Bushing bearing with optimized intermediate plate

Abstract

The invention relates to a bush bearing with optimized intermediate plates, the elastomer bush bearing comprising a metal core nucleus extending axially along a central longitudinal axis, a outer sleeve concentrically arranged to the core nucleus, an elastomer bearing body arranged between the core nucleus and the outer sleeve and vulcanized thereto, in which bearing body two longitudinal recesses are formed extending in axial direction through the entire length of the bearing body and opposite in a first radial direction, two intermediate plates vulcanized into the bearing body and each comprising at least one circular portion extending in circumferential direction in a cross-sectional plane perpendicular to the central longitudinal axis over at least 135° around a partial center, the bearing body comprising for each intermediate plate an outer elastomer track and an inner elastomer track, the intermediate plates each having two bent portions bent relative to the circular portion. The bent portions of the intermediate plates are bent towards a second radial direction perpendicular to the first radial direction and extend perpendicularly or nearly perpendicularly into the longitudinal recesses of the bearing body.

Description

Technical Field

[0001] This invention relates to an elastomer bushing bearing (Buchsenlager). Background Technology

[0002] Elastomer bushing bearings are known in the prior art. For example, CN103241086A relates to an elastomeric bushing bearing with slotted sides and two partially circular intermediate plates. A major problem with this structure is the strong strain concentration in the center clearance region of the elastomeric bearing body, especially under radial loads perpendicular to the clearance. The increased strain leads to excessive stress on the elastomer, and thus premature component failure.

[0003] Furthermore, JP4832344B2 also relates to an elastomer bushing bearing with a partially circular intermediate plate, but it has a convex core and intermediate plate. Despite its high radial and axial stiffness, this solution imposes additional loads on the elastomer in the central region due to the convex extension, resulting in increased strain and potential damage.

[0004] CN112555315A also describes a sleeve structure with only a partially circumferential intermediate plate. Due to the uneven distribution of the elastomer tracks, the stiffness varies greatly in the radial direction. Although the outwardly bent ends of the intermediate plate enhance the stiffness in one direction, they deteriorate the stiffness in the orthogonal direction and lead to uneven load distribution, which may also cause premature failure. Summary of the Invention

[0005] The object of the present invention is to overcome these and other disadvantages of the prior art and to provide an improved elastomeric bushing bearing that provides high radial stiffness while having improved functionality and a longer service life.

[0006] An elastomeric bushing bearing includes: a metal core extending axially along a central longitudinal axis; an outer sleeve concentrically disposed with respect to the core; an elastomeric bearing body disposed between the core and the outer sleeve and connected to them by vulcanization, wherein two longitudinal recesses extending axially through the entire length of the bearing body and opposing each other in a first radial direction are formed in the bearing body; two intermediate plates vulcanized and embedded in the bearing body and each including at least one circular portion extending at least 135° circumferentially in a section plane perpendicular to the central longitudinal axis around a partial center, wherein the bearing body includes an outer elastomeric track and an inner elastomeric track for each intermediate plate, wherein each intermediate plate has two bends bent relative to the circular portions. According to the invention, the bends of the intermediate plates are bent toward a second radial direction perpendicular to the first radial direction and extend vertically or nearly vertically into the longitudinal recesses of the bearing body.

[0007] Preferably, the longitudinal recesses extending completely through the bearing body in the axial direction can be configured to be identical. Preferably, the longitudinal recesses can extend from the metal core toward the outer sleeve in a first radial direction. More preferably, the longitudinal recesses can have the same cross-sectional shape or recess shape and / or extend from the core toward the outer sleeve in the same manner in the first radial direction, wherein the longitudinal recesses can have a substantially square or rectangular cross-sectional shape. Preferably, the longitudinal recesses can extend in the axial direction parallel to the flat sides of the core. The intermediate plate extending around the longitudinal recesses in the circumferential direction can then bend its bent portion toward a second radial direction perpendicular to the first radial direction and extend vertically or nearly vertically into the longitudinal recesses of the bearing body.

