DE102018006805B4 - Hydroelastic bearing - Google Patents

Abstract

Hydroelastic bearing (1), comprising a bearing body (2) and an outer sleeve (4) which is connected to the bearing body (2) and which surrounds the bearing body (2) in the radial direction (Ra), the bearing body (2) having: a Inner sleeve (12), a bearing frame (8) which surrounds the inner sleeve (12) in the radial direction (Ra), and an elastomer body (10) which elastically connects the inner sleeve (12) and the bearing frame (8) to one another, the bearing frame (8) has at least two bearing shells (6), the at least two bearing shells (6) being elastically connected to one another by means of the elastomer body (10) such that the at least two bearing shells (6) are spaced apart in an unloaded state in the circumferential direction (Um) (14) to one another and the distance (14) of the at least two bearing shells (6) to one another in an assembled state in which the bearing body (2) is mounted in the outer sleeve (4), the elastomer body (10) in Circumferential direction (Um) betw The at least two bearing shells (6) have a bridging section (26) which bridges the distance (14) between the at least two bearing shells (6), the bearing body (2) having a fluid channel (2) on its surface located on the outside in the radial direction (Ra). 22), which fluidly connects at least two fluid chambers (28) formed separately from one another in the bearing body (2) and the fluid channel (22) running through the bridging section (26).

Description

The invention relates to a hydroelastic bearing for the essentially vibration-decoupling mounting of a component.

With such hydroelastic bearings there is the technical challenge, on the one hand, to essentially decouple a component to be supported with them from vibrations that arise, for example, during the operation of a motor vehicle, or to dampen these vibrations and, on the other hand, to provide a bearing that is stable enough, in some cases high forces that have an effect on the bearing can be taken up or transferred to another component without being damaged.

The DE 195 02 732 A1 discloses an elastomer bearing bushing in which a circular cylindrical elastomer element with an annular recess and two spaced apart and communicating pockets are formed. An outer metallic tube receives an inner ring in a press fit in its longitudinal opening; the ring has a peripheral channel-forming recess in its outer surface and a pair of spaced-apart windows, the pockets, windows and channel communicating with one another. The elastomeric element has been constrained longitudinally in the ring and outer tube while being immersed in hydraulic fluid, filling the channel and pockets with fluid. The ring is arranged in the recess of the elastomeric element. An inner tube is then introduced into the opening of the elastomeric element and fixed in a manner according to the invention by forces acting in the radial direction without requiring adhesive or vulcanization.

The U.S. 5,657,510 A discloses a fluid chamber space of an elastic block which is arranged between an outer cylinder and an inner cylinder. The fluid chamber space is divided into two chambers by means of an elastic wall, the inner edges of which are in engagement with an engagement groove of an elastic wall mounting. The outer edges are clamped between end portions of two fluid chamber covers that cover an open portion of the fluid chamber space. When the outer cylinder is pressed in this state, the internal pressure increase is suppressed and the concentration of the stress is decreased even if the elastic wall is elastically deformed by the fluid pressure because a contact portion with the elastic block is movable around the elastic wall so that a spring with low action and high damping properties can be obtained and durability is improved.

JP H07-190 132 A discloses an outer cylinder fitting which is press-fitted into the base end side of a trailing arm for connection. An inner cylinder fitting is arranged on the inside of the outer cylinder fitting, and a protruding plate is provided at the end portion of the inner cylinder fitting. An elastic body made of rubber is arranged between the outer cylinder fitting and the inner cylinder fitting. An elastic body is also vulcanized to a protruding plate and the flange portion of the outer cylinder fitting. When a force is applied along the axial direction of the cylinder outer fitting, since the projection opposes the flange part, the elastic body formed by the flange part 12B and the projection 18th is held, pulled to absorb force so that no large displacement is generated in the axial direction.

The DE 10 2012 213 440 A1 discloses a bush bearing for receiving in an outer sleeve with an axially extending inner part, a bearing body surrounding the inner part made of an elastic material with at least two chambers for receiving a damping means and a cage surrounding the bearing body. The bush bearing is characterized in that the cage is formed from at least two cage parts, the spacing of which can be changed in the radial direction, and that a joint area provided between the cage parts is sealed.

The DE 10 2007 026 470 A1 discloses a hydraulic bearing, the elastomeric bearing body of which is preloaded when it is pressed into an outer sleeve. The bush bearing is designed with an inner part, an outer sleeve surrounding the inner part and the bearing body arranged between the inner part and the outer sleeve with at least two chambers for a damping means and at least one channel connecting these chambers, offset from one another with respect to the bearing circumferential direction and spatially separated from one another by webs of the bearing body . In each web there is at least one groove extending axially through the bearing body, through which a bearing cage vulcanized into the bearing body is divided into at least two cage parts along a parting plane in the axial direction. To prevent the damping agent from escaping, a trough is formed in at least one of the webs in an axially central region of the bearing body, which trough extends across the web transversely to the groove formed in the web in question. A throttle element bridging the parting plane and in which the channel is designed as a short throttle channel is inserted into the depression.

The DE 38 20 805 A1 discloses a vibration damping device, in particular for mounting the engine of a motor vehicle on a motor vehicle body. An elastic bearing part is firmly connected between an inner and an outer cylinder and has a cavity above the load introduction onto the inner cylinder, as well as a vibration damping unit with fluid damping in the direction of the load introduction, forming two fluid chambers connected by a flow throttle channel.

