BEARING BUSHING

Description

[0001] The invention relates to a bearing bushing according to the preamble of claim 1.

[0002] A bearing bushing can be used to support a vehicle component, such as an internal combustion engine, a transmission, or an electric motor, against a vehicle body. Furthermore, a bearing bushing can improve driving comfort by isolating vibrations generated by the vehicle component and dampening road vibrations.

[0003] Such bearing bushings are typically penetrated by a central longitudinal axis and comprise an inner core extending along the central longitudinal axis, an outer tube arranged circumferentially to the inner core, forming an intermediate region, and at least one elastomeric body located between the inner core and the outer tube in this intermediate region. The elastomeric body may have webs extending radially with respect to the central longitudinal axis, spanning the intermediate region.

[0004] These types of bearing bushings also vibrate at a natural frequency, which can have an undesirably large amplitude and / or occur in an undesirable frequency range. If the natural frequency and an excitation frequency introduced, for example, by the vehicle's engine, coincide, resonance can occur. This resonance leads to high dynamic stiffness of the bearing bushing, which means that, for example, high-frequency vibrations transmitted from the engine to the vehicle body cannot be satisfactorily reduced by the bearing bushing. These vibrations are then perceived more intensely, which can sometimes reduce the perceived quality of the vehicle and its comfort.

[0005] Document JP2018159455, which is considered to be the closest prior art, discloses a bearing bushing with all the features of the preamble of claim 1.

[0006] The invention is therefore based on the objective of creating a bearing bushing which overcomes the problems of the prior art, in particular to propose a bearing bushing which prevents the transmission of high-frequency vibrations into a body in an improved manner and which can be designed in a simple and cost-effective manner for different applications.

[0007] The main features of the invention are specified in the characterizing part of claim 1. Embodiments are the subject of claims 2 to 10.

[0008] According to the invention, a bearing bushing is therefore proposed through which a central longitudinal axis projects, comprising an inner core extending along the central longitudinal axis, an outer tube arranged circumferentially to the inner core, such that an intermediate region is formed between the inner core and the outer tube, and at least one elastomer body arranged between the inner core and the outer tube in the intermediate region, wherein the elastomer body has webs extending radially with respect to the central longitudinal axis and spanning the intermediate region, wherein at least one of the webs is associated with an arrangement of radial projections arranged on the circumferential side of the inner core and on the inside of the outer tube, the radial projections projecting radially into the elastomer body from the respective side.

[0009] The at least two radial projections create a geometry in the area of ​​the web that projects radially into the elastomer body. This geometry allows for influencing the volume of the elastomer body, its effective vibrating mass, and its geometric design. This advantageously enables the natural frequency of the bearing bushing and the elastomer body, as well as the frequency modes and dynamic stiffness, to be influenced. This geometric variation allows for the deliberate manipulation of the vibration modes. In principle, this leads to adjustment options for the bearing bushing, such as shifting the frequency of a resonance peak or dispersing it across the frequency band.Shifting at least one resonance peak may hardly change its amplitude, but it can shift it into a frequency range where it is perceived as less bothersome by a user or is masked by other influences. While scattering the peak in the frequency band generally keeps it within its untuned frequency range, it reduces its amplitude and thus diminishes its perceptibility to the user.

[0010] This advantageously creates a bearing bushing that can be adapted to a wide variety of installation situations and requirements in a simple and cost-effective manner.

[0011] The at least one arrangement of radial projections can have at least two radial projections, which can be distributed all on the inner core, all on the outer tube, or on both the inner core and the outer tube. Preferably, the radial projections are arranged alternately on the outer tube and the inner core in the longitudinal direction. The radial projections serve to limit the oscillating mass of the elastomer body in the longitudinal direction, with radial projections adjacent to each other on the inner core or the outer tube enclosing or limiting an elastomer section between them in the longitudinal direction. The radial projections can be in direct contact with the elastomer element and / or be completely covered by the elastomer element. At least one radial projection can be designed as an element projecting from a base region of the inner core or the outer tube, extending in the radial direction.

