 31, 31b. The essentially planar orThe slightly curved side surfaces 24a, 24b associated with the fluid chambers 6a, 6b, 7a, 7b can have flange collars 26a, 26b extending radially outwards at least at one longitudinal end, or, as in the described embodiment, at both longitudinal ends. These flange collars serve, in a manner to be described later, as axial pumping surfaces and / or as coupling sections for the chamber walls 35a, 35b that close off the respective fluid chamber 6a, 6b, 7a, 7b in the hydro bearing 1 according to the invention. In a modified embodiment, the flange collars 26a, 26b can also be fully closed and / or annular around the core section 21 of the inner element 2.

[0046] Fig. Figure 3 shows an exemplary construction of the cage element of the multidirectional hydraulically damping bearing 1 according to the invention in a perspective view. In this embodiment, the cage element 4 has two axially spaced ring sections 40a, 40b, which are connected to each other by means of two radially and diametrically opposed longitudinal webs 42a, 42b. The longitudinal webs 42a, 42b have curved thickenings 421a, 421b extending radially inwards towards the axial center, on which the bearings are attached. Fig. 1. The supporting spring sections 31a, 31b can be arranged to adhere to the inner element 2, which in turn can adhere radially inside to the inner element 2, whereby the inner element 2 and the cage element 4 are elastically connected to each other in the finished hydro bearing 1.

[0047] In the described embodiment, diametrically opposed transverse webs 44, 45 can be integrally formed and arranged with the two radial thickenings 421a, 421b of the longitudinal webs 42a, 42b and connect them to one another. The coupling of the transverse webs 44, 45 to the respective radial thickenings 421a, 421b can be effected via associated fork arms 442a, 442b and 452a, 452b, which extend from an axial end face of the respective transverse web 44, 45 and fork out to an associated longitudinal web 42a, 42b, forming a respective fork opening 443, 453. As a comparison of the Fig. 1 and Fig. As shown in Figure 3, the crossbars 44, 45 form respective partition wall sections for the respective pair of axially spaced fluid chambers 6a, 6b and 7a, 7b. In the described embodiment, the fork arms 442, 442b and 452a, 452b can serve as pivot surfaces for the elastomeric chamber wall sections 33a, 33b and 34a, 34b, which extend along the longitudinal extent of the crossbars 44, 45 between the longitudinal bars 42a, 42b (see also Figure 3). Fig. 1.

[0048] While the transverse webs 44, 45 have an approximately straight course on their end face facing the inner element between the longitudinal webs 42a, 42b, on which the elastomeric chamber walls 33a, 33b and 34a, 34b attack axially spaced and in opposite directions, the transverse webs 44, 45 have a respective radial projection 441, 451 on their end face facing away from the inner element 2, which extends radially into a respective channel shell 80a, 80b in a manner to be described below for the described separation of the two axially superimposed fluid chamber pairs 6a, 6b and 7a, 7b separated by the transverse webs 44, 45.

[0049] In the described embodiment, the channel shell 8, which is designed to radially delimit the fluid chambers 6a, 6b and 7a, 7b to the outer sleeve 5 and to provide fluid channels between the fluid chambers 6a, 6b and 7a, 7b and thus to provide a fluid exchange between the fluid chambers 6a, 6b, 7a, 7b, can be designed in two parts in the described embodiment. Fig. Figure 4 shows such a channel half-shell 80a in a perspective view looking towards the outer surface 81a in the installed position facing the outer sleeve 5, whereby the channel half-shell 82b, not shown, can be designed accordingly. The in Fig. 4 The channel half-shell 80a shown has a through-hole 83a approximately axially centered over a predetermined circumferential section, which can be, for example, between 30° and 110°, for receiving an associated radial projection 441 of the cross web 44, see Fig. 3. In this respect, this implementation 83a marks the separation of the two axially superimposed fluid chambers 6a, 6b, see Fig. 1.