The EP 0 331 916 A2 discloses a bushing comprising two concentric cylindrical members and a connecting elastomeric body disposed therebetween. The space between the elastomer body and the two cylindrical elements contains two opposing chambers connected by a channel. The chambers and the channel are filled with a fluid to create a circuit that can dampen the low frequency and high amplitude vibrations acting between the two elements of the bushing. The socket includes means for absorbing high frequency and small amplitude vibrations represented by two cavities occupied by a compressible fluid. The voids are obtained between a rigid surface of the socket and a flexible membrane.

It is an object of the present invention to provide an improved hydroelastic bearing with increased service life.

One aspect relates to a hydroelastic bearing which has a bearing body and an outer sleeve which is connected to the bearing body and which surrounds the bearing body in the radial direction. The bearing body contains an inner sleeve, a bearing frame which surrounds the inner sleeve in the radial direction, and an elastomer body which elastically connects the inner sleeve and the bearing frame to one another. The bearing frame has at least two bearing shells which are elastically connected to one another by means of the elastomer body such that the at least two bearing shells are at a distance from one another in an unloaded state in the circumferential direction. The distance in the circumferential direction of the at least two bearing shells from one another is reduced in a mounted state in which the bearing body is mounted in the outer sleeve.

The unloaded state can be understood as a preassembled state of the bearing body in which the bearing frame, in particular its bearing shells, is elastically connected to the inner sleeve by means of the elastomer body and is not mounted in the outer sleeve, with no external force acting on the bearing frame, in particular the Bearing shells, has the effect that the elastomer body is deformed and the distance between the bearing shells changes.

The assembled state can be understood to mean a state of the bearing body in which the bearing body has, for example, first been compressed in the radial direction and then inserted or pressed into the outer sleeve. Thereafter, the bearing body can partially relax due to the elasticity of the elastomer body or remain in the compressed shape. Alternatively, the bearing body can be further compressed in the radial direction, at least in sections, by means of the introduction or pressing into the outer sleeve. The bearing body is arranged or mounted in the outer sleeve with a preload in the radial direction. It goes without saying that - in order to achieve the preload - an, in particular assembly-relevant, outer diameter of the bearing frame or the bearing body in the unloaded state is somewhat larger than an, in particular assembly-relevant, inner diameter of the outer sleeve.

An advantage of the present invention is that the inventive design of the hydroelastic bearing can easily generate a preload in the bearing body or in the elastomer body, which can increase the service life of the hydroelastic bearing or the elastomer body. In particular, it is possible in a simple manner to avoid or reduce areas with sharp-edged material transitions between the bearing frame and the elastomer body. Furthermore, because the bearing frame has at least two bearing shells and thus the inner sides of the bearing shells are more accessible, sharp edges on the inner sides of the bearing shells can be avoided or smoothed when producing the bearing frame. As a result, lower local load peaks occur in the areas in which the elastomer body touches the insides of the bearing shells, which has a positive effect on the load capacity and the service life of the elastomer body and thus the hydroelastic bearing. In addition, the hydroelastic bearing according to the invention can be produced in a simple manner.

An axial direction or an axial direction is a direction in an extension of a length of a component. In the case of a body, for example, of cylindrical design, the axial direction is oriented approximately parallel to a surface line or the longitudinal axis of the body. The outer sleeve, the inner sleeve, the bearing body and the bearing frame can be essentially cylindrical and can be arranged concentrically to one another.

A radial direction or radial direction is oriented perpendicular to the axial direction. For example, in the case of a cylindrical bearing body, the radial direction is aligned so as to coincide with the radius of the cylindrical bearing body. In the case of a hollow cylindrical bearing frame or a hollow cylindrical outer sleeve, the radial direction can run in the direction of the wall thickness of the hollow cylindrical bearing frame or the hollow cylindrical outer sleeve. The radial direction can run normal to an outer circumference of the hollow cylindrical bearing frame or the hollow cylindrical outer sleeve.

Correspondingly, a circumferential direction is a direction in or along an extension of the circumference of the component.

The terms “outside” or “inside” and the like used here mean in the context of the present invention that an, in particular idealized or imagined, center point is an innermost point. An outer area in relation to this is a, in particular idealized or imaginary, circumferential area which at least partially surrounds the center point. A point or area, which is referred to as being further out than another point or area, is therefore further away in the radial direction from the center point in the direction of the circumferential area than the other, further inward point or area.

The component, in particular the component to be supported, can be a force-loaded component, wherein the forces on the component can be absorbed by the bearing and / or transferred to another element for absorption and which can be essentially decoupled from vibrations by means of the bearing, which can occur at an installation location of the bearing. For example, the component can be a chassis component which is to be connected to a vehicle frame via the hydroelastic bearing.

The elastomer body can be an elastic body that is on the one hand able to decouple the component from vibrations of another part connected to the component via the elastomer body and on the other hand is able to absorb a force from the component and / or to another Transfer part. The elastomer body can be formed from an elastomer material such as natural or synthetic rubber. The elastomer body can be designed as a one-piece, coherent body, or it can have elastomer body sections that are separate from one another.

At least two fluid chambers can be formed in the elastomer body which, with the inner sleeve in between, can be formed diametrically to one another. The fluid chambers can be delimited radially outward by the outer sleeve and filled with a damping fluid. The fluid chambers are fluidically connected to one another via a fluid channel, so that in the event of a relative, in particular radial, displacement of the inner sleeve to the outer sleeve or to the bearing frame, a fluid exchange of the damping fluid takes place between the fluid chambers, whereby damping is generated. The fluid channel is formed on the radial outer surface of the bearing body, wherein the fluid channel can be delimited radially outward by the outer sleeve. The fluid channel can be formed in the elastomer body, wherein the fluid channel can be at least partially supported or stiffened by a recess formed in the bearing frame along the radial outer surface of the bearing frame. The fluid channel can have a substantially rectangular cross section.

