DE102017111667B4 - Bearing bush - Google Patents

Abstract

Bearing bush (10) comprising a core (11), an outer sleeve (16) surrounding the core (11) and an elastomer body (13) arranged between the core (11) and the outer sleeve (16), the outer sleeve (16) at least three Projections (21) and the core (11) has at least three counter-projections (22) which overlap in a radial direction with the projections (21) to limit an axial movement of the outer sleeve (16) relative to the core (11), the elastomer body (13) is partially spaced from the outer sleeve (16) and / or from the core (11) by a gap (24), the gap (24) in the axial direction between the projections (21) and / or between the counter-projections (22) is arranged, wherein the gap (24) is arranged on a bottom of a groove extending in the circumferential direction, which is formed by the projections (21) and / or counter-projections (22), wherein a region of the elastomer body (13) , which is between the projection (21) and the Gegenvorsp tion (22) extends in the radial direction, is compressed in the axial direction, and wherein the core (11) comprises a core element (11a) and an intermediate sleeve (12), the intermediate sleeve (12) being rotatably supported on the core element (11a) and the mating projections (22) are provided on the intermediate sleeve (12).

Description

The invention relates to a bearing bushing with a core, an outer sleeve surrounding the core and an elastomer body arranged between the core and the outer sleeve. The outer sleeve has at least three projections and the core has at least three counter-projections which overlap in a radial direction with the projections in order to limit an axial movement of the outer sleeve with respect to the core.

The high stiffness of elastomer bearings is helpful for precise wheel kinematics, direct and precise steering behavior and the associated driving safety. However, the rigidity of conventional chassis bushings often cannot achieve the desired values, particularly in the axial load direction. High axial stiffness can usually only be achieved by external, pre-tensioned axial stops. However, these can cause noise problems and / or wear out prematurely.

It is known from the prior art to provide a toothing between the outer sleeve and the core, by means of which the axial rigidity can be significantly increased. In particular, by increasing the number of projections and counter projections, the axial rigidity can be increased significantly. Bearing bushes with a toothed outer contour are, for example, in the EP 0 654 617 B1 or the U.S. 2,962,311 A described.

EP 0 524 843 A1 discloses a bearing bushing in which an outer sleeve for axially fixing the core is crimped around two projections protruding from the core. FR 1 207 040 A deals with a large number of different suspensions, for example for a bearing bush. U.S. 2,300,013 A deals with a torsion connection in which the outer sleeve is pressed together to compress the elastomer body. US 2015/0 298 517 A1 deals with a bearing that comprises an ankle and a socket. U.S. 3,731,896 A looks at an engine mount. DE 198 59 152 C1 discloses a pivot bearing with a pivot bushing comprising a steel tube and a rubber layer. A plain bearing tube is positively attached to the steel tube. DE 733 768 A deals with a bearing for aircraft engines, which is supposed to absorb vibrations in all directions.

The object of the invention is to provide a bearing bush which has a high axial rigidity without the increase in the axial rigidity being accompanied by an excessive increase in the radial rigidity.

This object is achieved by the subject matter of claim 1. The dependent claims describe preferred embodiments of the invention.

A bearing bushing comprises a core, an outer sleeve surrounding the core and an elastomer body arranged between the core and the outer sleeve. The outer sleeve has at least three projections and the core has at least three counter-projections, the counter-projection overlapping in a radial direction with the projections to limit an axial mobility of the outer sleeve relative to the core. The elastomer body is partially spaced from the outer sleeve and / or from the core by a gap. The gap is arranged in the axial direction between the projections and / or between the mating projections. The gap is arranged on a bottom of a groove which extends in the circumferential direction and is formed by the projections and / or counter projections. A portion of the elastomer body which extends between one of the projections and one of the counter projections in the radial direction is compressed in the axial direction. The core comprises a core element and an intermediate sleeve, the intermediate sleeve being rotatably mounted on the core element and the projections being provided on the intermediate sleeve.

In conventional bearing bushes, the increase in axial rigidity due to the provision of several projections and counter-projections is accompanied by an increase in the radial rigidity of the bearing bush. The gap is provided to compensate for this increase in radial rigidity.