[0008] The solution of this invention advantageously provides a bushing bearing in which the deformed intermediate plate at its ends produces a near-closed geometry in the circumferential direction when pressed in. This solution creates a sleeve geometry that allows for radial stiffness similar to that in the prior art, but with lower strain elevation or strain concentration in the clearance region due to the vertically or near-vertically positioned bends. In the prior art, these strain elevations are generated, particularly under radial loads perpendicular to the clearance, by the compression of the elastomer. "Nearly circumferential" as used herein should be understood to mean that while the intermediate plates may be spaced apart from each other in the unpressurized state, they can be brought very close together by calibrating the outer sleeve and / or during the pressing process. However, preferably, even in the calibrated and / or pressed-in state, a small gap may still exist between the bends or between the two intermediate plates.

[0009] Because the bent portions of the intermediate plate of the present invention bend towards a second radial direction perpendicular to the first radial direction and extend vertically or nearly vertically into the longitudinal recesses of the bearing body, the stress distribution in the elastomer is advantageously and significantly improved, as the vertical or nearly vertical orientation of these portions more uniformly controls the elastomer body under radial loads in two orthogonal directions. This specifically reduces strain rise, particularly in the central region of the internal elastomer track area or gap, where critical stress concentrations often occur in the prior art, for example, in the partially circular intermediate plate described at the beginning. Simultaneously, the arrangement of the intermediate plate and the bent portions of the present invention helps to improve rotational symmetry, thereby ensuring more uniform stiffness in all radial directions. This is particularly advantageous in applications with cyclic or dynamic loads, as uneven deformation and material fatigue are minimized. Furthermore, the vertical or nearly vertical embedding into the longitudinal recesses allows for more stable anchoring of the intermediate plate, thus maintaining accurate positioning under load. Overall, this geometry results in increased service life, enhanced mechanical stability, and optimal force transmission for the elastomer bushing bearing.

[0010] According to a preferred embodiment, the bends can extend so nearly vertically into the longitudinal recesses of the bearing body that they deviate slightly inward toward the core in the first radial direction relative to the circumference of the circular portion. The bends of the intermediate plate extend nearly vertically into the longitudinal recesses, achieving controlled load transfer. Their inward orientation in the second radial direction ensures a uniform stress distribution within the elastomer, thereby reducing strain rise and increasing service life. Since strain rise tends to occur in the inner elastomer track in the central region when the elastomer track thicknesses of the inner and outer elastomer tracks are the same, it is advantageous if the inner elastomer track is made thicker than the outer elastomer track. Therefore, the inner elastomer track can preferably be constructed to be thicker than the outer elastomer track. Furthermore, the radially inward bending toward the core has a particularly positive effect on stiffness and elastomer compression, further reducing strain concentration.

[0011] According to another preferred embodiment of the invention, the bends may each bend at a point on the circumference. The bends may extend such that they each form an angle of up to 20°, preferably up to 15°, relative to the circumferential tangent of the circular portion at that point. Thus, the two pairs of bends in the intermediate plate, facing each other through their circumferential end faces in the longitudinal recess, form a total angle of 40° (preferably 30°). Radially inwardly deformed and angle-limited portions can produce particularly advantageous effects. The slight inward bending of these portions creates an optimized geometry that harmoniously distributes stress. Limiting the angle to a maximum of 20° (preferably up to 15°) minimizes material fatigue and improves the efficiency of force transmission while maintaining the structural integrity of the system. That is, if the gap were much larger, on the one hand, the stiffness in the two mutually perpendicular radial directions would be significantly different, and on the other hand, especially in the central region of the internal elastomer track, an increase in strain would be expected due to the compression of the elastomer. This situation is advantageously offset by the defined upper limit.

[0012] According to another preferred embodiment, the bent portions of the intermediate plate can extend into the longitudinal recesses such that their total extension at the end faces of the intermediate plate constitutes at most 60°, preferably at most 40°, more preferably at most 32°, of the circumference around the partial center. Their total extension in the central region of the intermediate plate preferably constitutes at most 90°, preferably at most 80°, of the circumference around the partial center. Limiting the total extension to at most 60° (preferably 40°) at the end faces and at most 90° (preferably 80°) in the central region ensures a precise balance between flexibility and stiffness, or stability. This improves load distribution and reduces localized overloads in the elastomer.