The elastomer body can be injection-molded on or around the inner sleeve and the bearing frame, in particular the bearing shells. In particular, the material of the elastomer body can be vulcanized onto the inner sleeve and / or the bearing frame or its bearing shells. The elastomer body can be injection molded on or around the body in one tool in one work step.

The component can be connected directly or indirectly to the hydroelastic bearing by means of the inner sleeve. The inner sleeve can be arranged within the elastomer body, preferably approximately in the middle of the elastomer body. The inner sleeve, in particular the length of the inner sleeve, can extend in an essentially axial direction through the elastomer body at least partially over the extent of the elastomer body in the axial direction, or even beyond.

The inner sleeve can be designed as a sleeve for receiving a fastening element, such as, for example, a bearing journal or a fastening bolt element of the component. However, it is also conceivable that the inner sleeve is formed by a recess in the axial direction in the elastomer body, into which the bearing journal or the fastening bolt can be inserted or by which the bearing journal or the fastening bolt can be received. The inner sleeve can be embedded in the elastomer body. In other words, the elastomer body can be cast or injection-molded onto the inner sleeve. The inner sleeve can be made of a rigid material such as metal or plastic, and can be essentially cylindrical.

The bearing frame can extend on the outside of the elastomer body in the circumferential direction. The The outer diameter of the bearing frame can essentially correspond to the outer diameter of the bearing body, wherein the radial outer surface of the bearing frame can be at least partially covered by a thin layer of the material of the elastomer body. The elastomer body can have a circumferential elastomer seal on the radial outer surface of the bearing frame. The bearing frame can be made of a rigid material such as metal or plastic.

The bearing frame can be embedded in the elastomer body. In other words, the elastomer body can be cast or injection-molded onto the bearing frame. For example, the elastomer body can be cast or injected onto the inner sleeve and the bearing frame in one work step. Inner sleeve, elastomer body and bearing frame can be aligned concentrically with one another and can have essentially the same axial extent or length.

The bearing frame can have two, three, four, five, six or more bearing shells. The bearing shells are designed in particular in such a way that together they result in a shape whose envelope essentially has the shape of a cylinder, in particular a hollow cylinder. In other words, the bearing shells are designed in particular in such a way that they complement one another to form the hollow cylindrical bearing frame. Two or more of the bearing shells can be connected by connecting elements such as film joints or the like, which can simplify the manufacture of the hydroelastic bearing. The connecting elements can be configured to provide a gap between the bearing shells and to yield under pressure.

The outer sleeve can have one or more fastening devices for fastening the hydroelastic bearing. However, the outer sleeve can also have a smooth radial outer surface in order to be able to be mounted in a corresponding receptacle. The outer sleeve can also be aligned concentrically to the inner sleeve, elastomer body and bearing frame and can also have essentially the same axial extent or length. At its axial ends, the outer sleeve can in particular be crimped inwards. The outer sleeve can be made of a rigid material such as metal or plastic.

In particular, the bearing body can be non-positively and / or positively connected to the outer sleeve.

The elastomer body can have at least one space between the inner sleeve and the bearing frame in order to create space for the displacement of the inner sleeve relative to the bearing frame or to the outer sleeve. This intermediate space can be provided at least partially by the fluid chambers.

In the unloaded state, the bearing shells are spaced apart from one another in the circumferential direction of the bearing frame. This means that the end edges of the bearing shells lying opposite one another in the circumferential direction are spaced apart from one another in the unloaded state and do not touch one another. The distance in the circumferential direction in the unloaded state is provided at least between a pair of opposite end edges of the bearing shells. Preferably, however, the distance in the circumferential direction in the unloaded state is provided between all opposite end edges of the bearing shells, in an embodiment with two bearing shells that is between two pairs of opposite end edges of the bearing shells. However, it is also conceivable to provide a smaller distance or no distance between one of the pairs of opposite end edges of the bearing shells, so that the opposite end edges of the bearing shells touch there in the unloaded state. The distance between the end edges of the bearing shells lying opposite one another in the circumferential direction can be bridged at least in sections by the elastomer body.

In the assembled state, the distance between the bearing shells from one another in the circumferential direction is reduced, that is to say less than in the unloaded state, since in the assembled state the bearing shells are compressed in the radial direction or are pressed towards one another. In the assembled state, the spacing of the bearing shells from one another in the circumferential direction can be reduced to zero, at least in sections, so that the end edges of the bearing shells lying opposite one another in the circumferential direction can abut or touch one another at least in sections. The circumferentially opposite end edges of the bearing shells can also be covered, at least in sections, with a thin layer of the material of the elastomer body, and in the assembled state the sections of the elastomer body covering the end edges of the bearing shells can abut or touch one another at least in sections.

The bearing body preferably has a gap, at least in sections, between the at least two bearing shells, viewed in the circumferential direction.

The gap is in particular an air gap. In other words is the gap between the Bearing shells free from the material of the elastomer body. A gap can thus be formed at least in sections on the elastomer body in an area between the at least two bearing shells. The width of the gap or the gap preferably extends in the circumferential direction and the length of the gap or the gap preferably extends in the axial direction of the bearing frame. The gap or the gap is present in particular in the unloaded state. In particular, the gap or the gap in the assembled state is at least partially smaller than in the unloaded state.

The gap or the gap can be formed between boundary surfaces of adjacent bearing shells, that is to say between the end edges of the bearing shells that are opposite one another in the circumferential direction. The gap or the gap can, in particular in the unloaded state, at least in sections have essentially the same width in the circumferential direction as the distance between the bearing shells. Since the circumferentially opposite end edges of the bearing shells can also be covered at least in sections with a thin layer of the material of the elastomer body, the gap can also be at least partially slightly smaller than the distance between the bearing shells. The gap or the gap advantageously enables easy elastic displaceability of the bearing shells relative to one another and also prevents excessive local deformation of the elastomer body in the assembled state.