[0012] The element referred to as the inner core can itself be the element that directly secures the bearing bushing to another structure, such as the vehicle body. However, it can also be mounted on another element, for example, a radially inner sleeve, which in turn secures the bearing bushing. In this case, the inner core can be firmly connected to the radially inner element, for example, by friction, positive locking, and / or a material connection. The inner core and the outer tube can be coaxially aligned. The inner core and / or the outer tube can be a sleeve. The inner core and / or the outer tube can be free of end or face flange sections.

[0013] The inner core can have a central recess that extends at least partially along the longitudinal axis. This recess can be a central through-hole along the longitudinal axis, extending from one end face of the bearing bushing to the other. However, this recess can also be open only to one end face. It is also conceivable that it has an opening to both end faces with blind holes on both sides, i.e., no through-hole.

[0014] The at least one elastomeric element can be the sole element connecting the two elements, the inner core and the outer tube. The at least one elastomeric element can be directly connected to the inner core via a connection section and / or to the outer tube via a connection section. The at least one elastomeric element is preferably vulcanized to the inner core and / or the outer tube, more preferably within a single vulcanization step. The connection sections of the at least one elastomeric element can overlap at least partially in the radial direction, preferably completely. The elastomeric element can completely fill the intermediate area in the region of each web – the elastomeric element can therefore be free of recesses, such as holes or longitudinal grooves.At least one end face of the elastomeric element can form an angle with the central longitudinal axis – that is, the respective end face can be tilted with respect to the central longitudinal axis. This can lead to improved force transmission into the inner core, especially if the elastomeric element or at least one web widens towards the inner core in the longitudinal radial direction.

[0015] The webs can completely span the intermediate area radially. The webs can be the only element connecting the two elements, the inner core and the outer tube. Preferably, the webs are the only elements arranged in the intermediate area. A longitudinal clearance can be formed between circumferentially adjacent webs in the intermediate area, preferably extending over the entire longitudinal extent of the adjacent webs. The longitudinal clearance can be limited by the inner core, the outer tube, and the two adjacent webs. The longitudinal clearance can therefore be free of separate stop elements. The longitudinal clearance can also be formed as a recess extending through the bearing bushing, open to both end faces of the bushing. Each web can be continuous in the longitudinal direction. Each web can extend from one end face of the bearing bushing to the opposite end face of the bearing bushing.

[0016] In a further development, adjacent radial projections can be arranged offset from one another in the direction of the central longitudinal axis on opposite sides or the circumferential side of the inner core and on the inside of the outer tube, wherein the bearing bushing preferably comprises at least one inner projection arranged on the inner core and at least one outer projection arranged on the outer tube. Thus, the radial projections are not only arranged on opposite sides but can also be longitudinally offset from one another. This design enables the axial limitation of at least one section of the elastomer body for frequency control while simultaneously ensuring sufficient static stiffness.

[0017] According to a further development of the bearing bushing, the radial projections arranged on opposite sides, or on the circumferential side of the inner core and on the inside of the outer tube, do not overlap in the radial direction – they are therefore designed without overlap in this direction. This design can ensure sufficient static stiffness.

[0018] According to a further optional embodiment, a minimum distance can exist between radial projections arranged on opposite sides or on the circumferential side of the inner core and on the inside of the outer tube. Preferably, this minimum distance is identical between all laterally alternating radial projections within a web, and more preferably within all webs of the bearing bushing. The minimum distance can also be the thickness of the elastomer element in the direct area between the respective radial projections. An identical or uniform minimum distance results in a constant static stiffness. This not only allows the natural resonance to be advantageously modified, but also ensures that the static stiffness in all three spatial directions remains essentially unchanged, which can also be desirable.

[0019] According to further development, the arrangement can comprise at least two radial projections on one side and at least one radial projection on the other side. For example, it is conceivable that two radial projections are arranged on one side and one radial projection on the opposite side. Thus, an opposing radial projection projects into an elastomer section axially bounded on one side by adjacent radial projections, whereby the axial boundary can also extend beyond the head section of the respective radial projection in the radial direction. The opposing radial projection can be arranged longitudinally midway between the two adjacent radial projections on one side.To adapt the bearing bushing design, the longitudinal distance between adjacent radial projections can be reduced to limit a smaller elastomer mass and increased to limit a larger elastomer mass. Similarly, the longitudinal extent of the opposite radial projection can also be adjusted, which is particularly useful for maintaining a consistent minimum distance. This allows for different resonant frequencies. The radial projections located on the same side can be identical in design, or at least have a uniform extent in the radial and / or longitudinal direction.

