Flange bushing with slotted intermediate piece
By introducing a closed housing and axial longitudinal recess design into the flange bushing bearing, the assembly process is simplified, the complex assembly and high cost problems of traditional flange bushing bearings are solved, and efficient material utilization and improved mechanical properties are achieved.
Patent Information
- Application Number
- CN202510282862.6
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Priority Date
- 2024-03-26
- Filing Date
- 2025-03-11
- Publication Date
- 2025-09-26
AI Technical Summary
The assembly and calibration process of existing flange bushing bearings is complicated and costly, especially when the wall thickness of the housing is small relative to the diameter of the bushing bearing. The end faces are prone to sliding against each other, and traditional calibration methods may result in material waste and poor mechanical performance.
An elastomeric bushing bearing having a closed shell and an intermediate piece is designed. A longitudinal recess extending in the axial direction is formed in the bearing body. The shell can be plastically or elastically deformed to reduce the diameter, simplifying the assembly process. Pre-compression stress is applied through the longitudinal recess to offset end face sliding.
This enables simplified assembly and alignment of flanged bushing bearings, reduces material consumption, improves sealing and mechanical performance, supports compact, lightweight and sustainable designs, and reduces manufacturing costs and complexity.
Smart Images
Figure CN120701697A_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to an elastomeric bushing bearing having a flange. Background Art
[0002] Elastomeric bushing bearings with flanges, also known as flanged bushing bearings or flanged bushing bearings, are rubber-elastic bearings that can accommodate torsional motion as well as axial and radial deflection. An elastomer pad vulcanized onto the flange acts as an axial stop, limiting axial travel and influencing the axial stiffness progression. These elastomer bushing bearings typically consist of a connection consisting of a metal inner part and a flanged outer part, with an elastomer bearing body vulcanized between them and the elastomer stop resting on the flange. They are commonly used in motor vehicles, for example, for vibration damping and isolation in the chassis, engine, transmission, steering system, auxiliary equipment, battery, and body.
[0003] In the elastomer bearing body of a bushing bearing, an intermediate piece is often used to achieve high radial stiffness while maintaining low torsional stiffness. The intermediate piece divides the bearing body into an inner elastomer track and an outer elastomer track. In order to compensate for the manufacturing-induced tensile stresses in the outer and inner elastomer tracks, which can lead to a shortened service life of the bushing bearing, appropriate countermeasures must be taken, such as aligning the bushing bearing.
[0004] For example, during calibration, compressive stress is applied to the outer elastomeric track of the elastomeric bearing body by permanently plastically deforming the diameter of the outer shell. The outer shell can be metallic and undergo corresponding permanent plastic deformation. Alternatively, the outer shell can be made of an elastic material (e.g. plastic) and its diameter is elastically deformed when the bearing is pressed into the mounting hole. The inner elastomeric track of the elastomeric bearing body can be compressed by enlarging the inner part (i.e. increasing the diameter of the inner part). In principle, both calibration methods must be carried out after vulcanization. Simultaneous calibration of the outer and inner elastomeric tracks by deformation of the outer shell and enlarging the inner part is not only relatively expensive, but the possible calibration rate is also limited, which is disadvantageous. On the one hand, high elongation of the outer shell and / or the inner part can lead to detachment of the adhesive from the substrate used. On the other hand, large enlargement rates can also lead to cracking of the inner part.
[0005] Another option is to use slotted outer shells and intermediate pieces. The slots are longitudinal indentations that penetrate completely through the bearing body in the axial direction of the bushing. They also penetrate the intermediate piece and outer shell in the radial direction of the bushing. During assembly and alignment, the bearing body is not primarily adjusted by plastic deformation of the metal or expansion of the inner part. Rather, alignment occurs by reducing the diameter (by closing the gap formed by the slots), which pre-stresses the inner and outer elastomer tracks of the elastomer bearing body.