The elastomer body can, in particular in the unloaded state, have a recess beyond the area of the gap or the gap, at least in sections, which extends radially inward from the gap or the gap. Thus, without changing the material of the elastomer body, the elastic displaceability of the bearing shells relative to one another can be changed, in particular increased.

Viewed in the circumferential direction, the elastomer body has a bridging section between the at least two bearing shells, which bridges the distance between the at least two bearing shells.

The bridging section can in particular be formed at the middle level of the bearing body or the elastomer body, viewed in the axial direction. The bridging section can fill the distance between the bearing shells in this area, that is to say the distance between the end edges of the bearing shells which are opposite one another in the circumferential direction. The bridging section can be provided at least between a pair of opposite end edges of the bearing shells. Or the bridging section can be provided between all opposite end edges of the bearing shells. In an embodiment with two bearing shells, two bridging sections can be provided, each of which is arranged between one of the two pairs of opposite end edges of the bearing shells. In the assembled state, the bridging section is at least partially squeezed in by or between the end edges of the bearing shells that are opposite one another in the circumferential direction. The distance between the bearing shells can in particular be bridged exclusively by the bridging section, whereas other areas of the distance are free of material of the elastomer body, that is to say have a gap.

The bearing body has a fluid channel on its outer surface in the radial direction, which fluidly connects at least two fluid chambers formed separately from one another in the bearing body. The fluid channel runs through the bridging section.

This configuration allows the fluid channel to be guided in an advantageous manner from the side of the one bearing shell to the side of the other bearing shell, the fluid channel being delimited radially outwardly by the outer sleeve.

The elastomer body can contain the fluid channel. The elastomer body and the fluid channel can be produced in one operation and / or from the same material. The elastomer body can have various functional sections, for example the bridging section, a connecting section by means of which in particular the inner sleeve and the bearing frame are elastically connected, a fluid chamber section, a fluid channel section by means of which the fluid chambers that are formed separately from one another are fluidically connected to one another, a spring section, a sealing section, a stop section, etc. For example, in an embodiment with two bearing shells and two bridging sections, the fluid channel can run through both bridging sections or only through one of the bridging sections.

For example, the bearing body can be formed in one piece by means of vulcanization or gluing the elastomer body to the inner sleeve and the bearing frame.

At least one of the bearing shells can preferably have a recess in the circumferential direction in the region of the bridging section.

In other words, the distance between the end edges of the two bearing shells is in The circumferential direction in the area of the recess or the bridging section is preferably larger than in the other areas. Thus, in the mounted state of the bearing body, compressed or squeezed material of the elastomer body, in particular the bridging section, can be received in the recess, so that lower local upsets or lower local stresses occur in the elastomer body. This can also prevent the contour of the fluid channel in the bridging section from changing significantly, for example due to bulges. The flow of the fluid between the fluid chambers and thus the damping behavior of the hydroelastic bearing thus remains essentially unchanged, although the fluid channel or the bridging section is also compressed when the bearing shells are pressed together for the assembled state.

The length of the recess, that is to say an extension of the recess in the axial direction, can be greater than an extension of the recess for the fluid channel or the fluid channel in the axial direction in the region of the recess. Advantageously, it is thus possible to improve the reception of material of the elastomer body, in particular of the bridging section, which is compressed or squeezed in in the mounted state of the bearing body in the recess, in particular in a receiving space formed by the recess in the bearing shell.

The bearing shells are preferably each designed to be identical to one another.

In particular, all of the bearing shells of the hydroelastic bearing that form the bearing frame can be designed to be identical to one another. With this configuration, manufacturing and / or storage costs can advantageously be reduced.

In the case of bearing shells designed identically to one another, the respective bearing shell, in particular a configuration of the end edges, can be designed mirror-symmetrically with respect to a transverse plane which is oriented perpendicular to the axial direction and, in particular, is arranged centrally to the bearing shell when viewed in the axial direction. The bearing frame can thus be formed with both an even and an odd number of bearing shells.

The mirror symmetry to the transverse plane described here relates to a single bearing shell. With such a mirror symmetry, both an even and an odd number of identical bearing shells can form a rotating cylinder. In the case of an asymmetrical design in relation to the transverse plane, as shown in the figures, an even number of identical bearing shells is required in order to form a rotating cylinder.

Alternatively, in the case of identical bearing shells, the respective bearing shell, in particular a configuration of the end edges, can be designed asymmetrically with respect to a transverse plane which is oriented perpendicular to the axial direction and, in particular, is arranged in the center of the bearing shell when viewed in the axial direction. With this configuration, the bearing shells can only be positioned in a single position with respect to one another with their end edges matching one another in order to form the bearing frame. Thus, a predetermined position of the bearing shells can be form-coded with respect to one another. Assembly errors in the production of the bearing body, in particular with regard to the connections of the fluid channels, can be excluded with this configuration.

The bearing frame preferably has exactly two bearing shells, which are each designed as half-shells.

The two half-shells can be rotated by 180 ° about an axis of rotation aligned in the radial direction with respect to one another and pivoted by 180 ° about its axial direction. In general, especially if there are more than two bearing shells, the bearing shells can each be rotated 180 ° around an axis of rotation aligned in the radial direction and pivoted about their axial direction by a pivot angle of 360 ° divided by the number of bearing shells. For example, in the case of three bearing shells, the bearing shells are each rotated by 180 ° about an axis of rotation aligned in the radial direction and pivoted by 120 ° about its axial direction.

