DE102017111667A1 - bearing bush - Google Patents

Abstract

The invention relates to a bearing bush (10) which has 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) has at least two projections (21) and the core (11) at least one counter-projection (22), which in a radial direction with the projections (21) for limiting an axial movement of the outer sleeve (16) relative to the core (11) overlaps. The elastomeric body (13) is partially spaced from the outer sleeve (16) and / or from the core (11) by a gap (24).

Description

The invention relates to a bearing bush 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 two projections and the core at least one counter-projection which overlaps in a radial direction with the projections for limiting an axial movement of the outer sleeve relative to the core.

High stiffnesses of elastomeric bearings are useful for precise wheel kinematics, direct and precise steering performance and related driving safety. In particular, in the axial direction of loading, however, the stiffness of conventional suspension bushes often can not achieve the desired values. High axial stiffnesses can usually only be achieved by external, preloaded axial stops. However, these can cause noise problems and / or prematurely wear out.

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

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

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

A bushing includes a core, an outer sleeve surrounding the core, and an elastomeric body disposed between the core and the outer sleeve. The outer sleeve has at least two projections and the core at least one counter-projection, wherein the counter-projection overlaps in a radial direction with the projections for limiting axial mobility of the outer sleeve relative to the core. The elastomeric body is partially spaced from the outer sleeve and / or from the core by a gap.

In conventional bushings, increasing the axial rigidity by providing a plurality of protrusions and counter protrusions also increases the radial rigidity of the bushing. To compensate for this increase in radial stiffness, the gap is provided.

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

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

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 each other.

The outer sleeve preferably surrounds the core extending in a circumferential direction. The outer sleeve is preferably multi-part, preferably in two parts, designed, wherein the two parts of the outer sleeve are formed as half shells. It is optionally provided that the outer sleeves are applied as the last method step to the elastomer body and / or the core. The multi-part design of the outer sleeve is helpful in particular when mounting the outer sleeve to the core when the core and the outer sleeve are provided by the projections and the counter-projection a toothing. The outer sleeve may also be made of metal or a plastic. The two half shells of the outer sleeve can be connected to each other by one or more hinge; In particular, when the half-shells are made of plastic, the hinge may be realized as a film hinge.

The elastomeric body is disposed between the outer sleeve and the core and serves for vibration isolation of the outer sleeve relative to the core. In particular, the elastomeric body extends completely in the circumferential direction around the core. However, it is also possible that the elastomeric body is designed in several parts, wherein free spaces are preferably provided between the individual parts. For example, the individual parts of the elastomer body are arranged distributed uniformly in the circumferential direction.

The at least two projections of the outer sleeve optionally form a circumferentially extending groove, in which engages the at least one counter-projection 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 in the axial direction within the groove of the projections is limited. Due to the provision of the projections and the counter-projection, the axial rigidity of the bearing bush can be increased. In particular, more than three protrusions and counter protrusions are provided. This can also be understood as a toothing of the outer sleeve with the core. The more protrusions and counter protrusions are provided in the bearing bush, the more increases the axial stiffness of the bearing bush.

Preferably, the elastomeric body extends along the contour of the projections and / or counter-projections, so that the elastomeric body is compressed in a movement of the projection in the axial direction relative to the counter-projection.

The gap extends at least partially along the outer sleeve and / or the core in the axial direction. Preferably, a plurality of gaps are provided, which are provided spaced apart, for example, in the axial direction. The gap can also be considered as a free space. In particular, the gap is filled with a gas, for example air; but the gap can also be wholly or partially filled with a lubricant, such as a grease. The gap optionally extends completely in the circumferential direction, it being also possible that the gap is interrupted in the circumferential direction, for example by the elastomeric body.

By providing the gap, the elastomeric body is not completely against the outer sleeve and / or the core, so that sets in vibrations whose amplitude is smaller than a thickness of the gap in the radial direction, a freewheel, wherein the elastomeric body, the is arranged in the radial direction adjacent to the gap, does not contribute to the radial stiffness.