[0006] While this type of slotted bushing allows for high prestressing in the elastomer of the bearing body, their assembly requires first pressing the slotted bushing into an assembly funnel to bring it to the required assembly diameter before further pressing it through the funnel into the mounting hole. Unfortunately, however, this "press-through" process is impossible if the elastomer bushing bearing has a flange. Therefore, an assembly funnel cannot be used with flanged bushings. Rather, they are first compressed to the assembly dimensions in a separate holder and then pressed into the mounting hole. The holder must then be removed before the bushing bearing can be fully pressed in. In this case, the unpressed portion of the housing may open slightly, so during further press-in, the end faces in the gap may disadvantageously slide against each other.
[0007] To counteract this undesirable sliding of the end faces against each other, complex end face geometries are required, such as half-shells with flanges and / or staggered end faces. This complicates and increases the cost of press-fitting during assembly or calibration, as it involves a complex, multi-step process that also requires complex and expensive housing geometries. Mutual sliding is particularly critical when the housing wall thickness is small relative to the bushing bearing diameter. Consequently, to avoid sliding, it may sometimes be necessary to use a greater wall thickness and more material than is mechanically necessary. This hinders the compact, lightweight, and sustainable design of flanged bushing bearings. Summary of the Invention
[0008] In view of this, an object of the present invention is to overcome these and other disadvantages of the prior art and to provide an improved elastomeric bushing bearing with a center piece and a flange which is particularly easy to manufacture and assemble.
[0009] An elastomeric bushing bearing comprises a metal inner part extending axially along a central longitudinal axis, an outer shell arranged concentrically with the inner part and having a flange, and an elastomeric bearing body arranged between the inner part and the outer shell and connected to them by vulcanization, wherein at least one intermediate piece is arranged between the inner part and the outer shell and is vulcanized into the bearing body. The invention is characterized in that at least one longitudinal recess is formed in the bearing body and extends axially through the entire length of the bearing body, wherein the longitudinal recess completely penetrates the at least one intermediate piece in the radial direction, and wherein the entire outer surface of the outer shell is closed.
[0010] Due to the inventive design of the longitudinal recess, the intermediate piece and the closing housing, the possibility of prestressing the elastomeric bearing body by reducing the diameter (by closing the gap formed by the longitudinal recess) is created, which is advantageous.
[0011] According to a preferred embodiment of the present invention, the closed housing can be made of metal, wherein the metal housing can be plastically deformed. Advantageously, this also eliminates the need for an assembly funnel and a separate clamp when assembling and / or calibrating flanged bushing bearings. More precisely, the closed, plastically deformable metal housing can be simply aligned into an assembled state in which its diameter is reduced to such an extent that it can be pressed into the bearing mounting hole without the need for an assembly funnel. The present invention provides a solution that advantageously allows for simpler assembly and improved bushing bearing calibration, while effectively counteracting any mutual sliding of the end faces in the described gap.
[0012] According to another preferred alternative embodiment, the housing can be made of an elastic material (preferably plastic), wherein the diameter of the plastic housing is elastically deformed when the bearing is pressed into the mounting hole.
[0013] Due to the closed design of the entire outer surface of the housing, the housing can also advantageously have a smaller wall thickness without the risk of the end faces sliding against each other in the gaps of the longitudinal recesses of the bearing body. This, in the overall scheme of things, simultaneously supports a compact, lightweight, and sustainable design and reduces material consumption. This further reduces manufacturing costs and expenses.
[0014] Due to the closed design of the housing, the overall sealing of the contact surfaces in the vulcanization tool can be designed to be simpler. With conventional slotted bushings, whose longitudinal recesses penetrate not only the inner part in the radial direction of the bushing bearing but also the housing, sufficient contact pressure along the housing groove must be ensured. This requires, in particular, precise insertion of the insert into the tool, which, in general, can disadvantageously increase cycle times and complexity. However, since, according to the present invention, the housing is designed to be closed and the longitudinal recesses or grooves of the bearing body do not penetrate the housing in the radial direction, this is advantageously significantly offset, the sealing is significantly improved, and the demolding edges in the vulcanization tool are simplified.
[0015] Preferably, the metal inner part can be designed to be rotationally symmetrical with respect to the central longitudinal axis. This simplifies the manufacture of the metal inner part and can save costs and reduce manufacturing time in an overall consideration.