With exactly two bearing shells, the elastomer body can have a bridging section exclusively at the distance between one of the two pairs of opposite end edges of the bearing shells in order to guide the fluid channel from one bearing shell over the distance to the other bearing shell. At the other distance between the other opposite end edges of the bearing shells, the fluid channel is then not passed over the bearing shells, so a bridging section can be omitted there. In particular, the fluid channel can then open into the respective fluid chamber in an area near these end edges of the respective bearing shells.

Furthermore, with exactly two bearing shells, the recess can be provided exclusively at one of the two distances between the bearing shells on at least one of the two opposite end edges.

The inner sleeve preferably has a stop element which protrudes in the radial direction from the inner sleeve and limits a radial displacement of the inner sleeve relative to the outer sleeve.

The bearing shells preferably have a stop recess in order to allow the stop element to strike the inner surface of the outer sleeve.

The stop element is preferably designed in such a way that it rests against an inner surface of the outer sleeve in the event of a maximum permissible radial displacement of the inner sleeve. Thus, the outer sleeve also serves as a stop for the stop element to limit the displacement of the inner sleeve in the radial direction to protect the elastomer body from damage caused by excessive displacement.

In particular, each of the bearing shells can each have a stop recess, wherein a stop element can be provided for each bearing shell or stop recess. Thus, the limited displacement of the inner sleeve can be provided in several different radial directions.

The stop element can be provided centrally on the inner sleeve or on the bearing body, viewed in the axial direction.

The stop element can be coated with the material of the elastomer body. In other words, the stop element can be encapsulated by the elastomer body. A striking of the stop element against the outer shell can thus be dampened.

• Ausbilden des Lagerrahmens mit mindestens zwei Lagerschalen,
• Elastisches Verbinden der mindestens zwei Lagerschalen mit dem Elastomerkörper derart, dass die mindestens zwei Lagerschalen in einem unbelasteten Zustand in Umfangsrichtung einen Abstand zueinander aufweisen und
• Montieren der mindestens zwei Lagerschalen in der Außenhülse derart, dass der Abstand der mindestens zwei Lagerschalen zueinander in einem in die Außenhülse montierten Zustand des Lagerkörper verkleinert ist.

Another aspect relates to a method for providing an above-described hydroelastic bearing with the steps:

• Forming the bearing frame with at least two bearing shells,
• Elastic connection of the at least two bearing shells to the elastomer body in such a way that the at least two bearing shells are at a distance from one another in the circumferential direction in an unloaded state and
• Mounting the at least two bearing shells in the outer sleeve in such a way that the spacing of the at least two bearing shells from one another is reduced in a state of the bearing body mounted in the outer sleeve.

In order to achieve the mounted state of the bearing body, the bearing body is for example first compressed in the radial direction and then inserted or pressed into the outer sleeve, the bearing body being arranged or mounted in the outer sleeve with a bias in the radial direction. It goes without saying that - in order to achieve the preload - an, in particular assembly-relevant, outer diameter of the bearing frame or the bearing body in the unloaded state is somewhat larger than an, in particular assembly-relevant, inner diameter of the outer sleeve.

The one or more advantages of the method described arise analogously to the advantages of the hydrostatic bearing described above.

An exemplary embodiment of the hydroelastic bearing according to the invention is explained in more detail below with reference to drawings. It goes without saying that the present invention is not limited to the exemplary embodiment described below and that individual features of the exemplary embodiment described can be combined to form further exemplary embodiments.

• 1 eine Seitenansicht eines Lagerkörpers des erfindungsgemäßen hydrostatischen Lagers gemäß dem Ausführungsbeispiel der Erfindung in einem unbelasteten Zustand;
• 2 eine räumliche Ansicht des Lagerkörpers gemäß 1 in einem montierten Zustand;
• 3 eine räumliche Ansicht des Lagerrahmens des Lagerkörpers gemäß 1, wobei die Lagerschalen wie im unbelasteten Zustand positioniert sind;
• 4 einen Halb-Querschnitt einer Vorderansicht des hydroelastischen Lagers gemäß 1 in einem unbelasteten Zustand;
• 5 einen Halb-Querschnitt einer Vorderansicht des hydroelastischen Lagers gemäß 1 in einem montierten Zustand;
• 6 eine räumliche Ansicht zweier Lagerschalen des Lagerkörpers gemäß 1 in gleicher Ausrichtung;
• 7 eine räumliche Ansicht einer Lagerschale des Lagerkörpers gemäß 1 mit Blick auf deren Endkanten und
• 8 eine räumliche Ansicht eines aufgeschnittenen hydrostatischen Lagers mit dem Lagerkörper gemäß 1.

Show it:

• 1 a side view of a bearing body of the hydrostatic bearing according to the invention according to the embodiment of the invention in an unloaded state;
• 2 a three-dimensional view of the bearing body according to 1 in an assembled state;
• 3 a three-dimensional view of the bearing frame of the bearing body according to 1 , wherein the bearing shells are positioned as in the unloaded state;
• 4th a half-cross section of a front view of the hydroelastic bearing according to FIG 1 in an unloaded state;
• 5 a half-cross section of a front view of the hydroelastic bearing according to FIG 1 in an assembled state;
• 6th a three-dimensional view of two bearing shells of the bearing body according to 1 in the same orientation;
• 7th a three-dimensional view of a bearing shell of the bearing body according to 1 with a view of their end edges and
• 8th a three-dimensional view of a cut hydrostatic bearing with the bearing body according to FIG 1 .