The bearing bush can be installed, for example, in a leaf spring eye bearing of a passenger car or a truck. For this purpose, for example, the core is screwed to the body and the outer sleeve is pressed into the leaf spring eye.

The core can for example have a bore extending in an axial direction into which a bolt can be inserted in order to connect the bearing bush to the motor vehicle. The direction of the axial bore can coincide with an axis of rotation of the core or the bearing bush. The core is made of a metallic material, plastic or polyamide, for example.

The circumferential direction forms a cylindrical coordinate system with the axial direction and the radial direction, so that base vectors of the circumferential direction, the radial direction and the axial direction are perpendicular to one another.

The outer sleeve surrounds the core preferably extending in a circumferential direction. The outer sleeve is preferably designed in several parts, preferably in two parts, the two parts of the outer sleeve being designed as half-shells. It is optionally provided that the outer sleeves are applied to the elastomer body and / or the core as the last method step. The multi-part design of the outer sleeve is particularly helpful when assembling the outer sleeve on the core, if the core and the outer sleeve are provided with a tooth system by the projections and the counter-projection. The outer sleeve can also be made of metal or a plastic. The two half-shells of the outer sleeve can be connected to one another by one or more hinges; in particular if the half-shells are made of plastic, the hinge can be implemented as a film hinge.

The elastomer body is arranged between the outer sleeve and the core and serves to decouple the vibrations of the outer sleeve from the core. In particular, the elastomer body extends completely around the core in the circumferential direction. However, it is also possible for the elastomer body to be designed in several parts, with free spaces preferably being provided between the individual parts. For example, the individual parts of the elastomer body are distributed evenly in the circumferential direction.

The at least three projections of the outer sleeve optionally form a groove extending in the circumferential direction, in which a counter-projection engages in the radial direction. This means that the projections and the counter-projection overlap in the radial direction, so that a movement of the counter-projection is limited in the axial direction within the groove of the projections. Due to the provision of the projections and the counter-projection, the axial rigidity of the bearing bush can be increased. There are more than three projections and mating projections. This can also be understood as the interlocking of the outer sleeve with the core. The more projections and mating projections are provided on the bearing bush, the more the axial rigidity of the bearing bush increases.

The elastomer body preferably runs along the contour of the projections and / or mating projections, so that the elastomer body is compressed with respect to the mating projection when the projection moves in the axial direction.

The gap extends at least partially along the outer sleeve and / or the core in the axial direction. A plurality of gaps are preferably provided, which are provided at a distance from one another in the axial direction, for example. The gap can also be viewed as a free space. In particular, the gap is filled with a gas, for example air; however, the gap can also be completely or partially filled with a lubricant, for example a fat. The gap optionally extends completely in the circumferential direction, it also being possible for the gap to be interrupted in the circumferential direction, for example by the elastomer body.

By providing the gap, the elastomer body does not lie completely against the outer sleeve and / or the core, so that in the event of vibrations whose amplitude is less than a thickness of the gap in the radial direction, a freewheel occurs in which the elastomer body, the is arranged in the radial direction adjacent to the gap, does not contribute to the radial rigidity.

In particular, if several gaps spaced apart in the axial direction are provided, when radial vibrations act on the bearing bush, the result is that initially only areas of the elastomer body are compressed in which no gap is provided when viewed in the radial direction. Only when the amplitude of the vibration exceeds the thickness of the gap in the radial direction does the elastomer body act in its entire axial extent. Accordingly, for vibrations whose amplitude is smaller than the radial thickness of the gap, a lower rigidity results than for vibrations whose amplitude is greater than the thickness of the gap in the radial direction. In this way, on the one hand, a lower radial rigidity can be set for small amplitudes of the vibration, so that the link known from the prior art between the increase in the axial rigidity and the associated increase in the radial rigidity can be canceled. In addition, a progressive radial stiffness profile of the bearing bush can also be set.