[0016] According to a preferred embodiment of the present invention, the bearing body can be formed from at least two elastomeric tracks, with an inner elastomeric track being arranged between the intermediate sheet and the inner part, and an outer elastomeric track being arranged between the intermediate sheet and the outer shell. The elastomeric tracks advantageously support the desired bearing function. Due to the inventive design of the longitudinal recesses, the intermediate sheet, and the closed outer shell, the inner and outer elastomeric tracks of the elastomeric bearing body can advantageously be prestressed by reducing their diameter (by closing the gap formed by the longitudinal recesses). This also offers the possibility of designing the inner and / or outer elastomeric tracks differently as required, for example by means of additional recesses or additionally inserted intermediate sheets, so that the desired mechanical and dynamic response or reaction behavior of the flanged bushing bearing can be adjusted as required.
[0017] Furthermore, this measure has a particularly positive impact on the assembly and / or calibration process, as it additionally facilitates press-in without the need for a funnel and / or calibration clamp. Furthermore, the inner elastomeric track of the bearing body (which directly surrounds the metal inner part) can advantageously be calibrated without the aforementioned expansion of the inner part. Consequently, both the inner and outer elastomeric tracks can be calibrated solely by deforming the outer shell, rather than by simultaneously expanding the inner part, which advantageously significantly reduces costs and complexity. At the same time, this increases the possible calibration rate, as predominantly compressive stresses are generated during calibration of the outer shell, while tensile stresses are generated during expansion of the inner part. This is advantageous because compressive stresses are less critical than tensile stresses with regard to crack induction.
[0018] According to a preferred embodiment of the present invention, the longitudinal recess can at least partially penetrate the bearing body in the radial direction in the region between the intermediate piece and the outer shell, wherein the longitudinal recess at least partially or completely penetrates the bearing body in the radial direction in the region between the intermediate piece and the inner piece. This ensures that the entire outer surface of the metal outer shell of the bushing bearing is closed. The longitudinal recess only extends radially to the extent that the outer shell remains closed.
[0019] According to another preferred embodiment, the cross-section of at least one longitudinal recess of the bearing body can be trapezoidal, wherein the trapezoidal longitudinal recess can extend in the radial direction. The trapezoidal cross-section of the longitudinal recess is particularly easy and economical to manufacture. At the same time, this allows the surfaces that are relative or facing each other in the gap of the longitudinal recess to move toward each other more evenly when the gap is closed, so that partial or complete contact of the relative surfaces can be set as required. Further preferably, the shorter side of the trapezoidal longitudinal recess can be arranged radially adjacent to the inner part, while the longer side of the trapezoidal longitudinal recess can be arranged radially adjacent to the outer shell. Thus, the cross-sectional shape of the longitudinal recess is adapted to the principle diameter reduction of the individual elements of the bushing bearing towards the inner part, so that the surfaces to be moved toward each other in the gap can contact evenly over the entire area as required without generating critical large strain peaks on the elastomer surface in the longitudinal recess.
[0020] According to another preferred embodiment, at least one longitudinal recess can completely penetrate the bearing body in the radial direction, wherein the longitudinal recess can penetrate the bearing body radially from the inner part to the outer shell, so that a bearing body residual layer is formed on the inner part and the outer shell, respectively. The inner and outer bearing body residual layers being arranged directly on the inner part, on the one hand, and on the outer shell, on the other hand, significantly simplify overall production and further support the closed design of the gaps between the longitudinal recesses of the outer shell and the bearing body.
[0021] Preferably, the bearing residue layer may have a thickness of approximately 2 mm in the radial direction of the bushing bearing. Further preferably, the bearing residue layer may have a thickness of less than 2 mm in the radial direction of the bushing bearing. In particular, the thickness of the bearing residue layer in the radial direction of the bushing bearing may have a value between 1.3 mm and 1.4 mm. This ensures that the bearing residue layer is not over-designed relative to the wall thickness of the housing and does not hinder simple alignment, assembly, or press-fitting.
[0022] According to a preferred embodiment of the present invention, the inner and / or outer elastomeric tracks of the bearing body can have at least two further recesses, which can extend axially across the entire length of the bearing body. This allows the stiffness of the bearing, in particular the radial stiffness, to be adjusted individually and coordinated with one another in different directions, depending on requirements and load conditions.