For the sake of a more detailed presentation, the in 1 shown hydroelastic bearings according to the invention 1 in the 8th shown outer sleeve 4th omitted. In a sense it is not the complete hydroelastic bearing 1 but only the bearing body 2 shown. In the 3 returns shown 40 on the bearing shells 6th are not visible because of the radial outer surface of the bearing frame 8th from a thin layer of the material of the elastomer body 10 is covered.

The axial direction Ax, the circumferential direction Um and the radial direction Ra are shown in the figures by means of directional arrows, in particular in the manner of a coordinate system. Although the direction arrows only point in one direction, the directional information also contains a respective opposite direction. Two radial directions Ra are given by way of example; this is only intended to give an impression of the many possible radial directions Ra. A dimension in the circumferential direction Um is given in simplified form in the figures as a dimension projected onto a plane.

The bearing body shown in a front view 2 of the hydrostatic bearing 1 is shown in an unloaded state. The bearing shells designed as half shells are here 6th of the storage frame 8th such by means of the elastomer body 10 with the inner sleeve 12 in one piece elastically connected that they are a distance 14th have to each other in the circumferential direction Um. Thus, in the circumferential direction Um are opposite end edges 16 of the respective bearing shells 6th spaced apart and do not touch. The bearing shells 6th seen in the axial direction Ax are chamfered at their ends or flanged inward, which means that the bearing body can be inserted or mounted 2 into the outer sleeve 4th is relieved. Flanging is also an advantage around the elastomer body 10 in addition to the positive connection described above, it is also positively connected to the bearing frame 8th connect to.

The inner sleeve 12 stands on both ends of the bearing body 2 seen in the axial direction Ax over the bearing shells 6th over and has two oppositely formed stop elements 18th in the radial direction Ra from the inner sleeve 12 protrude. The stop elements 18th are seen in the axial direction Ax approximately in the middle of the inner sleeve 12 or the bearing shells 6th educated.

The bearing shells 6th each have a stop recess 20th through which the respective stop element 18th through with the maximum permissible displacement of the inner sleeve 12 in the radial direction Ra on the outer sleeve (not shown) 4th strikes. The stop recesses 20th are like the stop elements 18th in the case of the half-shells shown here 6th formed opposite one another.

Alternatively, the stop elements 18th and the stop recesses 20th be formed at positions different from one another in the axial direction Ax.

On the outer surface of the bearing shells in radial direction Ra 6th is a fluid channel 22nd formed, the two around the stop elements 18th fluid chambers formed around and fluidically separated from one another 28 connects. The respective stop elements 18th extend into the respective fluid chambers 28 inside. The stop recesses 20th each form radial openings of the respective fluid chambers 28 , which in the assembled state through the outer sleeve 4th are closed radially outward. The fluid channel 22nd is from one bearing shell 6th about that by the distance 14th formed gap 24 to the other bearing shell 6th guided, the gap 24 by means of a bridging section 26th of the bearing body 2 or the elastomer body 10 is bridged. The fluid channel 22nd is in the assembled state in the radial direction Ra continuously outwards from the outer sleeve (not shown) 4th limited.

The fluid channel 22nd runs from one fluid chamber 28 coming at one end 30th the one bearing shell 6th in the circumferential direction Um before moving in the axial direction Ax approximately to the middle of the one bearing shell 6th runs. Then the fluid channel bridges 22nd in the circumferential direction by the distance 14th or the gap 24 and initially continues in the circumferential direction Um on the other bearing shell 6th before moving in the axial direction Ax to the other end region 32 the other bearing shell 6th runs. There it then continues in the circumferential direction Um until it is in the other fluid chamber 28 flows out. If necessary, the fluid channel 22nd in addition to this again run in the axial direction Ax and then again in the circumferential direction Um before entering the other fluid chamber 28 flows out.

The gap 24 or the end edges 16 of the bearing shells 6th run asymmetrically to a transverse plane AA , seen in the axial direction Ax through the middle of the bearing body 2 or the bearing shells 6th and is oriented perpendicular to the axial direction Ax. On both sides of the transverse plane AA trained and each to the (not shown) recesses 40 according to 3 adjoining intermediate sections 34 the end edges 16 a bearing shell 6th run in the unloaded state in the axial direction Ax parallel to a longitudinal plane BB of the bearing body 2 which is the central axis of the bearing body 2 contains. End sections 36 the end edges 16 a bearing shell 6th run at the respective end areas 30th , 32 the bearing shell 6th each in the opposite direction parallel to the longitudinal plane BB offset. The transverse plane AA and the longitudinal plane BB are in 1 each shown in its two-dimensional view, i.e. as a straight line.

Alternatively, the gap 24 or the end edges 16 of the bearing shells 6th mirror symmetrical to the transverse plane AA run away. For example, the end sections then run 36 the end edge 16 at the respective end areas 30th , 32 of the bearing shells 6th in the same direction parallel to the longitudinal plane BB offset. The end sections 36 the end edges 16 can also each by the same amount to the longitudinal plane BB be offset like those on both sides of the transverse plane AA trained and each to the (not shown) recesses 40 adjacent intermediate sections 34 the end edge 16 the bearing shell 6th .

In 2 is a perspective view of the bearing body 2 according to 1 shown in an assembled state.

In the mounted state of the bearing body shown here 2 are the bearing shells 6th compressed so far in the radial direction Ra that the distance 14th of the bearing shells 6th or the gap 24 equals zero. The end edges 16 of the bearing shells 6th So touch and are not shown here - although usually still visible.

3 shows a three-dimensional view of the storage frame 8th of the bearing body 2 according to 1 , with the bearing shells 6th as positioned in the unloaded state, so it exists between the bearing shells 6th the distance 14th in the circumferential direction Um. In 3 is the elastomer body 10 not shown, and instead of the fluid channel 22nd is the one in the bearing cups 6th trained recess 38 shown in which the fluid channel 22nd is formed and which the fluid channel 22nd supports or stiffens. So is the inner sleeve 12 Not shown.