In particular, when a plurality of gaps spaced in the axial direction are provided, the action of radial vibrations on the bearing bush results in a behavior that initially only areas of the elastomer body are compressed, in which case no gap is provided in the radial direction. Only when the amplitude of the vibration exceeds the thickness of the gap in the radial direction, the elastomeric body acts in its entire axial extent. Thus, for vibrations whose amplitude is smaller than the radial thickness of the gap, there is less rigidity than for vibrations whose amplitude is greater than the thickness of the gap in the radial direction. In this way, on the one hand for small amplitudes of the vibration, a lower radial rigidity can be set, so that the link known from the prior art between the increase of the axial rigidity and the associated increase in the radial rigidity can be canceled. In addition, a progressive radial stiffness curve of the bearing bush can also be adjusted.

It is preferable that the gap is arranged in the axial direction between the protrusions and / or between the counter protrusions.

This means that the gap is arranged in particular in the groove formed by the projections and / or the counter-projections, in particular at the bottom of the groove, which is formed by the projections and / or counter-projections. For example, the gap is arranged only between the counter-projections or the projections. In the groove, in which no gap is arranged, preferably the elastomeric body bears against the projection or counter-projection projecting into the groove. Thus, in the case of a radial deflection of the bearing bush relative to the core element, the elastomer body is initially not effective in the region of the grooves in which the gap is not arranged. Rather, only the elastomer body in the region of the grooves without gap and between the flanks of the projections and counter projections contributes to the rigidity. Only in the case of a radial deflection, which is greater than the thickness of the gap in the radial direction, does the elastomer body additionally act 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 elastomeric body has at least one additional cushion which extends into the gap.

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

The additional cushion is preferably on the outer sleeve or on the core. At this Design results in a stiffness in the radial direction, which is less than if no gap is provided, which is greater than when a gap is provided. The additional cushion allows the stiffness curve of the bearing bush to be varied.

Optionally, a gap is provided both in the grooves of the projections and in the grooves of the counter-projections, wherein each gap is associated with an additional cushion. A softer in the radial direction embodiment compared to this embodiment is obtained if provided in an embodiment of the column in both 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, the additional cushion is.

It is preferred that the additional cushion has a convexly convex outer contour in cross section.

The cross section can be seen in particular along a plane extending in the axial direction. In such an embodiment of the additional cushion increases with the radial deflection of the outer sleeve relative to the core, the effective area of the elastomeric body, which is compressed. In this way, progressively increases the rigidity of the bearing bush in the radial direction.

It is preferable that a portion of the elastomeric body which extends between the projection and the counterpart projection in the radial direction on its flanks is compressed in the axial direction.

In particular, the region of the elastomeric body, which is compressed in an axial deflection of the outer sleeve relative to the core, biased. This means that in an unassembled state of the bearing bush, for example, when the outer sleeve is not provided and thus the projection is not inserted into the groove of the counter-projection, the thickness of the elastomeric body is greater than in comparison, when the bearing bush is completely assembled. In other words, the thickness of the elastomer body in the region where the elastomer body contributes to the axial rigidity is larger than the distance between the protrusion and the counter protrusion measured in an axial direction. The portion of the elastomer body contributing to the axial rigidity is substantially parallel to the radial direction, that is, the portion of the elastomer body extends at axial side surfaces of the projection and / or the counter projection. By the bias of the elastomeric body in this area, the axial stiffness can be further increased because the elastomeric body is already precompressed. The flank of the projection and / or the counter-projection can also be referred to as the axial side surface.