[0023] Preferably, provision can be made for the further recess of the bearing body to extend in the circumferential direction of the bush bearing, wherein the further recess is arcuate in cross section.
[0024] According to another preferred embodiment, the further recesses of the bearing body can extend in the circumferential direction of the bush bearing by at least 1 / 8 of the circumference, in particular by at least 1 / 6 of the circumference.
[0025] The additional recess and the associated design advantageously increase the load-bearing capacity for relatively large torsional or torsional loads and large axial deformations. At the same time, in particular due to the arcuate shape, the relatively high radial stiffness of the bushing bearing is maintained in the radial direction perpendicular to the arcuate recess.
[0026] According to another preferred embodiment, stop pads can be arranged in the other recesses of the bearing body respectively. Therefore, it is advantageously possible to prevent the surfaces in the other recesses from contacting when closed or loaded, and the bearing body can additionally be buffered or damped in the radial direction.
[0027] According to a preferred embodiment of the present invention, it can be provided that an axial end of the bearing body on the flange of the housing has a flange structure, wherein the flange structure of the bearing body is formed by at least one axial stop having a larger axial extension along the central longitudinal axis than the bearing body.
[0028] Preferably, at least one axial stop can extend along the circumference of the bushing bearing and have an arcuate or circular cross-section. If multiple axial stops are provided, they can preferably be symmetrically arranged at the axial ends of the bearing body. For example, the axial stops can be arranged at a constant distance from one another.
[0029] The arched axial stops and the symmetrical and / or constant spacing in the circumferential direction advantageously create a torsionally independent, uniform structure in the region containing the axial stops. These advantageously act as dampers and further improve the function of the bushing bearing. The axial stops, which advantageously function as axial dampers, can axially contact correspondingly suitable elements during assembly or in the assembled position of the bushing bearing, thereby further supporting simple and secure assembly in a defined axial end position. Since the axial stops can be arched and segmented or spaced apart from one another, in the spacing region on the flange of the assembly tool, greater press-in forces can advantageously be transmitted to the flange without the axial stops themselves being subject to these high pressures.
[0030] Preferably, at least two axial stops can be provided, wherein at least two axial stops can be arranged at diametrically opposed positions at the axial end. Further preferably, a total of four axial stops can be provided, wherein each of the four axial stops can be formed by two axial stops arranged at diametrically opposed positions at the axial end. These measures also support a symmetrical and uniform structure of the axial end with the axial stop and flange structure, while also providing good press-fit or assembly properties.
[0031] According to another preferred embodiment, at least one groove can be embossed into the housing at the level of the flange, radially toward the central longitudinal axis. The bearing body can have a recess complementary to the groove of the housing, into which the groove is introduced. Preferably, the groove can be aligned with the longitudinal recess. The groove advantageously creates a position indicator, which in particular improves orientation when pressing the bearing into the mounting hole.
[0032] Preferably, the intermediate piece and the bearing body can have two end faces facing each other, which are formed by the longitudinal recess, wherein the longitudinal recess is closed during alignment of the housing and / or assembly of the bushing bearing, so that after closing the longitudinal recess, the end faces of the intermediate piece and / or the bearing body facing each other are at least partially in contact. The intermediate piece and the bearing body preferably together form the end faces facing each other in the longitudinal recess or in the gap between the longitudinal recesses.
[0033] Furthermore, the gaps in the intermediate pieces can be completely closed by calibrating the flanged housing. The intermediate pieces vulcanized into the bearing body can preferably be designed to be annular. In this case, the intermediate pieces can generally include flow openings or other flow optimizations, which facilitate the filling behavior in the vulcanization mold. Furthermore, the flanged housing and the bearing body can be aligned so that the gaps formed by the longitudinal recesses in the intermediate pieces are completely closed by the alignment, so that at least the separate intermediate pieces come into contact and form a closed annular shape. Thus, the open annular shape of the intermediate piece vulcanized into the bearing body is advantageously transformed into a closed annular shape, thereby further increasing the radial stiffness of the bushing bearing.