The bearing shells 6th seen in the axial direction Ax each have a recess approximately in the middle 40 on. The end edge in the circumferential direction Um of the respective recess 40 runs parallel to the longitudinal plane BB , with the end edges 16 of the bearing shells 6th in the area of the respective return jump 40 are offset in mutually opposite circumferential directions Um that the distance 14th between the end edges 16 of the bearing shells 6th in the area of the respective return jump 40 is made larger than in the other areas. The longitudinal plane BB is shown here as a section from its three-dimensional view, i.e. as a spatially viewed rectangular section, with a dash-dotted line.

The expansion 42 of the return 40 in the axial direction Ax is greater than an extension of the depression 38 or the (not shown) fluid channel 22nd in the axial direction Ax in the area of the recess 40 .

In 4th and 5 each is a half-cross section of a front view of the bearing body 2 or the hydroelastic bearing 1 according to 1 shown, whereby the section profile corresponds to that in 1 specified course for the transverse plane AA follows. The half-cross section thus runs through the bridging section 26th and through the fluid channel 22nd . In contrast to 1 is the hydroelastic bearing 1 in 5 with outer sleeve 4th shown.

4th shows the bearing body 2 in the unloaded state and 5 shows the hydroelastic bearing 1 in the assembled state.

The elastomer body also shown in section 10 has different functional sections: a connecting section 44 , by means of which in particular the inner sleeve 12 and the bearing frame 8th are elastically connected, a fluid chamber portion 46 , by means of which fluid chambers are formed separately from one another 28 are formed, a fluid channel section 48 , by means of which the fluid chambers formed separately from one another 28 are fluidically connected to one another, a spring section 50 , by means of which the displacement of the inner sleeve 12 relative to the outer sleeve 4th is enabled, a sealing portion 52 , by means of which the bearing frame 8th , especially the fluid chambers 28 and the fluid channel 22nd , against an inner surface of the outer sleeve 4th is sealed, a stop portion 54 , by means of which a stop of the stop element 18th to the outer sleeve 4th is damped and the bridging section 26th , by means of which the distance 14th or the gap 24 between the bearing shells 6th is bridged. At least part of the sealing portion 52 runs on both sides along the fluid channel 22nd and seals the fluid channel 22nd also in its course over the bridging section 26th from. Ie the fluid channel 22nd is on the bridging section 26th not divided but has a continuous course. In that the bridging section 26th is formed from an elastomer, it can together with the fluid channel 22nd and the sealing portion 52 be deformed so that the sealing portion 52 the fluid channel 22nd reliably seals in the assembled state and also during operation.

The bridging section 26th fills the gap 14th in the circumferential direction around between the bearing shells 6th in the central area of the bearing body in the axial direction Ax 2 out. The distance 14th in the unloaded state in 4th is greater than the distance 14th in the assembled state in 5 .

The bridging section 26th fills the gap 24 viewed in the axial direction Ax only in the area of the fluid channel 22nd out. As above too 3 is the extent of the return 40 in the axial direction Ax greater than the extension of the recess 38 or the fluid channel 22nd in the axial direction Ax in the area of the recess 40 . Thus, viewed in the axial direction Ax is in each case on the Bridging section 26th an in 3 shown recording room 56 in the bearing shell 6th educated.

The material of the between the compressed bearing shells 6th squeezed bridging section 26th is from the return 40 or that of the return 40 formed recording space 56 in the bearing shell 6th at least partially included. Local deformations of the bridging section 26th or the fluid channel 22nd in the bridging section 26th can thus be reduced or avoided, whereby in particular a cross section of the fluid channel 22nd is essentially retained, so the contour of the fluid channel 22nd essentially not changed, although the fluid channel 22nd or the bridging section 26th when pressing the bearing shells together 6th is pressed together for the assembled state.

As in 6th in a three-dimensional view of the two bearing shells designed as half-shells 6th of the bearing body 2 according to 1 shown are the two bearing shells 6th designed identically to each other, which is the case with the illustration of the two bearing shells 6th easier to see in the same orientation.

The two bearing shells 6th are in particular identical with regard to the formation of their end edges 16 with the return 40 , the deepening 38 and the stop recess 20th . When assembling the two bearing shells 6th becomes one of the bearing shells 6th rotated by 180 ° around one of the spatial axes Ra shown and around the spatial axis Ax, so that the raised steps 36a and the recessed levels 36b be joined together, resulting in a form fit in the axial direction Ax.

The bearing shells 6th can be made of plastic, aluminum or other materials that allow the production of voluminous components, for example including variable wall thicknesses, depressions, elevations, etc., whereby the production can also include additive processes.

There can be symmetrical as well as asymmetrical bearing shells 6th are manufactured by means of plastic injection molding, with the bearing shells already during injection molding 6th can be connected via at least one film hinge or film joint, so that the bearing shells belonging to one another 6th when inserted into the vulcanization mold can only be joined by folding. The manufacturing process can be further simplified due to the lower number of components and the elimination of sorting.

7th shows a three-dimensional view of one of the bearing shells 6th of the bearing body 2 according to 1 with a view of their end edges 16 .

The return 40 is only at the end edge 16 on one side of the bearing shell 6th educated. The one on one side of the bearing shell 6th on both sides to the return 40 adjacent intermediate sections 34 run parallel to the longitudinal plane, set back by the same amount BB , with the end edge 16 in the area of the return 40 also parallel to the longitudinal plane BB , but is set back even further. The end edge 16 on the other side of the bearing shell 6th runs in the central region of the bearing shell viewed in the axial direction Ax 6th continuously set back by the same amount parallel to the longitudinal plane BB .