[0050] In the described embodiment, each of the channel half-shells 80a, 80b, which is assigned to a pair of axially superimposed fluid chambers 6a, 6b and 7a, 7b respectively and radially delimits these chambers, can have two channel or radial feedthroughs 8011, 8021 and 8012 and 8031 ​​respectively for each of the fluid chambers 6a, 6b and 7a, 7b, which open into associated channel grooves 801, 802 and 803. These channel grooves 801a, 802a, 803a provide fluid channels assigned to associated sections of the inner surface of the outer sleeve 5, through which fluid can be exchanged between the fluid chambers 6a, 6b and 7a, 7b. For example, while the channel groove 801a with the associated radial feedthroughs 8011a and 8012a connects two fluid chambers 6a, 6b arranged one above the other and circumferentially over the same section or overlapping, the fluid flow in the installed position of the channel half-shells is achieved via the Fig. 4 upper channel groove 802a and a channel groove 802b aligned with it of the second channel half-shell 82b form a fluid connection between two diametrically opposed fluid chambers 6a and 7a. The same applies accordingly to two with respect to the representation of the Fig. Four lower fluid chambers 6b, 7b, via the channel groove 803a and an associated channel groove 803b aligned with it, for fluid connection of two fluid chambers 6b and 7b arranged at approximately the same axial height in the installed position and diametrically opposed in the radial direction. As the person skilled in the art will recognize, in the illustrated embodiment each fluid chamber is fluidly connected to a fluid chamber spaced at the same circumferential section and axially, and furthermore fluidly connected to a fluid chamber located axially at approximately the same height and radially diametrically opposed.

[0051] Depending on the embodiment, the channel shell 80 can be designed as an injection-molded part, in particular as a two-part injection-molded part, whereby embodiments made of a fiber-reinforced plastic are also within the scope of the invention.

[0052] Fig. Figure 5 shows the multidirectional hydraulically damping bearing 1 according to the invention in a partial exploded view, in which the two-part inner element 2, the outer sleeve 5, the two half-shells 80a, 80b, and the elastomer body 3 are shown axially and radially spaced from each other by the cage element 4, which is at least partially embedded with elastomer material. It can be seen that the two channel half-shells each radially enclose a pair of axially superimposed fluid chambers 6a, 6b and 7a, 7b, which are axially separated by the transverse webs 44, 45 of the cage element 4. The radially and axially opposing forked chamber walls 33a, 33b and 34a, 34b form respective cavities 39a, 39b, which expediently may not be filled with damping fluid, in particular damping liquid.Advantageously, these two cavities 39a, 39b can be filled with a gas such as air and sealed to allow high mobility of the chamber walls 33a, 33b and 34a, 34b under operating loads in the radial direction, in particular to adjust a low radial stiffness of the multidirectional damping hydraulic bearing 1 designed according to the invention.

[0053] As from Fig. As can be seen from Figure 5, the inner element can have a core section 21 and an outer section in the form of an injection-molded section 26, the latter being able to define the radial boundary surfaces of the inner element 2 in the area of ​​the fluid chambers 6a, 6b and 7a, 7b.

[0054] As explained, in one embodiment, the multidirectional hydraulically damping bearing 1 according to the invention may comprise at least four fluid chambers 6a, 6b and 7a, 7b, wherein a pair of fluid chambers 6a and 6b or 7a and 7b are arranged axially one above the other over the same circumferential section of the hydraulic bearing 1 or at least over an overlapping circumferential section of the hydraulic bearing 1, and a circumferentially spaced pair of fluid chambers, in particular a pair of fluid chambers radially opposite the first fluid pair diametrically, is provided for this pair of fluid chambers 6a and 6b or 7a and 7b. The second pair of fluid chambers may again be arranged axially one above the other over the same circumferential section or at least circumferentially overlapping the first pair.