[0034] Preferably, the end surfaces facing each other in the gap of the longitudinal notch can at least partially contact and close the gap in the calibration state. Further preferably, the end surfaces facing each other in the gap of the longitudinal notch can at least partially contact each other after the bearing is pressed into the mounting hole or in the assembled state. Particularly preferably, the gap of the longitudinal notch is completely closed in the assembled state, and the end surfaces are in complete contact. This advantageously reduces the reduction in stiffness, particularly in the gap direction (due to the complete closing process), thereby ensuring overall high radial stiffness in the gap-bridging direction.
[0035] In this case, it can further be advantageous to provide that the gap or longitudinal recess of the flanged elastomeric bushing bearing is completely closed in the delivery state. This measure further simplifies the process of pressing the bearing into the mounting hole, since the bearing is already prestressed when it is delivered to the end customer.
[0036] Further preferably, provision can be made for the gap or longitudinal recess of the flanged elastomeric bush bearing to be completely closed at the latest in the pressed-in and assembled state, and for the intermediate disk or the bearing body to assume an annular geometry.
[0037] According to another preferred embodiment of the invention, provision can be made for the bushing bearing to be suitable for a bearing body having a large diameter, wherein the housing comprises an inner diameter for accommodating the bearing body, which inner diameter is at least 50 mm, preferably at least 60 mm.
[0038] According to a preferred embodiment, the housing can comprise a steel material, wherein the housing can have a wall thickness of maximum 1.6 mm, preferably maximum 1.4 mm.
[0039] According to a further preferred embodiment, the housing can comprise an aluminum material, wherein the housing can have a wall thickness of maximum 2.5 mm, preferably maximum 2.0 mm, particularly preferably maximum 1.6 mm.
[0040] Advantageously, the wall thickness of the housing can therefore be relatively small in relation to the diameter of the bushing bearing, although this ratio is particularly critical against the backdrop of undesirable mutual sliding of the end faces in the gap. BRIEF DESCRIPTION OF THE DRAWINGS
[0041] Other features, details and advantages of the present invention can be found in the following description of embodiments based on the accompanying drawings, in which:
[0042] Figure 1 is a schematic diagram of a perspective longitudinal view of a bushing bearing according to the invention,
[0043] Figure 2 is a schematic diagram of a front view of a first embodiment of a bushing bearing according to the present invention, and
[0044] Figure 3 is a schematic diagram of a front view of another embodiment of a bush bearing according to the present invention.
[0045] Reference Signs List
[0046] r radial
[0047] L center longitudinal axis (axial)
[0048] 10 shell
[0049] 11 base (shell)
[0050] 12 grooves (housing, flange)
[0051] 13 flange
[0052] 20 bearing body
[0053] 21 Internal elastomer track
[0054] 21' external elastomer track
[0055] 22 notches (circumferential, bearing body)
[0056] 22' longitudinal notch (radial, bearing body)
[0057] 24 pitch (axial stop)
[0058] 25 intermediate pieces
[0059] 26 axial stop (flange structure)
[0060] 27 stop pad
[0061] 28 end face (longitudinal notch)
[0062] 28' end face (longitudinal notch)
[0063] 30 internal parts
[0064] 31 center notch
[0065] 50 Elastomer Bushing Bearing DETAILED DESCRIPTION
[0066] Figures 1 to 3 The elastomeric bushing bearing, generally designated 50, comprises a metal inner part 30 which extends axially along a central longitudinal axis L and is designed to be rotationally symmetrical with respect to the central longitudinal axis.
[0067] like Figure 1 As shown, a metal outer shell 10 with a flange 13 is arranged concentrically with an inner part 30. An elastomeric bearing body 20 is arranged between the inner part 30 and the outer shell 10 and is connected to the inner part 30 and the outer shell 10 by vulcanization, wherein an intermediate piece 25 is provided between the inner part 30 and the outer shell 10. The intermediate piece 25 is vulcanized into the bearing body 20. The entire outer surface of the outer shell 10 is closed.
[0068] By combining Figure 2 or Figure 3 From a comprehensive observation, it can be seen that a longitudinal notch 22' is formed in the bearing body 20 and extends axially through the entire length of the bearing body 20. The longitudinal notch 22' completely penetrates at least one intermediate piece 25 in the radial direction r.