The recessed levels 36b or the end sections 36 the end edge 16 run on both sides of the bearing shell 6th at one end 30th parallel to the longitudinal plane BB set back by an amount greater than that of the intermediate sections 34 . The elevated steps 36a or the end sections 36 the end edge 16 at the other end 32 run on both sides of the bearing shell 6th parallel to the longitudinal plane BB advanced.

Alternatively, the end section 36 the end edge 16 at one end 30th on one side of the bearing shell 6th parallel to the longitudinal plane BB run back and on the other side of the bearing shell 6th parallel to the longitudinal plane BB run forward. The end section 36 the end edge 16 at the other end 32 then runs on one side of the bearing shell 6th parallel to the longitudinal plane BB forward and on the other side of the bearing shell 6th parallel to the longitudinal plane BB set back so that the bearing shell 6th symmetrical to a transverse plane AA is that transverse to the longitudinal plane BB runs.

In the in 8th shown three-dimensional view of the cut hydrostatic bearing 1 is the bearing body 2 according to 1 with the outer sleeve 4th shown.

The inner sleeve 12 with the stop elements 18th is with material of the elastomer body 10 encapsulated or coated. The hollow cylindrical outer sleeve 4th is crimped radially inward at its axial ends to the bearing body 2 to fix positively and to achieve better fluid tightness.

List of reference symbols

1

Hydroelastic bearing

2

Bearing body

4th

Outer sleeve

6th

Bearing shell

8th

Storage frame

10

Elastomer body

12

Inner sleeve

14th

distance

16

End edge of the bearing shell

18th

Stop element

20th

Stop recess

22nd

Fluid channel

24

gap

26th

Bridging section

28

Fluid chamber

30th

an end region of the bearing shell

32

another end of the bearing shell

34

Intermediate section of the end edge

36

End section of the end edge

36a

increased level

36b

deepened level

38

deepening

40

Return

42

expansion

44

Connection section

46

Fluid chamber section

48

Fluid channel section

50

Spring section

52

Sealing section

54

Stop section

56

Recording room

A-A

Transverse plane

B-B

Longitudinal plane

Ax

Axial direction

Ra

Radial direction

Around

Circumferential direction

Claims (8)

Hydroelastic bearing (1), having a bearing body (2) and an outer sleeve (4) which is connected to the bearing body (2) and which surrounds the bearing body (2) in the radial direction (Ra), wherein the bearing body (2) has: an inner sleeve (12), a bearing frame (8) which surrounds the inner sleeve (12) in the radial direction (Ra), and an elastomer body (10) which elastically connects the inner sleeve (12) and the bearing frame (8) to one another, wherein the bearing frame (8) has at least two bearing shells (6), wherein the at least two bearing shells (6) are elastically connected to one another by means of the elastomer body (10) such that the at least two bearing shells (6) are at a distance (14) from one another in an unloaded state in the circumferential direction (Um) and wherein the distance (14) of the at least two bearing shells (6) from one another is reduced in a mounted state in which the bearing body (2) is mounted in the outer sleeve (4), wherein the elastomer body (10) in the circumferential direction (Um) between the at least two bearing shells (6) has a bridging section (26) which bridges the distance (14) between the at least two bearing shells (6), wherein the bearing body (2) has a fluid channel (22) on its outer surface in the radial direction (Ra) which fluidly connects at least two fluid chambers (28) formed separately from one another in the bearing body (2) and wherein the fluid channel (22) extends through the bridging portion (26). Hydroelastic bearing according to Claim 1 wherein the bearing body (2) has a gap (24) at least in sections in the circumferential direction (Um) between the at least two bearing shells (6). Hydroelastic bearing according to Claim 1 or 2 wherein at least one of the bearing shells (6) has a recess (40) in the circumferential direction (Um) in the area of the bridging section (26). Hydroelastic bearing according to one of the preceding claims, wherein the bearing shells (6) are each identical to one another. Hydroelastic bearing according to one of the preceding claims, wherein the bearing frame (8) has two bearing shells (6) which are designed as half shells. Hydroelastic bearing according to one of the preceding claims, wherein the inner sleeve (12) has a stop element (18) which protrudes in the radial direction (Ra) from the inner sleeve (12) and a radial displacement of the inner sleeve (12) relative to the outer sleeve (4) limited. Hydroelastic bearing according to Claim 6 wherein the bearing shells (6) have a stop recess (20) in order to allow the stop element (18) to strike the inner surface of the outer sleeve (4). Method for providing the hydroelastic bearing according to one of the preceding Claims 1 to 7th , with the steps: forming the bearing frame (8) with at least two bearing shells (6), elastic connection of the at least two bearing shells (6) with the elastomer body (10) such that the at least two bearing shells (6) in an unloaded state in the circumferential direction (To) have a distance (14) from one another, mounting the at least two bearing shells (6) in the outer sleeve (4) in such a way that the distance (14) of the at least two bearing shells (6) from one another is mounted in one in the outer sleeve (4) State of the bearing body (2) is reduced, provision of a bridging section (26) in the circumferential direction (Um) on the elastomer body (10) between the at least two bearing shells (6), the bridging section (26) the distance (14) between the at least two Bearing shells (6) bridged and provision of a fluid channel (22) on a surface of the bearing body (2) lying outside in the radial direction (Ra), the fluid channel (22) separating at least two in the bearing body (2) fluidly connects fluid chambers (28) formed from one another with one another, the fluid channel (22) running through the bridging section (26).

Images