This means that the gap is arranged in particular in the groove formed by the projections and / or the counter-projections, in particular on the bottom of the groove which is formed by the projections and / or counter-projections. For example, the gap is only arranged between the counter-projections or the projections. In the groove in which there is no gap, the elastomer body preferably rests against the projection or counter-projection protruding into the groove. Thus, in the event of a radial deflection of the bearing bush relative to the core element, the elastomer body is initially not effective in the area of the grooves in which the gap is not arranged. Rather, only the elastomer body contributes to the rigidity in the area of the grooves without a gap and between the flanks of the projections and mating projections. Only with a radial deflection which is greater than the thickness of the gap in the radial direction Direction, the elastomer body also acts in the grooves in which a gap is arranged. In this way, with small radial deflections, a lower rigidity results than with larger radial deflections, whereby a progressive course can be set.

It is preferred that the elastomer body has at least one additional cushion which extends into the gap.

The additional cushion can extend completely into the gap along the circumferential direction or be arranged in sections in the circumferential direction. The additional cushion is optionally assigned to each gap. In an axial cross section, that is, viewed in the circumferential direction, the additional cushion has an area which is smaller than the gap when no additional cushion is provided. This means that, compared to the provision of a gap, more volume of the elastomer body is effective in the radial direction and, compared to the omission of the gap, less volume of the elastomer body is effective in the radial direction.

The additional cushion preferably rests on the outer sleeve or on the core. In this embodiment, there is a rigidity in the radial direction which is less than when no gap is provided, but which is greater than when a gap is provided. The stiffness curve of the bearing bush can thus be varied by the additional padding.

Optionally, a gap is provided both in the grooves of the projections and in the grooves of the counter-projections, an additional cushion being assigned to each gap. A configuration that is softer in the radial direction compared to this embodiment is obtained when the additional padding is provided in one configuration of the gaps both in the groove of the projections and in the groove of the counter-projections only in the grooves of the projections or alternatively in the grooves of the counter-projections is.

It is preferred that the additional cushion has an outer contour that is convexly arched in cross section.

The cross section can be seen in particular along a plane running in the axial direction. With such a configuration of the additional cushion, the radial deflection of the outer sleeve with respect to the core increases the effective area of the elastomer body that is compressed. In this way, the rigidity of the bearing bush increases progressively in the radial direction.

In particular, the area of the elastomer body which is compressed in the event of an axial deflection of the outer sleeve with respect to the core is pretensioned. This means that in a non-assembled state of the bearing bush, for example when the outer sleeve is not yet provided and thus the projection is not inserted into the groove of the counter-projection, the thickness of the elastomer body is greater than in comparison when the bearing bush is completely assembled. In other words, the thickness of the elastomer body in the area in which the elastomer body contributes to the axial rigidity is greater than the distance between the projection and the counter-projection measured in an axial direction. The region of the elastomer body which contributes to the axial rigidity runs essentially parallel to the radial direction, that is to say the region of the elastomer body runs on axial side surfaces of the projection and / or the counter-projection. By pretensioning the elastomer body in this area, the axial rigidity can be increased further, since the elastomer body is already pre-compressed. The flank of the projection and / or the counter-projection can also be referred to as an axial side surface.

It is preferred that the elastomer body has at least one sealing lip in order to seal the gap. It is further preferred that the elastomer body is fastened to the core, for example in a materially bonded manner by vulcanization, with the sealing lip preferably resting against the outer sleeve. Alternatively, it is preferred that the elastomer body is firmly attached to the outer sleeve, for example by vulcanization of the elastomer body on the outer sleeve.

Optionally, the outermost projections of the toothing are not formed by the projections on the outer sleeve, but by the counter-projections of the core. That is to say, the outer sleeve has a first axial end region at one axial end and a second axial end region on which no projection is provided at the other axial end. If the gap is provided at the first axial end area and at the second axial end area, it is open to the outside so that dirt can penetrate into the gap. To avoid this, the sealing lip is provided on the elastomer body, which bridges the gap in the radial direction of the elastomer body and either, if the elastomer body is attached to the intermediate sleeve, in the direction of the outer sleeve or, if the elastomer body is attached to the outer sleeve , protrudes in the direction of the intermediate sleeve. The sealing lip thus rests with its free end on the corresponding mating surface.