[0069] The bearing body 20 is formed by two elastomer rails 21 , 21 ′: the inner elastomer rail 21 is arranged between the intermediate piece 25 and the inner part 30 , and the outer elastomer rail 21 ′ is arranged between the intermediate piece 25 and the outer housing 10 .
[0070] The longitudinal recess 22 ′ completely penetrates the bearing body 20 in the radial direction r, wherein a thin rubber skin, which can also be referred to as a bearing body residual layer, can be at least partially present on the intermediate piece 25 , the outer shell 10 and the inner part 30 for manufacturing reasons.
[0071] In this case, the longitudinal recess 22' completely penetrates the bearing body 20 in the radial direction r, wherein the longitudinal recess 22' penetrates the bearing body 20 radially from the inner part 30 to the outer shell 10, so that a thin bearing body residual layer is formed on the inner part 30 and the outer shell 10. In the embodiment shown, the thickness of both these bearing body residual layers resulting from manufacturing reasons in the radial direction r is less than 2 mm.
[0072] The longitudinal recess 22' of the bearing body 20 has a trapezoidal cross-section, thereby forming a gap. The intermediate piece 25 and the bearing body 20 have two facing end faces 28, 28', which are formed by the longitudinal recess 22' or the gap. The longitudinal recess 22' is closed during calibration of the housing 10 and / or during press-fitting of the bushing bearing 50 into the installation opening, so that after the longitudinal recess 22' is closed, the facing end faces 28, 28' of the intermediate piece 25 and / or the bearing body 20 are at least partially in contact.
[0073] Especially if Figure 3In the embodiment shown, it can be seen that the outer elastomeric track 21 ′ of the bearing body 20 has two further recesses 22 which extend axially over the entire length of the bearing body 20 and penetrate the bearing body 20 axially like the longitudinal recesses 22 ′.
[0074] The additional recess 22 of the bearing body 20 extends along the circumference of the bushing bearing, wherein the additional recess 22 is arcuate in cross section. Two additional recesses 22 are arranged diametrically opposite each other in the outer elastomer track 21' of the bearing body 20. The additional recesses 22 of the bearing body 20 each extend approximately 1 / 6 of the circumference along the circumference of the bushing bearing. This extension corresponds to approximately 60°. A stop washer 27 is arranged in each of the additional recesses 22 of the bearing body 20.
[0075] exist Figure 2 In the embodiment shown, no further recess 22 is provided.
[0076] The bearing body 20 has a flange structure at one axial end on the flange 13 of the housing 10, wherein the flange structure of the bearing body 20 is formed by four axial stops 26. The four axial stops 26 have a larger axial extension along the central longitudinal axis L than the bearing body 20. This proportional relationship is Figure 1 In this case, two axial stops 26 are arranged to be diametrically opposed.
[0077] Similar to the further recesses 22 , the four axial stops 26 also extend in the circumferential direction of the bushing bearing and are arcuate in cross section. The axial stops 26 are arranged at constant distances 24 from one another at the axial ends of the bearing body 20 .
[0078] In the housing 10 , at the level of the flange 13 , a groove 12 is formed radially towards the central longitudinal axis L, wherein the bearing body 20 has a recess complementary to the groove 12 of the housing 10 , into which the groove 12 is introduced.
[0079] Figures 1 to 3 The illustrated bushing bearing is suitable for a bearing body 20 having a relatively large diameter, wherein the housing 10 comprises an inner diameter for accommodating the bearing body 20 which is approximately at least 60 mm.
[0080] The invention is not limited to the above-described embodiments, but can be modified in various ways. In particular, the housing can comprise steel or aluminum, wherein the housing can have a wall thickness of approximately 1.4 mm to 2.5 mm, for example. At the same time, relatively large bushing or housing diameters of up to 60 mm can be achieved.
[0081] All features and advantages that can be derived from the description and the drawings, including construction details, spatial arrangements and process steps, can be essential to the invention, both individually and in any combination.