[0013] Preferably, the intermediate plate may have a rotationally symmetric region about a longitudinal axis at its end faces, which is at least 270° in the circumferential direction, preferably at least 300°. This high rotational symmetry of at least 270° (preferably 300°) results in uniform radial stiffness in all directions. This reduces stress peaks and ensures improved torsional strength, thereby enhancing the stability of the bushing bearing under dynamic loads. Therefore, the rotationally symmetric region of the intermediate plate corresponds to at least 270° or 3 / 4 of the circumference, and in a preferred embodiment, 300° or 5 / 6 of the circumference. This high rotational symmetry results in radial stiffness similar to that in the prior art, but also provides good torsional characteristics. Good torsional characteristics here refer to low strain rise at bends.

[0014] According to another preferred variation, the opposing longitudinal recesses can be closed such that the opposing end faces of the bends in the intermediate plate approach each other during the calibration of the outer sleeve and / or the installation of the bushing bearing. In this case, a gap can be provided between the end faces, which is at most twice the wall thickness of the intermediate plate, preferably at most 1.5 times the wall thickness. The ability to close the longitudinal recesses during the calibration or installation of the bushing bearing ensures better fit and reduces noise and vibration. The controlled gap between the end faces ensures optimal elastomer deformation and avoids excessive stress concentration.

[0015] According to another preferred embodiment, the longitudinal recess can extend completely through the outer and inner elastomer tracks of the bearing body in a first radial direction. The longitudinal recess can extend completely radially from the core to the outer sleeve, wherein the surfaces of the outer sleeve, core, and intermediate plate can be covered with a thin rubber sheet for manufacturing purposes. More preferably, the thickness of the rubber sheet can be about 0.6 mm to 1 mm. The complete radial extension of the longitudinal recess through the inner and outer elastomer tracks ensures better separation of the load areas. This reduces stress concentration in the elastomer and ensures uniform force transmission between the core, outer sleeve, and intermediate plate.

[0016] Preferably, the outer sleeve can be constructed to be closed over its entire outer surface, or have longitudinal grooves corresponding to longitudinal recesses, which can extend axially through the entire length of the outer sleeve. A closed outer sleeve provides high structural integrity and prevents the intrusion of dirt or moisture. Alternatively, the longitudinal grooves improve installation flexibility and allow for adjustments for specific applications.

[0017] According to a preferred embodiment, the core can be substantially cylindrical and have a convex or spherical central region. The convex or spherical central region can be used to optimize and guide the deformation of the elastomer under axial and radial loads.

[0018] Preferably, the core may have two radially opposite flat sides facing the longitudinal recess. The convex or spherical central region of the core may be flattened by the sides in the longitudinal recess region. The flat sides and the flattened central region minimize strain rise in the longitudinal recess region and ensure controlled deformation. The flattening of the convex or spherical central region also improves fit and stability.

[0019] According to another preferred variation, the core may have at least two unloading grooves, which are axially offset from the spherical central region of the core relative to the central longitudinal axis. The unloading grooves reduce localized stress peaks, particularly under radial loads perpendicular to the longitudinal recesses, and improve the system's flexibility. Their axial arrangement on either side of the spherical central region results in a reduction of strain in the elastomer, which is observed under radial loads through axial outward compression of the elastomer. They thus prevent excessive loading in the elastomer.

[0020] Preferably, the unloading groove can be partially implemented in the circumferential direction and offset from the flat side of the core by 90° in the circumferential direction. The 90° offset of the unloading groove in the circumferential direction ensures targeted stress release and a defined orientation, thereby improving the structural integrity of the bushing bearing while reducing material stress.

[0021] According to another preferred embodiment, the internal elastomer tracks can each be disposed between the core and an intermediate plate. The external elastomer tracks can each be disposed between an intermediate plate and an outer sleeve. In this case, the thickness of the internal elastomer tracks can be up to 30% greater than the thickness of the external elastomer tracks, preferably up to 20% greater, wherein this greater thickness exists in at least 50% of the elastomer track extension, preferably in at least 80% of the elastomer track extension. The respective thicknesses can be measured along a radial vector perpendicular to the central longitudinal axis and passing through the maximum radial extension of the convex or spherical central region. Adjusting the thickness ratio of the elastomer tracks can optimize deformation characteristics and load transfer. This results in better utilization of the elastomer and higher load-bearing capacity in specific applications.