By providing the sealing lip, the penetration of dirt can be prevented in a particularly simple manner and thus a gap itself be provided at the outer axial ends of the bearing bush, so that a particularly low rigidity can be provided in the radial direction. The sealing lip is preferably made of the same material as the elastomer body.

It is preferred that the projections and / or the counter-projection extend essentially perpendicular to the axial direction of the bearing bush.

In particular, the axial side surfaces of the projections and / or of the counter-projection extend essentially perpendicular to the axial direction, that is to say essentially parallel to the radial direction. Essentially means that a deviation of up to ± 25 °, in particular up to ± 15 °, is possible. The extension of the axial side surface of the projection and of the counter-projection perpendicular to the axial direction enables a particularly high axial rigidity. In particular, the axial side surface of the projection is arranged to run parallel to the axial side surface of the adjacent counter-projection. The area of the elastomer body which contributes to the axial rigidity and is compressed in a preferred embodiment is arranged between these axial side surfaces.

Another aspect of the invention relates to a method for producing the above-described bearing bushing, the elastomer body being connected to the core in a first method step, in particular being vulcanized onto it. In a second process step, the outer sleeve is then attached to the elastomer body. This procedure makes it possible to design the outer contour of the elastomer body, that is to say the surface of the elastomer body which faces the outer sleeve, with a particularly high degree of design freedom. In particular, it is possible to provide the additional cushion with a particularly high degree of design freedom, for example its outer contour. In this way, a bearing bush can be produced in which the gap is arranged between the outer sleeve and the elastomer body and the additional cushion protrudes radially outward from the elastomer body into the gap.

The core has a core element and an intermediate sleeve, the intermediate sleeve being rotatably mounted on the core element. In this case, a bearing gap can be provided between the intermediate sleeve and the core element, due to which the intermediate sleeve is rotatably mounted on the core element in the circumferential direction. To limit the axial mobility of the intermediate sleeve, a stop device can be connected to the core element at the axial ends. The stop device can be designed, for example, as two ring disks which are pressed onto the core element at the axial ends of the core element.

It is preferred that the elastomer body is materially connected, in particular vulcanized, to the core, in particular the intermediate sleeve. Alternatively, the elastomer body can be positively and / or cohesively connected to the outer sleeve or on a side facing the core to a solid substrate, such as an intermediate body. The elastomer body is vulcanized onto the outer sleeve, for example. In particular, the elastomer body is connected to the two half-shells, so that the elastomer body, in particular also an existing sealing geometry, is composed of two partial areas. The outer sleeve and the elastomer body are then applied to the core.

• 1 eine schematische Querschnittsdarstellung einer ersten Ausführungsform einer Lagerbuchse;
• 2 eine schematische Querschnittsdarstellung einer zweiten Ausführungsform der Lagerbuchse
• 3 einen vergrößerten Ausschnitt eines Teils der Lagerbuchse gemäß 1;
• 4 ein der 3 entsprechender Ausschnitt einer Lagerbuchse gemäß einer dritten Ausführungsform; und
• 5 eine der 3 entsprechender Ausschnitt einer Lagerbuchse gemäß einer vierten Ausführungsform.

The invention is explained in more detail with reference to the accompanying drawings. Show in it:

• 1 a schematic cross-sectional view of a first embodiment of a bearing bush;
• 2 a schematic cross-sectional view of a second embodiment of the bearing bush
• 3 an enlarged section of part of the bearing bush according to 1 ;
• 4th one of the 3 corresponding section of a bearing bush according to a third embodiment; and
• 5 one of the 3 Corresponding section of a bearing bush according to a fourth embodiment.

A bearing bush 10 has a core 11 , an outer sleeve 16 and an elastomer body 13th on. In the in 1 illustrated embodiment of the bearing bush 10 is the core 11 integrally formed and made for example of metal. The core 11 optionally has a bore through which a bolt can be inserted, by means of which the bearing bushing 10 can be attached to a vehicle.