Claims
1. An elastomeric bushing bearing (50), comprising a metal inner part (30) extending axially along a central longitudinal axis (L), an outer shell (10) having a flange (13) arranged concentrically with the inner part (30), and an elastomeric bearing body (20), the elastomeric bearing body (20) being arranged between the inner part (30) and the outer shell (10) and connected to them by vulcanization, wherein: At least one intermediate piece (25) is arranged between the inner part (30) and the outer shell (10), and the intermediate piece (25) is vulcanized into the bearing body (20), characterized in that at least one longitudinal recess (22') is formed in the bearing body (20) and extends axially through the entire length of the bearing body (20), wherein the longitudinal recess (22') completely penetrates the at least one intermediate piece (25) in the radial direction (r), wherein the entire outer surface of the outer shell (10) is closed.
2. The elastomeric bushing bearing according to claim 1, wherein: The closed housing (10) is made of metal, wherein the metal housing (10) is plastically deformable.
3. The elastomeric bushing bearing according to claim 1 or 2, characterized in that: The bearing body (20) is formed by at least two elastomer tracks (21, 21'), wherein an inner elastomer track (21) is arranged between the intermediate piece (25) and the inner part (30), and an outer elastomer track (21') is arranged between the intermediate piece (25) and the outer shell (10).
4. Elastomeric bushing bearing according to any one of the preceding claims, characterized in that The longitudinal recess (22') penetrates the bearing body (20) at least partially in the radial direction (r) in the region between the intermediate piece (25) and the outer shell (10), wherein the longitudinal recess (22') penetrates the bearing body (20) at least partially or completely in the radial direction (r) in the region between the intermediate piece (25) and the inner part (30).
5. Elastomeric bushing bearing according to any one of the preceding claims, characterized in that The at least one longitudinal recess (22') of the bearing body (20) has a trapezoidal cross section, wherein the longitudinal recess (22') extends in a radial direction (r).
6. Elastomeric bush bearing according to any one of the preceding claims, characterized in that The at least one longitudinal recess (22') completely penetrates the bearing body (20) in the radial direction (r), wherein the longitudinal recess (22') extends radially from the inner part (30) to the outer shell (10), so that a bearing body residual layer is formed on the inner part (30) and the outer shell (10).
7. The elastomeric bushing bearing according to any one of claims 3 to 6, characterized in that The inner elastomeric track (21) and / or the outer elastomeric track (21') of the bearing body (20) has at least two further recesses (22) which extend axially over the entire length of the bearing body (20).
8. The elastomeric bushing bearing according to claim 7, wherein: The further recess (22) of the bearing body (20) extends in the circumferential direction of the bush bearing, wherein the further recess (22) is arcuate in cross section.
9. The elastomeric bushing bearing according to claim 7 or 8, characterized in that: The further recesses (22) of the bearing body (20) extend in the circumferential direction of the bushing bearing over at least 1 / 8 of the circumference, in particular over at least 1 / 6 of the circumference.
10. The elastomeric bushing bearing according to any one of claims 7 to 9, characterized in that A stop washer (27) is arranged in each of the further recesses (22) of the bearing body (20).
11. Elastomeric bushing bearing according to any one of the preceding claims, characterized in that The intermediate piece (25) and the bearing body (20) have two end faces (28, 28') facing each other, which are formed by the longitudinal recess (22'), wherein the longitudinal recess (22') is closed during calibration of the housing (10) and / or assembly of the bushing bearing (50), so that after closing of the longitudinal recess (22'), the end faces (28, 28') of the intermediate piece (25) and / or the bearing body (20) facing each other are at least partially in contact.
12. An elastomeric bushing bearing according to any one of the preceding claims, characterised in that The bushing bearing is suitable for a bearing body (20) having a large diameter, wherein the housing (10) comprises an inner diameter for accommodating the bearing body (20), the inner diameter being at least 50 mm, preferably at least 60 mm.
13. An elastomeric bushing bearing according to any one of the preceding claims, characterised in that The housing (10) comprises a steel material, wherein the wall thickness of the housing (10) is at most 1.6 mm, preferably at most 1.4 mm.
14. The elastomeric bushing bearing according to any one of claims 1 to 12, characterized in that The housing (10) comprises an aluminum material, wherein the wall thickness of the housing (10) is at most 2.5 mm, preferably at most 2.0 mm, particularly preferably at most 1.6 mm.