[0022] According to a preferred variation, the end face of the bent portion of the intermediate plate may involve the intermediate plate itself and have a straight orientation in the axial direction along the central longitudinal axis. The end face involving the elastomeric layer of the bearing housing may have a draft angle in the axial direction along the central longitudinal axis. The combination of the straight end face in the axial direction (of the intermediate plate) and the draft angle (on the covered elastomeric layer) enables easy installation and prevents unwanted stress accumulation in the elastomeric layer, especially in the central gap region. This also improves installation friendliness and functionality.

[0023] Preferably, the longitudinal extension of the intermediate plate in the axial direction can be less than the longitudinal extension of the unloading groove in the axial direction. Thus, each side of the axial end of the intermediate plate is positioned within the region of an unloading groove, resulting in a larger distance between the axial end of the intermediate plate and the core during the universal joint movement of the bearing compared to the case without unloading grooves. Therefore, the smaller longitudinal extension of the intermediate plate reduces strain peaks in the elastomer and advantageously improves the flexibility of the bushing bearing. This optimizes the system's adaptability to dynamic radial and universal loads and extends its service life.

[0024] According to another preferred embodiment of the invention, the central region of the intermediate plate can be configured as convex or spherical, wherein, viewed axially, the position of the convex or spherical central region of the intermediate plate can be configured to correspond to the spherical central region of the core. The convex or spherical configuration of the central region of the intermediate plate, designed to correspond to the geometry of the spherical central region of the core, provides several technical advantages. This shape optimizes the adaptability of the intermediate plate to the deformation of the elastomeric bearing body under load, particularly under universal load. Through this appropriate design, a uniform strain distribution is achieved in the elastomeric track between the core, intermediate plate, and outer sleeve, thereby effectively reducing strain peaks in the material. Furthermore, the spherical or convex shape advantageously achieves a lower overall universal stiffness than that achievable using a cylindrical intermediate plate. This results in greater ride comfort and reduced material fatigue, thereby improving the overall service life and NVH performance of the bushing bearing. Attached Figure Description

[0025] Other features, details, and advantages of the present invention will become apparent from the following description of embodiments based on the accompanying drawings. Wherein:

[0026] Figure 1a A schematic top view of a bushing bearing according to a first embodiment of the present invention is shown, having two intermediate plates extending at least 135° in the circumferential direction in a cutting plane perpendicular to the central longitudinal axis.

[0027] Figure 1b Show Figure 1a A schematic enlarged view of the intermediate bushing bearing;

[0028] Figure 2a A schematic diagram showing a perspective longitudinal view of the core of the bushing bearing according to the present invention;

[0029] Figure 2b Show Figure 2a A schematic diagram of a longitudinal perspective view of a core with two intermediate plates;

[0030] Figure 2c Show Figure 2a A schematic diagram of a perspective longitudinal sectional view of a core with two intermediate plates;

[0031] Figure 2d Show Figure 2a A schematic diagram of a perspective cross-sectional view of a core with two intermediate plates;

[0032] Figure 2e Show Figure 2a A schematic diagram of a longitudinal sectional view of a core with two intermediate plates;

[0033] Figure 3 A schematic top view of a bushing bearing according to another embodiment of the invention is shown, having two intermediate plates extending at least 135° in the circumferential direction in a section plane perpendicular to the central longitudinal axis.

[0034] List of reference numerals

[0035] R1 First radial (bulb bearing)

[0036] R2 Second Radial (Bushing Bearing, Perpendicular to R1)

[0037] Axial (Bushing Bearing)

[0038] U-shaped circumferential (shroud bearing)

[0039] L - Center longitudinal axis (bushing bearing longitudinal axis)

[0040] M is the center of the circle (circular part).