It is preferred that the elastomeric body has at least one sealing lip to seal the gap. It is further preferred that the elastomeric body is attached to the core, for example by material bonding by vulcanization, wherein preferably the sealing lip rests against the outer sleeve. Alternatively, it is preferred that the elastomeric body is firmly bonded to the outer sleeve, for example by vulcanization of the elastomeric body to 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, the outer sleeve has a first axial end portion at one axial end and a second axial end portion at the other axial end where no protrusion is provided. If the gap is provided at the first axial end region and at the second axial end region, this gap is open towards the outside, so that dirt can penetrate into the gap. To avoid this, the sealing lip is provided on the elastomeric body, which bridges the gap from the elastomeric body in the radial direction and either, if the elastomeric body is mounted on the intermediate sleeve, in the direction of the outer sleeve or, if the elastomeric body is mounted on the outer sleeve , protrudes in the direction of the intermediate sleeve. The sealing lip thus lies with its free end against the corresponding counter surface.

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

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

In particular, the axial side surfaces of the projections and / or the counter-projection extend substantially perpendicular to the axial direction, that is, substantially 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 the counter-projection perpendicular to the axial direction allows a particularly high axial rigidity. In particular, the axial side surface of the projection is arranged parallel to the axial side surface of the adjacent counter projection. Between these axial side surfaces of the region of the elastomeric body is arranged, which contributes to the axial stiffness and is compressed in a preferred embodiment.

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

It is preferred that the core is integrally formed. In an alternative variant, it is preferred that the core has a core element and an intermediate sleeve, wherein the intermediate sleeve is rotatably mounted on the core element. In this variant, a bearing gap can be provided between the intermediate sleeve and the core element, due to which the intermediate sleeve is rotatably mounted in the circumferential direction on the core element. In order 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 annular disks, which are pressed onto the core element at the axial ends of the core element.

It is preferred that the elastomeric body is materially bonded to the core, in particular the intermediate sleeve, in particular vulcanized. Alternatively, the elastomeric body may be positively and / or materially connected to the outer sleeve or on a side facing the core to a fixed substrate, such as an intermediate body. The elastomeric body is vulcanized, for example, to the outer sleeve. In particular, the elastomer body is connected to the two half shells so that the elastomer body, in particular also an existing seal geometry, is composed of two subregions. The outer sleeve and the elastomeric 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 will be explained in more detail with reference to the accompanying drawings. Show:

• 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 a part of the bearing bush according to 1 ;
• 4 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 elastomeric body 13 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 bush 10 can be attached to a vehicle.

The core 11 has a plurality of opposing projections 22 on, which in the radial direction to the outer sleeve 16 protrude. The counterprojections 22 have axial side surfaces which are arranged substantially 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 counter projections 22 that is, the area of the counterprojections 22 that extends in a circumferential direction is preferably parallel to the outer sleeve 16 arranged.

The outer sleeve 16 serves 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 constructed 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; therefore, the outer sleeve 16 shown without hatching. The half-shells of the outer sleeve 16 can be connected by one or more hinges. This is not shown in the figures.

The outer sleeve 16 has a variety of protrusions 21 up in the radial direction to the core 11 projected facing. The axial Side surfaces of the projections 21 are analogous to the opposing projections 22 arranged substantially parallel to the radial direction and serve to adjust the rigidity of the bearing bush 10 ,

The projections 21 and / or the counterprojections 22 preferably extend completely along the circumferential direction. As well as the counter-projections 22 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 counterprojections 22 as well as the end faces of the projections 21 and the counterprojections 22 are arranged parallel to each other. Two tabs 21 and two opposing projections 22 each form a groove, in which the other of the projections 21 and counterprojections 22 intervenes. For example, engages in by two projections 21 formed groove a counter projection 22 one. This means that the protrusions 21 and the counterprojections 22 overlap in the radial direction, so that a deflection of the outer sleeve 16 opposite the core 11 in the axial direction through the projections 21 and counterprojections 22 is limited. Through the projections 21 and the counterprojections 22 Thus, a toothing is provided.