[0020] According to one embodiment, a gap, preferably a head gap, can be formed between radial projections adjacent on one side. Additionally or alternatively, the at least one radial projection arranged on the other side can have a width extending in the direction of the central longitudinal axis, preferably a head width. The head gap can be the distance between the two radial projections in the region of their respective head sections. The head gaps and / or head widths can be identical or different within a web or within the bearing bushing.

[0021] According to a further development, the longitudinal profile of one of the sides between adjacent radial projections can correspond to the longitudinal profile of at least one head section of a radial projection located on the other side, preferably centrally with respect to the adjacent radial projections. Thus, both sides are congruent in the radial direction. They can therefore be conceptually joined in a form-fit. The radial thickness of the elastomeric element can therefore be uniform in this area.

[0022] In a further development, at least one of the radial projections has a trapezoidal shape in longitudinal section, preferably an isosceles trapezoid. All radial projections can also have such a trapezoidal shape. Preferably, the longitudinal section tapers towards the opposite side, starting from a base section and ending at a head section. The side faces of the radial projections can form an angle with the longitudinal axis in the range of 45° to 90°, preferably in the range of 60° to 70°. Side faces of radial projections located on opposite sides that face each other can be parallel. However, the longitudinal shape can also be rectangular or square. Here, too, the at least one opposing radial projection can be arranged substantially perpendicular to the axial direction. The free corners of each radial projection can have rounded or angular edges.

[0023] In a further embodiment, it is conceivable that the webs are arranged offset from each other by 45°, 60°, 90°, 120°, or 180° with respect to the central longitudinal axis and / or, viewed longitudinally, that an imaginary extension of at least one outer flank of a web passes through the central longitudinal axis. The webs can thus be uniformly spaced circumferentially, with two webs being diametrically opposed to each other with respect to the central longitudinal axis. The webs can be designed to converge concentrically on the central longitudinal axis in order to prevent torque from being introduced into the inner core under radial load. Preferably, both outer flanks of each web intersect the central longitudinal axis. The outer flanks of webs diametrically opposed with respect to the central longitudinal axis can be arranged in a common plane. However, the side flanks can also be designed to project into the longitudinal free space, for example, by means of a concavity.

[0024] According to further development, the radial projections arranged on one side can have the same radial distances to the central longitudinal axis in diametrically opposite arrangements. The opposing radial projections thus extend the same distance radially into the elastomer. They therefore lie on the same diameter circle, the center of which lies on the central longitudinal axis.

[0025] A bearing bushing is conceivable in which at least one arrangement can be designed to be mirror-symmetrical with respect to a transverse median plane of the bearing bushing. However, the at least one arrangement can also be mirror-symmetrical with respect to a transverse plane that is spaced apart from the transverse median plane of the bearing bushing. According to the invention, both arrangements, which are diametrically opposed with respect to the central longitudinal axis, are designed to be mirror-symmetrical with respect to a transverse median plane or to their own transverse plane.

[0026] Preferably, all arrangements are designed to be mirror-symmetrical.

[0027] According to the invention, the arrangements, which are diametrically opposed to the central longitudinal axis, are designed differently. The design can relate to the geometry. With different designs, the bearing bushing can be described as asymmetrical, since both webs can be designed differently with respect to a longitudinal center plane. A high degree of asymmetry can be achieved by designing the two diametrically opposed arrangements to the greatest possible degree. This makes it possible to realize a bearing bushing in which no resonances are apparent in the high-frequency characteristic, where the high-frequency range can lie particularly between 500 Hz and 3000 Hz. For the dynamic stiffness in the range up to 3000 Hz, this has the effect that no common vibration mode can develop and the mass vibrating in resonance at the same frequency is kept as small as possible.In the case of an unstressed, identical design, particularly of all webs, the bearing bushing can be described as symmetrical, since both webs can be identical with respect to the longitudinal center plane. In this case, the bearing bushing is also rotationally symmetrical with respect to the central longitudinal axis. The asymmetrical bearing bushing serves, in particular, to disperse a resonance peak across the frequency band. The symmetrical bearing bushing is cost-effective because the individual components do not necessarily need to be oriented in a specific way when inserted into a vulcanization tool. Here, too, a characterization of the high-frequency response is possible; however, a distinct peak remains in the response, which can be oriented differently in the frequency range depending on the spacing of the geometries or radial projections. The symmetrical bearing bushing serves, in particular, to shift the frequency range of a resonance peak.