[0041] T-tangent

[0042] P - Bending point (bend)

[0043] d1 Thickness (Radial Extension - External Elastomer Track)

[0044] d2 thickness (radial extension - internal elastomer track)

[0045] s Wall thickness (intermediate plate)

[0046] L1 Longitudinal extension (unloading slot)

[0047] L2 Longitudinal extension (middle plate)

[0048] α Angle (Bend point - Tangent)

[0049] β angle (extension of the bend)

[0050] 10. Outerwear

[0051] 20 Bearing body (elastic body)

[0052] 21 External elastomer track (bearing body)

[0053] 21' Residual layer of external bearing housing

[0054] 22 Internal elastomer track (bearing body)

[0055] 22' Residual layer of internal bearing housing

[0056] 23. Circular section (intermediate plate base, partially circular)

[0057] 24. Bending section (circumferential end of the middle plate)

[0058] 24' end face (bend, circumferential, without elastomer layer)

[0059] 24'' end face (with elastomer layer)

[0060] 25 Intermediate Plate

[0061] 26. Gap (End Face Spacing)

[0062] 28. Longitudinal groove (outer sleeve)

[0063] 30 cores

[0064] 31 Central recess (core)

[0065] 32. Flat side (core)

[0066] 32' Flat side area (middle plate)

[0067] 33. Protruding / spherical central area (core)

[0068] 34 Unloading slot (core)

[0069] 35 End face (middle plate, longitudinal)

[0070] 36. Central Area (Middle Plate)

[0071] 40. Longitudinal recess (bearing body)

[0072] 50 Elastomer Bushing Bearing Detailed Implementation

[0073] exist Figure 1a , Figure 1b and Figure 3 The elastomeric bushing bearing, generally represented by 50, is a type of bearing that includes a metal core 30 extending axially along a central longitudinal axis L.

[0074] The outer sleeve 10 is concentrically arranged with the core 30, and the elastomeric bearing body 20 is disposed between the core 30 and the outer sleeve 10. The bearing body 20 is connected to the core 30 and the outer sleeve 10 by vulcanization.

[0075] Two longitudinal recesses 40 are formed in the bearing body 20, which extend through the entire length of the bearing body 20 in the axial direction A and are opposite each other in the first radial direction R1.

[0076] Two intermediate plates 25 are vulcanized and embedded in the bearing body 20. Each intermediate plate 25 includes at least one circular portion 23, which extends at least 135° in the circumferential direction U in a section plane perpendicular to the central longitudinal axis L around a partial center M.

[0077] Each bearing body 20 includes an outer elastomeric track 21 and an inner elastomeric track 22 for each intermediate plate 25. Each intermediate plate 25 has two bends 24 that bend toward a second radial direction R2 perpendicular to the first radial direction R1 and extend vertically or nearly vertically into the longitudinal recess 40 of the bearing body 20.

[0078] In particular, through combination Figure 1b and Figure 2d It can be seen that the bent portions 24 can extend into the longitudinal recesses 40 almost vertically, such that they are slightly deformed inward toward the core 30 in the first radial direction R1 relative to the circumference of the circular portion 23, deviating from the circular shape.

[0079] like Figure 1b As further shown, the bent portions 24 may each bend at a point P on the circumference and extend such that they each form an angle α of up to 20°, preferably up to 15°, relative to the circumferential tangent T of the circular portion 23 at that point P.

[0080] The bends 24 can extend into the longitudinal recesses 40 such that the sum of their extensions at the end face 35 of the intermediate plate 25 constitutes at most 60°, preferably at most 40°, and more preferably at most 32° around the partial center M.

[0081] The sum here refers to the sum of the two pairs of bends 24 extending into the radially opposite longitudinal recesses 40. In other words, the bends 24 on each longitudinal recess side constitute at most 30° around the partial center M, preferably at most 20°, more preferably at most 16°. The sum of the extensions in the central region 36 of the intermediate plate 25 can be at most 90° around the partial center M, preferably at most 80°.

[0082] The intermediate plate 25 may have a rotationally symmetric region about the longitudinal axis L at its end face 35, which is at least 270°, preferably at least 300°, in the circumferential direction U.

[0083] The opposing longitudinal recesses 40 in the radial direction R1 can be closed such that the opposing end faces 24' and 24'' of the bends 24 of the intermediate plate 25 are close to each other when calibrating the outer sleeve 10 and / or installing the bushing bearing 50. The spacing between the end faces 24' and 24'' should preferably be configured to be at most twice the wall thickness s of the intermediate plate 25, and particularly preferably at most 1.5 times the wall thickness s of the intermediate plate 25.

[0084] Especially in Figure 1b As can be seen, end face 24' relates to the surface of intermediate plate 25, while end face 24'' relates to the covering elastomer layer.