The elastomer body 13 is in the in 1 illustrated embodiment of the core 11 vulcanized and extends along the contour of the counter-projections 22 , How this particular out 3 is clearly visible, is between the elastomeric body 13 and the outer sleeve 16 A gap 24 intended. In particular, there are several columns 24 provided at the bottom by the projections 21 formed grooves and at the end surfaces 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, also from the elastomeric body 13 through the gap 24 is spaced. This column 24 are each by a on the elastomeric body 13 trained sealing lip 15 locked. The sealing lip 15 is in the radial direction in the direction of the outer sleeve 16 before and is located at the first axial end portion 16a or in the second axial end region 16b at. The sealing lip 15 preferably extends completely in the circumferential direction.

As this particular in 3 is apparent, are column 24 between the elastomeric body 13 and an end face of the projection 21 and the counter-projection 22 provided, in particular, is a gap 24 at each end face between the projection 21 as well as the counter-projection 22 and the elastomeric body 13 intended. That is, in each through the projections 21 and the counterprojections 22 formed groove is a gap 24 provided, with the gap 24 between the elastomeric body 13 and the outer sleeve 16 is arranged.

In the gap 24 , the end face of the projection 21 is an additional cushion 26 provided, extending from the elastomeric body 13 in the gap 24 hineinerstreckt. The additional cushion 26 has a convexly curved outer contour in cross section 26a on. The additional cushion 26 preferably contacts the end face of the projection 21 ,

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

The compression of the area of the elastomer body 13 , which contributes to the axial rigidity, biases the elastomeric body 13 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 bushings, as a variety of protrusions 21 and counterprojections 22 is provided. In particular, the bearing bush 10 more than three tabs 21 and counterprojections 22 on. By such a toothing of the projections 21 and counterprojections 22 a particularly high radial rigidity can be achieved.

The lead 21 is in the radial direction so far in the direction of the core 11 before that he in the radial direction with the counter-projection 22 overlaps. In other words, the counterproposal stands 22 from the core 11 so far in the direction of the outer sleeve 16 before that he 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 stiffness associated with the increase in axial stiffness can be compensated. In particular, in the case of vibrations in the radial direction with an amplitude that is smaller than the thickness of the gap 24 in the radial direction, only the additional cushion is 26 or to the additional cushion 26 adjacent region of the elastomeric body 13 compressed.

Furthermore, increases with increasing radial deflection of the outer sleeve 16 opposite the core 11 the Surface of the additional cushion 26 , which on the outer sleeve 16 is applied. In this way, a progressive course of the radial stiffness can be provided. Only when the amplitude of the vibrations in the radial direction is greater than the thickness of the gap 24 in the radial direction, carries the complete elastomer body 13 to the stiffness in the radial direction. In this way, for small amplitude vibrations in the radial direction, a significant reduction in radial stiffness can be made.

The gap 24 thus creates a certain freewheel. Through the additional cushion 26 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 cushion 26 is provided. In this way, vibrations in the radial direction with an amplitude smaller than the thickness of the gap act 24 in the radial direction no or only small areas of the elastomer body 13 , so that a particularly low rigidity can be adjusted.

The bearing bush 10 according to 2 agrees with the bushing 10 according to 1 except for the following differences. The core 11 is in accordance with the embodiment of 2 from a core element 11a and an intermediate sleeve 12 together. The intermediate sleeve 12 is on the core element 11a arranged rotatably mounted. This can, for example, a bearing gap 18 be provided, which is optionally filled with lubricant. The projections 22 are thus on the intermediate sleeve 12 provided, which may be made of plastic.