The core 11 has a large number of counter-projections 22nd on, which in the radial direction to the outer sleeve 16 protrude. The counter projections 22nd have axial side surfaces which are arranged essentially perpendicular to the axial direction or, in other words, parallel to the radial direction. However, a deviation of up to ± 25 °, in particular up to ± 15 °, from the radial direction is possible. The face of the mating projections 22nd , that is, the area of the counter-projections 22nd extending in a circumferential direction is preferably parallel to the outer sleeve 16 arranged.

The outer sleeve 16 is used to fasten the bearing bush 10 with the vehicle. For example, the outer sleeve 16 inserted into a bearing eye. The outer sleeve 16 is preferably composed of two half-shells, which together form the core 11 completely surrounded in the circumferential direction. In the in 1 The view shown is the parting plane of the half-shells exactly in the cutting plane of the drawing; hence the outer sleeve 16 shown without hatching. The half-shells of the outer sleeve 16 can be connected to one another by one or more hinges. This is not shown in the figures.

The outer sleeve 16 has a multitude of protrusions 21 on that in the radial direction of the core 11 facing. The axial side surfaces of the protrusions 21 are analogous to the counter-projections 22nd arranged essentially parallel to the radial direction and are used to set the rigidity ratios of the bearing bush 10 .

The protrusions 21 and / or the counter-projections 22nd preferably extend completely along the circumferential direction. Likewise analogous to the counter-projections 22nd are the end faces of the projections 21 parallel to the axial direction and parallel to the core 11 . This means that the axial side surfaces of the projections 21 and the mating protrusions 22nd as well as the end faces of the projections 21 and the mating protrusions 22nd are arranged parallel to each other. Two ledges 21 and two counter projections 22nd each form a groove into which the other of the projections 21 and counter projections 22nd intervenes. For example, it engages through two projections 21 formed groove a mating projection 22nd a. This means that the protrusions 21 and the mating protrusions 22nd overlap in the radial direction so that a deflection of the outer sleeve 16 opposite the core 11 in the axial direction through the protrusions 21 and counter projections 22nd is limited. Through the ledges 21 and the mating protrusions 22nd a toothing is thus provided.

The elastomer body 13th is in the in 1 illustrated embodiment on the core 11 vulcanized and extends along the contour of the counter-projections 22nd . Like this in particular 3 can be clearly seen is between the elastomer body 13th and the outer sleeve 16 A gap 24 intended. In particular, there are multiple columns 24 provided at the bottom of the by the projections 21 grooves formed and on the end faces of the projections 21 are arranged.

Furthermore, the outer sleeve 16 optionally a first axial end region 16a and a second axial end region 16b on, which is also from the elastomer body 13th through the gap 24 is spaced. This column 24 are each by one on the elastomer body 13th trained sealing lip 15th locked. The sealing lip 15th stands in the radial direction in the direction of the outer sleeve 16 and is located at the first axial end region 16a or in the second axial end region 16b at. The sealing lip 15th preferably extends completely in the circumferential direction.

As is particularly the case in 3 can be seen are column 24 between the elastomer body 13th and an end face of the protrusion 21 and the counter projection 22nd provided, in particular a gap is provided 24 on each face between the protrusion 21 as well as the counter projection 22nd and the elastomer body 13th intended. That is, in each one through the protrusions 21 and the mating protrusions 22nd formed groove is a gap 24 provided, the gap 24 between the elastomer body 13th and the outer sleeve 16 is arranged.

In the gap 24 that of the face of the protrusion 21 is adjacent is an additional pad 26th provided that is different from the elastomer body 13th in the gap 24 extends into it. The additional cushion 26th has a convex outer contour in cross section 26a on. The additional cushion 26th preferably touches the face of the projection 21 .

An area of the elastomer body 13th , which extends in the radial direction between the respective projection 21 and the respective counter projection 22nd extends is compressed. This means that when the outer sleeve 16 not provided is the thickness of the elastomer body 13th is larger (see dashed line in 3 ) than if the outer sleeve 16 is provided. The thickness of the elastomer body 13th in the axial direction is greater than the distance between the axial side surfaces of the projection 21 and the counter projection 22nd .