[0085] The core 30 can be substantially cylindrical and includes a convex or spherical central region 33 (see [reference]). Figure 2a ).

[0086] Figure 2b and Figure 2c It is clarified that the intermediate plate 25 may have a central region 36, which may be constructed in a convex or spherical shape. Viewed from the axial direction A, the position of the convex or spherical central region 36 of the intermediate plate 25 may be constructed to correspond to the spherical central region of the core.

[0087] The longitudinal recess 40 can extend completely through the outer elastomer track 21 and the inner elastomer track 22 of the bearing body 20 in the first radial direction R1, and extend completely radially from the core 30 to the outer sleeve 10.

[0088] The outer sleeve 10 may be constructed to be closed over its entire outer surface, or have longitudinal grooves 28 that extend along the entire length of the outer sleeve 10 in the axial direction A (see [reference]). Figure 3 ).

[0089] The core 30 may have two radially opposing flat sides 32 facing the longitudinal recess 40 and corresponding to the bend 24 in terms of their opposing surfaces. The convex or spherical central region 33 of the core 30 may be flattened by the sides 32 in the region of the longitudinal recess 40 (see, in particular) Figure 2a ).

[0090] Core 30 may have at least two unloading slots 34, which are axially offset from the spherical central region 33 of core 30 relative to the central longitudinal axis L (see in particular). Figure 2e ).

[0091] The unloading groove 34 can be partially implemented in the circumferential direction U, and is offset by 90° from the flat side 32 of the core 30 in the circumferential direction U.

[0092] The internal elastomer track 22 can be disposed between the core 30 and an intermediate plate 25, while the external elastomer track 21 can be disposed between an intermediate plate 25 and an outer sleeve 10. The thickness d2 of the internal elastomer track 22 can be up to 30% larger than the thickness d1 of the external elastomer track 21, preferably up to 20% larger (see [reference]). Figure 1b ).

[0093] The end face 24' of the bent portion 24 of the intermediate plate 25 can have a straight direction along the central longitudinal axis L in the axial direction A, while the end face 24'' involves the elastomeric layer of the bearing body 20 and can have a draft angle along the central longitudinal axis L in the axial direction A.

[0094] The longitudinal extension l2 of the intermediate plate 25 in the axial direction A can be less than the longitudinal extension l1 of the unloading groove 34 in the axial direction A (see in particular) Figure 2e ).

[0095] The present invention is not limited to the aforementioned embodiments, but can be modified in various ways.

[0096] All features and advantages arising from the specification and drawings, including structural details, spatial arrangements and method steps, may exist individually or in various combinations and are essential to the invention.

Claims

1. An elastomer bushing bearing (50), the elastomer bushing bearing (50) comprising: A metal core (30) extending axially along a central longitudinal axis (L); an outer sleeve (10) concentrically disposed with respect to the core (30); an elastomeric bearing body (20) disposed between the core (30) and the outer sleeve (10) and connected to them by vulcanization, wherein two longitudinal recesses (40) are formed in the bearing body (20) extending through the entire length of the bearing body (20) in the axial direction (A) and opposing each other in a first radial direction (R1); two intermediate plates (25) vulcanized and embedded in the bearing body (20) and each including at least one circular portion. (23) The circular portion extends at least 135° in the circumferential direction (U) in a cutting plane perpendicular to the central longitudinal axis (L) around a partial center (M), wherein the bearing body (20) includes an outer elastomer track (21) and an inner elastomer track (22) for each intermediate plate (25), wherein each intermediate plate (25) has two bent portions (24) relative to the circular portion (23), characterized in that the bent portions (24) of the intermediate plate (25) are bent toward a second radial direction (R2) perpendicular to the first radial direction (R1) and extend vertically or nearly vertically into the longitudinal recess (40) of the bearing body (20).

2. The elastomeric bushing bearing according to claim 1, characterized in that, The bent portion (24) extends almost vertically into the longitudinal recess (40) of the bearing body (20), such that the bent portion (24) deviates slightly inward toward the core (30) in the first radial direction (R1) relative to the circumference of the circular portion (23).

3. The elastomeric bushing bearing according to claim 2, characterized in that, Each of the bent portions (24) undergoes a bend at a point (P) on the circumference, wherein the bent portions (24) of the intermediate plate (25) extend such that they each form an angle (α) of up to 20°, preferably up to 15°, relative to the circumferential tangent (T) of the circular portion (23) at point (P).