[0028] It is conceivable that, in the bearing bushing, the head width of a radial projection in this arrangement can be smaller than the head spacing of adjacent radial projections on one side in the same arrangement. Simultaneously, in the arrangements arranged diametrically with respect to the central longitudinal axis, the head width of a radial projection in this arrangement can be smaller than the head spacing of adjacent radial projections on one side in the same arrangement. The head widths and head spacings are distances. The head spacings and / or head widths of radial projections arranged on one side diametrically opposite the longitudinal axis in arrangements can be identical or different. The head spacing of one arrangement can be smaller than a head width of the diametrically opposed arrangement; preferably, the distances exhibit uniform differences in length, or the distances can differ by a fixed amount or a multiple thereof.By uniformly sliding the adjacent radial projections towards or away from each other on one side of the bearing bushing, the elastomer mass between them is altered. This can result in different resonant frequencies, allowing the elastomer bearing to be designed for a specific installation situation.

[0029] It is also conceivable that at least one radial projection is formed in one piece, preferably monolithically or from a single material, with the inner core or the outer tube. In this case, the radial projection is formed by the inner core or the outer tube. Such a design reduces the number of individual components and the manufacturing complexity, since fewer parts need to be inserted into the vulcanization tool.

[0030] In the case of the bearing bushing, it is conceivable that the section of the elastomer body adjacent to a radial projection in the direction of the central longitudinal axis, and preferably facing the end face of the bearing bushing, can have a longitudinal extent that corresponds at most to the longitudinal extent of the adjacent radial projection. Thus, the elastomer element is no thicker at its end face than the radial projection located there. This can particularly apply to the at least one radial projection on the inner core.

[0031] The at least one radial projection on the inner core can cover between 10% and 70% of the intermediate area in the radial direction, preferably 20%. The at least one radial projection on the outer tube can cover between 70% and 10% of the intermediate area in the radial direction, preferably 60%. The uncovered longitudinal area between the radial projections can be between 10% and 30% of the intermediate area in the radial direction, preferably 20%. The sum of the radial extent of the at least one radial projection on the inner core, the at least one radial projection on the outer tube, and the uncovered radial area between them can be 100% of the intermediate area in the radial direction.

[0032] The ratio of the head width to the longitudinal extent of the elastomer element and / or the inner core and / or the outer tube can be in the range of 1:8 to 1:1.25, preferably in the range of 1:5.5 to 1:2.

[0033] Further features, details and advantages of the invention will become apparent from the wording of the claims and from the following description of exemplary embodiments with reference to the drawings. The drawings show: Fig. 1 is an end-face view of a bearing bushing according to a first embodiment according to the invention, Fig. 2 is a first longitudinal section view through the bearing bushing according to Fig. 1 along line II-II, Fig. 3 a second longitudinal section view through the bearing bushing after Fig. 1 along line III-III, Fig. 4 an end-face view of a bearing bushing according to a second embodiment according to the invention, Fig. 5 a first longitudinal section view through the bearing bushing according to Fig. 4 along line VV, and Fig. 6 a second longitudinal section view through the bearing bushing after Fig. 4 along line VI-VI.

[0034] In the figures, identical or corresponding elements are designated with the same reference numerals and are therefore not described again unless expedient. Features already described are not described again to avoid repetition and are applicable to all elements with the same or corresponding reference numerals, unless explicitly excluded. The disclosures contained in the entire description are transferable analogously to identical parts with the same reference numerals or component designations. Furthermore, the positional designations chosen in the description, such as top, bottom, side, etc., refer to the directly described and illustrated figure and must be applied analogously to the new position if the position changes.Furthermore, individual features or combinations of features from the different exemplary embodiments shown and described can also represent independent, inventive or inventive solutions.