[0055] It can be provided that the two fluid chambers 6a and 6b or 7a and 7b of a respective pair of fluid chambers are fluidically connected via a single fluid channel, and that each fluid chamber of this fluid pair is connected to another fluid chamber 6a, 6b, 7a, 7b of the other fluid pair with approximately the same axial position, so that in this embodiment each of these fluid chambers 6a, 6b, 7a, 7b is part of a hydraulic system in which damping work can be performed, both in the case of a radial relative displacement of cage element 4 and inner element 2 and in the case of an axial relative displacement of cage element 4 and inner element 2. It can be provided that the respective channel parameters, such as channel length and channel diameter, are adapted to the desired damping, so that the hydraulic damping behavior of the hydro bearing 1 according to the invention can be adjusted independently of each other in the radial and axial working directions.

[0056] In a further embodiment, it is also possible to connect the four described fluid chambers 6a, 6b, 7a, 7b, each comprising a pair of axially superimposed fluid chambers, with only two fluid channels, in particular such that a single fluid chamber of the first pair of fluid chambers 6a and 6b is connected to a single fluid chamber of the second fluid pair 7a and 7b, wherein the fluid-connected fluid chambers are arranged circumferentially offset from one another, in particular diametrically opposed and additionally axially offset from one another. In this embodiment as well, each of the at least four fluid chambers forms part of a hydraulic system that acts both under an axial load on the hydraulic bearing 1 and under a radial load on the bearing 1.In contrast to the embodiment with four fluid channels, the hydraulic damping properties, which are essentially determined by the design of the fluid channel connecting the respective two fluid chambers, are set the same here.

[0057] Fig. Figure 6 shows the hydraulic bearing 1 of the Fig. 1 in a full longitudinal section showing the diametrically opposed fluid chamber pairs 6a, 6b and 7a, 7b, each separated by a transverse web 44, 45 and chamber walls 33a, 33b, 34a, 34b extending from the respective transverse web to the inner element 2. Also visible are the two channel half-shells 80a, 80b with their channel grooves 801a, 802a and 803a and their corresponding channel penetrations 8011a, 8011b, 8012a, 8012b, 8021a, 8021b and 8031a, 8031b.

[0058] The fluid chambers 6a, 6b of the in the Fig. The 6 left fluid chamber pair are axially bounded externally by elastomeric chamber walls 35a, 35b, the fluid chambers 7a, 7b of the in Fig. 6 right fluid pair through the outer chamber walls 36a, 36b.

[0059] The hydraulic bearing 1 designed according to the invention, as described in the figures, has design features for limiting the radial and design features for limiting the axial relative displacement of the inner element 2 and the cage element 4 or outer sleeve 5. To limit the radial relative displacement, an annular stop element 23 is arranged on a radial interface in an axial end section of the inner element 2. In another embodiment, this stop element 23 can, for example, be formed integrally with the injection molding 26 onto the core section 21 of the inner element 2. A radial outer surface of the stop element 23 is spaced radially apart from an elastomer-coated radial inner surface of the cage element 4 by a distance d1. In the embodiment shown in the figures, the elastomer coating of the stop element 23 can be...The radial surface associated with the stop ring 23 is formed as an axial extension of the outer chamber wall 35a, 36a within the circumferential sections of the fluid pairs 6a, 6b and 7a, 7b.

[0060] A limitation of the relative axial displacement of the inner element and cage element 4 or outer sleeve 5 can be achieved in the hydro bearing 1 according to the invention by mounting the inner element 2 on a ,in Fig. 6, the upper section is attached to a component that extends radially outwards into the area of ​​the front face of the cage element 4, with elastomeric stops 37a, 37b arranged on its front face, see Fig. 1. As in Fig. As specified in 6, the axial spacing of the installed hydraulic bearing 1 designed according to the invention is thus limited to the distance d2.