The compression of the area of the elastomer body 13th , which contributes to the axial rigidity, tensions the elastomer body 13th in the axial direction so that the axial rigidity can be increased. The axial stiffness of the bearing bush 10 is also increased compared to known bearing bushes, as a large number of projections 21 and counter projections 22nd is provided. In particular, the bearing bush 10 more than three protrusions 21 and counter projections 22nd on. By such a toothing of the projections 21 and counter projections 22nd a particularly high radial rigidity can be achieved.

The lead 21 stands so far towards the core in the radial direction 11 before that it is in the radial direction with the mating projection 22nd overlaps. In other words, there is the opposite projection 22nd from the core 11 so far in the direction of the outer sleeve 16 before that he was with the lead 21 overlaps.

The provision of the gap 24 allows the radial stiffness of the bearing bush 10 to reduce. In this way, the increase in radial rigidity associated with the increase in axial rigidity can be compensated for. In particular with vibrations in the radial direction with an amplitude that is smaller than the thickness of the gap 24 is in the radial direction, only the auxiliary pad becomes 26th or that of the additional cushion 26th adjacent area of the elastomer body 13th compressed.

Furthermore, the greater the radial deflection of the outer sleeve increases 16 opposite the core 11 the area of the additional pad 26th , which on the outer sleeve 16 is present. In this way, a progressive course of the radial rigidity can be provided. Only when the amplitude of the vibrations in the radial direction is greater than the thickness of the gap 24 is in the radial direction, carries the complete elastomer body 13th contributes to the rigidity in the radial direction. In this way, for vibrations with a small amplitude in the radial direction, a significant reduction in the radial rigidity can be undertaken.

The gap 24 thus creates a certain amount of freedom. With the additional padding 26th a progressive stiffness curve can be achieved. In an embodiment not shown in the figures, the bearing bush 10 according to 1 and 3 modified in such a way that no additional padding 26th is provided. In this way, vibrations act in the radial direction with an amplitude smaller than the thickness of the gap 24 in the radial direction no or only small areas of the elastomer body 13th so that a particularly low rigidity can be set.

The bearing bush 10 according to 2 agrees with the bearing bush 10 according to 1 except for the following differences. The core 11 settles according to the embodiment of 2 from a core element 11a and an intermediate sleeve 12th together. The intermediate sleeve 12th is on the core element 11 a rotatably arranged. A bearing gap, for example, can be used for this purpose 18th be provided, which is optionally filled with lubricant. The protrusions 22nd are thus on the intermediate sleeve 12th provided, which can be made of plastic.

Because the intermediate sleeve 12th on the core element 11a is rotatably mounted, the intermediate sleeve 12th in the axial direction with respect to the core element 11a move. About the axial mobility of the intermediate sleeve 12th to limit is an anchor device 17th intended. The anchor device 17th can be integral with the core element 11a be designed, for example as a circumferential flange. In the in 2 The embodiment shown is the stop device 17th as a first washer 17a and a second washer 17b formed, each on the core element 11a are pressed on at the axial ends. Around the area between the anchorage device 17th and the intermediate sleeve 12th to increase is the bearing bush 10 designed such that the outer elements of the toothing between the bearing sleeve 16 and the core 11 on the spacer 12th are trained. The counter projections 22nd , which are arranged at the axial ends, can also be used as the first limiting projection 12a and second limiting protrusion 12b are designated. The first limiting ledge 12a and the second limiting protrusion 12b differ in their contour from the other counter-projections 22nd . In particular, the surface of the first or the second delimiting projection 12a , 12b , which of the anchorage device 17th facing across the bearing gap 18th parallel to the anchor device 17th arranged.

In the in 2 The illustrated embodiment have the projections 21 and / or the counter-projections 22nd axial side surfaces which are not parallel to the radial direction, but for example deviate by 10 °, but at most 25 ° from the radial direction.