Because the intermediate sleeve 12 on the core element 11a is rotatably mounted, the intermediate sleeve 12 in the axial direction relative to the core element 11a move. To the axial mobility of the intermediate sleeve 12 to limit is a stop device 17 intended. The stop device 17 Can be integral with the core element 11a be formed, for example, as circumferential flange in the circumferential direction. In the in 2 illustrated embodiment, the stop device 17 as a first ring disk 17a and a second annular disc 17b formed, each on the core element 11a are pressed at its axial ends. To the area between anchor device 17 and the intermediate sleeve 12 to increase, is the bearing bush 10 formed such that the outer elements of the toothing between the bearing sleeve 16 and the core 11 at the intermediate sleeve 12 are formed. The counterprojections 22 , which are arranged at the axial ends, can also be used as a first limiting projection 12a and second limiting projection 12b be designated. The first limiting projection 12a and the second limiting projection 12b differ in their contour from the other counter-projections 22 , In particular, the area of the first or the second limiting projection is 12a . 12b , which the stop device 17 facing, over the bearing gap 18 parallel to the stop device 17 arranged.

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

In addition, the gap 24 exclusively in the through the projections 21 provided grooves provided. In through the counter-projections 22 formed grooves is not a gap 24 provided because there the elastomeric body 13 at the projections 21 is applied. This means that at a radial deflection whose amplitude is smaller than the radial thickness of the gap 24 , the elastomeric body 13 only in the area of the groove of the counter-projections 22 is compressed. Compared to a deflection in the radial direction, which is greater than the thickness of the gap 24 in the radial direction, thus only a portion of the elastomeric body is effective 13 , In this way, a progressive course of rigidity can be achieved.

In addition, the runs in 2 illustrated section through the outer sleeves 16 ; therefore they are hatched.

In the 4 shown embodiment of the bearing bush 10 agrees with the in 1 shown embodiment match. The only difference is that the additional cushion 26 not between two opposing projections 22 is provided, but between two projections 21 , Because the distance between two protrusions 21 greater than the distance between two opposing projections 22 is, the additional cushions 26 be made wider; Thus, a harder rigidity can thus be adjusted in the radial direction.

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

LIST OF REFERENCE NUMBERS

10

bearing bush

11

core

11a

core element

12

intermediate sleeve

12a

first limiting projection

12b

second limiting projection

13

elastomer body

15

sealing lip

16

outer sleeve

16a

first axial end region

16b

second axial end region

17

stop device

17a

first annular disc

17b

second annular disc

18

bearing gap

21

head Start

22

counter-projection

24

gap

26

additional cushion

26a

outer contour

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 0654617 B1 [0003]
• US 2962311 [0003]

Claims (10)

Bearing bush (10) comprising a core (11), an outer sleeve (16) surrounding the core (11) and an elastomeric body (13) disposed between the core (11) and the outer sleeve (16), wherein the outer sleeve (16) has at least two projections (21) and the core (11) at least one counter-projection (22) which in a radial direction with the projections (21) for limiting axial movement of the outer sleeve (16) relative to the core (11) overlaps, and wherein the elastomeric body (13) is partially spaced from the outer sleeve (16) and / or from the core (11) by a gap (24). Bearing bush after Claim 1 , characterized in that the gap (24) is arranged in the axial direction between the projections (21) and / or between the counter-projections (22). Bearing bush after Claim 1 or 2 , characterized in that the elastomeric body (13) has at least one additional cushion (26) which extends into the gap (24). Bearing bush after Claim 3 , characterized in that the additional cushion (26) has a convexly convex in cross-section outer contour (26a). Bearing bush according to one of the preceding claims, characterized in that a portion of the elastomeric body (13) which extends between the projection (21) and the counter-projection (22) in the radial direction is compressed in the axial direction. Bearing bush according to one of the preceding claims, characterized in that the elastomeric 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-projection (22) substantially perpendicular, but at a maximum extend 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 elastomeric body (13) integrally connected to the core (11) or the outer sleeve (16), in particular vulcanized is. Bearing bush according to one of the preceding claims, characterized in that the core (11) comprises a core element (11a) and an intermediate sleeve (12), wherein the intermediate sleeve (12) is rotatably mounted on the core element (11a). Bearing bush according to one of the preceding claims, characterized in that the outer sleeve (16) is made of several parts, preferably two parts in the form of half shells, wherein preferably the parts of the outer sleeve (16) are interconnected by means of a hinge.

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