[0061] Fig. Figure 7 shows a full section of the hydraulic bearing 1 of the Fig. 1 with regard to the radially and diametrically opposed support spring sections 31a, 31b, which in the described embodiment adhere to the associated radial thickenings 421a, 421b of the longitudinal webs 42a, 42b of the cage element 4 and to outer shell sections of the inner element 2 and are thus metallurgically connected. From the sectional view of the Fig. 7 further shows a further axial stop, formed by an internal axial surface of the ring plate 9 and an elastomeric stop 38a, 38b arranged on a lower end face of the cage element 4 in the figure, to limit an axial displacement of inner element 2 and outer sleeve 5 to the dimension d3. Reference symbol list 1 hydraulic bearing 2 interior elements 3 elastomer bodies 4 cage elements 5 Outer sleeve 6a, 6b Fluid chamber, first pair of fluid chambers 7a, 7b Fluid chamber, second pair of fluid chambers 8 channel shell 9 ring sheet 20 bore 21 Core Section 22 Exterior section 23 Stop element 24a, 24b side surface 25a, 25b side surface 26 Injection 26a, 26b Flange collar 31a, 31b Support spring section 33a, 33b Chamber wall 34a, 34b Chamber wall 35a, 35b outer chamber wall 36a, 36b outer chamber wall 37a, 37b elastomeric stop 38a, 38b elastomeric stop 39a, 39b cavity 40a, 40b Ring section 41 Flange 42a, 42b Longitudinal web 44 Crossbar 45 Crossbar 50 outer shell area 51 Inner surface area 80a, 80b Channel half-shell 81a, 82b Exterior area 82a, 82b Inner surface 83a, 83b Implementation 90 radial spacing 411 End face of the flange 421a, 421b radial thickening 441 radial projection 442a, 442b Fork arm 443 Fork opening 451 radial projection 452a, 452b Fork arm 453 Fork opening 801a, 801b Channel groove 802a, 802b Channel groove 803a, 803b Channel groove 805a, 805b Radial view 8011a Radial feedthrough 8011b Radial feedthrough 8012a Radial feedthrough 8012b Radial feedthrough 8021a Radial feedthrough 8021b Radial feedthrough 8031a Radial feedthrough 8031b Radial feedthrough Axis d1 radial spacing d2 axial distance d3 Axial distance