4. The elastomeric bushing bearing according to claim 3, characterized in that, The bent portions (24) extend into the longitudinal recesses (40) such that the sum of their extensions at the end face (35) of the intermediate plate (25) constitutes a circumference of at most 60°, preferably at most 40°, more preferably at most 32°, around the partial center (M), and / or the sum of their extensions in the central region (36) of the intermediate plate (25) constitutes a circumference of at most 90°, preferably at most 80°, around the partial center (M).

5. The elastomeric bushing bearing according to any one of the preceding claims, characterized in that, The intermediate plate (25) has a total rotationally symmetric region about the longitudinal axis (L) at its end face (35), the region being at least 270° in the circumferential direction (U), preferably at least 300° in the circumferential direction (U).

6. The elastomeric bushing bearing according to any one of the preceding claims, characterized in that, The opposing longitudinal recesses (40) close when calibrating the outer sleeve (10) and / or installing the bushing bearing (50), such that the opposing end faces (24', 24'') of the bends (24) of the intermediate plate (25) are close to each other, wherein, after the longitudinal recesses (40) are closed, a gap is provided between the end faces (24', 24'') of the bends (24), the gap being configured to be at most twice the wall thickness of the intermediate plate (25), preferably at most 1.5 times the wall thickness of the intermediate plate (25).

7. The elastomeric bushing bearing according to any one of the preceding claims, characterized in that, The longitudinal recess (40) extends completely through the outer elastomer track (21) and inner elastomer track (22) of the bearing body (20) in the first radial direction (R1), wherein the longitudinal recess (40) extends completely radially from the core (30) to the outer sleeve (10).

8. The elastomeric bushing bearing according to any one of the preceding claims, characterized in that, The outer sleeve (10) is constructed to be closed over its entire outer surface, or has longitudinal grooves (28) corresponding to the longitudinal recesses (40), which extend in the axial direction (A) through the entire length of the outer sleeve (10).

9. The elastomeric bushing bearing according to any one of the preceding claims, characterized in that, The core (30) is basically constructed in a cylindrical shape, wherein the core (30) has a convex or spherical central region (33).

10. The elastomeric bushing bearing according to claim 9, characterized in that, The core (30) has two radially opposite flat sides (32) facing the longitudinal recess (40), wherein the convex or spherical central region (33) of the core (30) is flattened by the sides (32) in the region of the longitudinal recess (40).

11. The elastomeric bushing bearing according to claim 9 or 10, characterized in that, The core (30) has at least two unloading slots (34), wherein the unloading slots (34) are axially offset from the central longitudinal axis (L) of the core (30) in the spherical central region (33).

12. The elastomeric bushing bearing according to claim 11, characterized in that, The unloading groove (34) is partially implemented in the circumferential direction (U), wherein the unloading groove (34) is offset from the flat side surface (32) by 90° in the circumferential direction (U).

13. The elastomeric bushing bearing according to any one of claims 9 to 12, characterized in that, The internal elastomer tracks (22) are each disposed between the core (30) and an intermediate plate (25), and the external elastomer tracks (21) are each disposed between an intermediate plate (25) and the outer sleeve (10), wherein the thickness (d2) of the internal elastomer track (22) is at most 30% larger than the thickness (d1) of the external elastomer track (21), preferably at most 20% larger, and wherein the corresponding thicknesses (d2, d1) are measured along a radial vector that is perpendicular to the central longitudinal axis (L) and extends radially through the maximum radial extension of the convex or spherical central region (33).

14. The elastomeric bushing bearing according to claim 6, characterized in that, The end face (24') of the bent portion (24) relates to the intermediate plate (25) and has a straight orientation in the axial direction (A) along the central longitudinal axis (L), wherein the end face (24'') relates to the elastomeric layer of the elastomeric bearing body (20) and has a draft angle in the axial direction (A) along the central longitudinal axis (L).

15. The elastomeric bushing bearing according to any one of claims 11 to 14, characterized in that, The longitudinal extension (l2) of the intermediate plate (25) in the axial direction (A) is less than the longitudinal extension (l1) of the unloading groove (34) in the axial direction (A).

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