[0035] The Figures 1 to 3Figure 1 shows a first embodiment of the bearing bushing 2 according to the invention in an asymmetrical configuration. A four-rib bushing, i.e., a bearing bushing 2 with four ribs 12, is shown. The bearing bushing 2 shown is penetrated by a central longitudinal axis Z and a transverse median plane Q and comprises a cylindrical inner core 4 designed as an unslotted sleeve, an outer tube 6 also cylindrical and designed as an unslotted sleeve, and an elastomer body 8. The inner core 4 is circumferentially surrounded in the circumferential direction U by the outer tube 6, with the inner core 4 and outer tube 6 being coaxially aligned. The inner core 4 has a through-pass 30 along the central longitudinal axis Z with a groove 32 for aligned mounting. Since the outer tube 6 is arranged at a distance R from the inner core 4 in the radial direction, an intermediate region 10 is formed between them. The elastomer body 8 is arranged in the intermediate region 10. As shown in particular in Figure 1, the inner core 4 is arranged in a radially spaced area R. Fig. 1 and4 As can be seen, the elastomer body 8 comprises four webs 12 evenly distributed around the central longitudinal axis Z. The webs are thus arranged offset from each other by 90°, so that two webs 12 are diametrically opposed to each other with respect to the central longitudinal axis Z, as shown in the Fig. 2 and 3Figures 5 and 6 show the webs 12. The webs 12 are continuous in the radial direction R and in the direction of the central longitudinal axis Z, each extending radially in the direction R and completely spanning the intermediate region 10 in the radial direction R. Each web 12 has two side surfaces or outer flanks 26 in the circumferential direction U, with an extension 24 of each of the outer flanks 26 extending through the central longitudinal axis Z. Thus, each web 12 has a circular sector cross-section, at least in the intermediate region 10. Between webs 12 adjacent in the circumferential direction U, a longitudinal clearance 34 is formed in the intermediate region 10, extending over the entire longitudinal extent of the adjacent webs 12. Each longitudinal clearance 34 is bounded radially on the inside by the inner core 4, radially on the outside by the outer tube 6, and circumferentially U by the two adjacent webs 12 or their side flanks 26.Each longitudinal clearance 34 is free of separate stop elements and is designed as a continuous recess that is open to both end faces 28.

[0036] As the longitudinal views in Fig. 2 , 3 , 5 and 6As shown, the elastomeric element 8 is vulcanized to the inner core 4 and the outer tube 6, forming connection sections. The longitudinal section views also show that the elastomeric element 8 covers the entire circumferential side 14 of the inner core 4 and the entire inner surface 16 of the outer tube 6, with the elastomeric element 8 tapering to a thin, collar-like profile in the region of the end faces 28 of the bearing bushing 2 and having no vibration-influencing function there. Each web 12 thus comprises a main section 36 and the tapered collar sections 38. The main section 36 is M-shaped in longitudinal section, with the two basic lines of the M-shape running between the inner core 4 and the outer tube 6 and having an end face 40 on the outside. The end faces 40 are tilted longitudinally with respect to the central longitudinal axis Z, so that the main section 36 tapers longitudinally towards the outer tube 6 and widens longitudinally towards the inner core 4.

[0037] The inner core 4 has a cylindrical base body 42 with a circumferential side 14. Two radial projections 18 extend from the base body 42, which project radially into the elastomer body 18 and can be described as internal projections. The outer tube 6 also has a cylindrical base body 44 with an inner side 16. A radial projection 20 extends from the base body 44, which projects radially into the elastomer body 18 and can be described as an external projection. The radial projections 18 and 20 are formed with the same material as the inner core 4 and the outer tube 6, respectively, and are arranged alternately along the inner core 4 and the outer tube 6 in the longitudinal direction. They are longitudinally offset from each other on opposite sides 14 and 16. The radial projections 18 and 20 of a web 12 form an arrangement of radial projections.The radial projections 18, 20 have the longitudinal shape of an isosceles trapezoid, with the shape tapering longitudinally from the respective sides 14, 16 into the elastomeric element 8. The free corners of each radial projection 18, 20 have rounded edges.