Claims

[1] Hydraulically damping bearing (1) comprising - an axially extending inner element, - an elastomer body (3), - a cage element which is embedded at least partially in the elastomer body (3), wherein the elastomer body (3) elastically connects the cage element and the inner element; - an outer sleeve (5) encompassing the inner element, the cage element and the elastomer body (3) - at least a first and a second fluid chamber (6a, 6b, 7a, 7b) each arranged between the outer sleeve and the inner element, which are connected via a fluid channel, comprising at least a third and a fourth fluid chamber each arranged between the outer sleeve and the inner element, and the at least four fluid chambers being connected via at least one further fluid channel, wherein each of the at least four fluid chambers (6a, 6b, 7a, 7b) participates in performing damping work during a relative displacement of the inner element and the cage element in a first direction and during a relative displacement of the inner element and the cage element in a second direction, characterized by, that an annular stop element (23a, 23b) is arranged axially outside the fluid chambers (6a, 6b, 7a, 7b) on the inner element at an axial end section of the bearing (1), which is located radially spaced from an elastomer section arranged on an inner surface of one of the ring elements of the cage in the unloaded state of the bearing (1). [2] Hydraulically damping bearing (1) according to claim 1, characterized by , that the bearing (1) has at least two pairs of axially arranged fluid chambers (6a and 6b; 7a and 7b), wherein the at least two pairs are spaced apart from each other circumferentially, in particular arranged radially opposite each other at the same axial height. [3] Hydraulically damping bearing (1) according to claim 1 or 2, characterized by , that the two fluid chambers (6a and 6b or 7a and 7b) of a respective pair of axially arranged fluid chambers extend essentially over the same circumferential section. [4] Hydraulically damping bearing (1) according to one of claims 1 to 3, characterized by , that the at least four fluid chambers (6a, 6b, 7a, 7b) have an essentially identical extent in the circumferential direction of the bearing (1). [5] Hydraulically damping bearing (1) according to any one of claims 1 to 4, characterized by , that each of the at least four fluid chambers (6a, 6b, 7a, 7b) is connected to a fluid chamber arranged radially opposite to the respective fluid chamber and in particular at the same axial height by means of an associated fluid channel and to a fluid chamber arranged axially adjacent to the respective fluid chamber and in particular on the same circumferential section by means of an associated fluid channel. [6] Hydraulically damping bearing (1) according to any one of claims 1 to 5, characterized by, that two fluid channels for providing damping work in the axial direction and two fluid channels for providing damping work in the radial direction are arranged between the at least four fluid chambers (6a, 6b, 7a, 7b). [7] Hydraulically damping bearing (1) according to any one of claims 1 to 4, characterized by , that each of the four fluid chambers (6a, 6b, 7a, 7b) is connected to one of the other three fluid chambers via a fluid channel, the interconnected fluid chambers being arranged radially opposite each other and axially consecutive to each other. [8] Hydraulically damping bearing (1) according to any one of claims 1 to 7, characterized by, that the cage element in the longitudinal section of the bearing (1) has a first transverse web (44) which extends radially towards the inner element to provide a respective axial pumping surface for two axially successive fluid chambers arranged over a predetermined circumferential section of the at least four fluid chambers (6a, 6b, 7a, 7b). [9] Hydraulically damping bearing (1) according to claim 8, characterized by , that the cage element in the longitudinal section of the bearing (1) has a second crossbar (45) spaced at a circumferential distance to the first crossbar (44), which extends radially towards the inner element to provide a respective axial pumping surface for the two other fluid chambers arranged over a predetermined circumferential section and axially successive. [10] Hydraulically damping bearing (1) according to claim 8 or 9, characterized by, that adhering to the radial end section of the respective transverse web (44, 45) facing the inner element, two axially opposing and angled inner elastomeric chamber wall sections (33a, 33b, 34a, 34b) extend towards the inner element to axially delimit the two axially successive fluid chambers (6a, 6b and 7a, 7b, respectively). [11] Hydraulically damping bearing (1) according to claim 8, 9 or 10, characterized by that the cage element has at least two axially spaced ring sections which are connected by at least two, in particular diametrically opposed, longitudinal webs, wherein the first and / or the second transverse web (44, 45) are connected to the two longitudinal webs (42a, 42b). [12] Hydraulically damping bearing (1) according to any one of claims 1 to 11, characterized by, that in a transverse direction of the bearing to a longitudinal direction of the inner element at least two, in particular straight and parallel to each other and bounded by elastomer wall sections, cavities are included, each adjoining the inner element. [13] Hydraulically damping bearing (1) according to any one of claims 1 to 12, characterized by , that a channel shell, in particular a two-part one, is provided, which is arranged axially between the ring sections of the cage element and closes off the fluid chambers (6a, 6b, 7a, 7b) to the outer sleeve and has radial recesses to provide at least two, in particular four, fluid channels with associated inner wall sections of the outer sleeve. [14] Hydraulically damping bearing (1) according to any one of claims 1 to 13, characterized by , that the inner element in the axial section of the fluid chambers (6a, 6b, 7a, 7b) has an approximately square cross-section. [15] Hydraulically damping bearing (1) according to any one of claims 1 to 14, characterized by , that the inner element has a collar-like, in particular square, flange to provide an inner part-side attachment to a respective outer chamber membrane wall. [16] Hydraulically damping bearing (1) according to any one of claims 1 to 15, characterized by , that an axial end face of the cage is covered with an elastomer buffer which lies axially below the end face of the inner element. [17] Hydraulically damping bearing (1) according to any one of claims 1 to 16, characterized by that the cage element is designed in two parts, wherein the two parts can be assembled in a longitudinal section plane in the transverse direction with radially acting complementary locking means which, after locking, provide an axial positive locking of the two cage elements to each other.

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