In addition, the gap is 24 exclusively in the through the projections 21 formed grooves provided. In the through the counter projections 22nd formed grooves is not a gap 24 provided because there the elastomer body 13th on the projections 21 is present. This means that with a radial deflection, the amplitude of which is smaller than the radial thickness of the gap 24 , the elastomer body 13th only in the area of the groove of the counter-projections 22nd is compressed. Compared to a deflection in the radial direction that is greater than the thickness of the gap 24 is in the radial direction, thus only a portion of the elastomer body acts 13th . In this way, a progressive course of the stiffness can be achieved.

In addition, the in 2 shown section through the outer sleeves 16 ; therefore these are provided with hatching.

In the 4th Shown embodiment of the bearing bush 10 agrees with the in 1 embodiment shown. The only difference is that the additional padding 26th not between two counter-projections 22nd is provided, but between two projections 21 . Because the distance between two protrusions 21 greater than the distance between two counter-projections 22nd can use the additional cushions 26th be made wider; a harder rigidity in the radial direction can thus be set.

In the 5 Shown embodiment of the bearing bush 10 agrees with the in 4th embodiment shown except for the fact that the elastomer body 13th with the outer sleeve 16 is connected and not to the core 11 . For example, the elastomer body 13th on the outer sleeve 16 be vulcanized. The gap 24 is thus between the elastomer body 13th and the core 11 provided, the additional cushion 26th radially inwards into the gap 24 protrudes. Also the sealing lip 15th stands radially inward from the elastomer body 13th before and is at the core 11 at.

List of reference symbols

10

Bearing bush

11

core

11a

Core element

12th

Intermediate sleeve

12a

first limiting ledge

12b

second limiting protrusion

13th

Elastomer body

15th

Sealing lip

16

Outer sleeve

16a

first axial end area

16b

second axial end area

17th

Anchor device

17a

first washer

17b

second washer

18th

Bearing gap

21

head Start

22nd

Counter advantage

24

gap

26th

Additional padding

26a

Outer contour

Claims (7)

Bearing bush (10) comprising a core (11), an outer sleeve (16) surrounding the core (11) and an elastomer body (13) arranged between the core (11) and the outer sleeve (16), wherein the outer sleeve (16) has at least three projections (21) and the core (11) has at least three counter-projections (22), which in a radial direction with the projections (21) to limit an axial movement of the outer sleeve (16) relative to the core (11) overlap, wherein the elastomer body (13) is partially spaced from the outer sleeve (16) and / or from the core (11) by a gap (24), wherein the gap (24) is arranged in the axial direction between the projections (21) and / or between the counter-projections (22), wherein the gap (24) is arranged on a bottom of a groove extending in the circumferential direction which is formed by the projections (21) and / or counter projections (22), wherein a portion of the elastomer body (13) which extends between the projection (21) and the counter projection (22) in the radial direction is compressed in the axial direction, and wherein the core (11) comprises a core element (11a) and an intermediate sleeve (12), the intermediate sleeve (12) being rotatably mounted on the core element (11a) and the counter-projections (22) being provided on the intermediate sleeve (12). Bearing bushing Claim 1 , characterized in that the elastomer body (13) has at least one additional cushion (26) which extends into the gap (24). Bearing bushing Claim 2 , characterized in that the additional cushion (26) has an outer contour (26a) which is convexly arched in cross section. Bearing bush according to one of the preceding claims, characterized in that the elastomer body (13) has at least one sealing lip (15) in order to seal the gap (24). Bearing bush according to one of the preceding claims, characterized in that the projections (21) and / or the counter-projections (22) extend essentially perpendicular, but at most at an angle of 25 °, to the axial direction of the bearing bush (10). Bearing bush according to one of the preceding claims, characterized in that the elastomer body (13) is integrally connected, in particular vulcanized, to the core (11) or the outer sleeve (16). Bearing bush according to one of the preceding claims, characterized in that the outer sleeve (16) is constructed in several parts, preferably in two parts in the form of half-shells, wherein preferably the parts of the outer sleeve (16) are connected to one another by means of a hinge.

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