[0038] The side faces of the radial projections 18, 20 are tilted relative to the central longitudinal axis Z and form an angle of approximately 67° with it. The two radial projections 18, or inner projections, extend into the elastomeric element 8 by approximately 20% of the radial extent of the intermediate region. The radial projection 20, or outer projection, extends into the elastomeric element 8 by approximately 60% of the radial extent of the intermediate region. This results in a non-overlapping region in the radial direction R, in which the radial projections 18, 20 arranged on the opposite sides 14, 16 do not overlap. This non-overlapping region comprises 20% of the radial extent of the intermediate region. Each radial projection 18, 20 has a head section 22 between its edges and a foot section 46 at its other end, by which it is connected.

[0039] The smallest distance between radial projections 18, 20 arranged on opposite sides 14, 16 can be measured between their edges of the respective head sections 22. This smallest distance b is identical for all such adjacent radial projections 18, 20 within a bearing bushing 20 to ensure uniform static stiffness in all three spatial directions. The two radial projections 18, or internal projections, define an elastomer section between them in the longitudinal direction, into which the opposite radial projection 20 projects. The radial projection 20 is arranged centrally to the two radial projections 18.

[0040] It is also evident that the longitudinal profile of the inner surface 16 between the adjacent radial projections 18 corresponds to the longitudinal profile of the head section 22 of the opposite radial projection 20. Thus, both sides are congruent in the radial direction. They can therefore be conceptually fitted together, and the facing side faces of the radial projections 18 can then be projected congruently onto the two side faces of the radial projection 20. The radial thickness of the elastomeric element 8 is therefore uniform in this area.

[0041] Each bearing bushing 2 is designed to be mirror-symmetrical with respect to the transverse median plane Q, although this is only optional.

[0042] The previous character description can be used for all Figures 1 to 6 The following section will discuss the details of the two embodiments.

[0043] A summary of Figures 2 and 3 This clarifies that the bearing bushing 2 of the first embodiment has four arrangements O1, O2, O3, O4 of radial projections 18, 20, with a separate arrangement O1, O2, O3, O4 in each web 12. Each arrangement O1, O2, O3, O4 comprises, in each web 12, the radial projections 18 arranged radially inside the intermediate area 10 and the radial projection 20 arranged radially outside the intermediate area 10. Each radial projection 18, 20 has a head section 22 with a head width A1, A2, A3, A4. The head widths of the radial projections 18 in an arrangement O1, O2, O3, O4 are identical. A head spacing I1, I2, I3, I4 exists between the head sections 22 of adjacent radial projections 18, i.e., the direct longitudinal distance between the two head sections 22.

[0044] It can be seen that the base body 42 of the inner sleeve 4 has a uniform outer diameter Di over its entire longitudinal extent. The radial projections 18 of all four arrangements O1, O2, O3, O4 on the inner sleeve 4 have uniform radial extents and equal radial distances to the central longitudinal axis Z, so that all head sections 22 of the radial projections 18 lie on the same diameter circle Di2, the center of which lies on the central longitudinal axis Z. The radial projections 18 thus project the same distance into the elastomer element 8. It can also be seen that the base body 44 of the outer tube 6 has a uniform outer diameter Da over its entire longitudinal extent.The radial projections 20 of all four arrangements O1, O2, O3, O4 arranged on the outer tube 6 have uniform radial extensions and equal radial distances to the central longitudinal axis Z, so that all head sections 22 of the radial projections 20 lie on an equal diameter circle Da2, the center of which lies on the central longitudinal axis Z.

[0045] The arrangements O1, O2, O3, O4 differ in particular by the different head spacings I1, I2, I3, I4 and the corresponding head widths A1, A2, A3, A4 of the radial projections 20. This also results in an asymmetric bearing bushing 2. The bearing bushing 2 is therefore mirror-asymmetric about the central longitudinal axis Z.

[0046] The head width A1 of the radial projection 20 of the first arrangement O1 is smaller by a defined length than the head spacing I1 between the radial projections 18 of the first arrangement O1. The head spacing I1 of the first arrangement O1 is smaller by this defined length than the head width A2 of the radial projection 20 of the second arrangement O2. The head width A2 of the radial projection 20 of the second arrangement O2 is smaller by this defined length than the head spacing I2 between the radial projections 18 of the second arrangement O2. The head spacing I2 of the second arrangement O2 is smaller by this defined length than the head width A3 of the radial projection 20 of the third arrangement O3. The head width A3 of the radial projection 20 of the third arrangement O3 is smaller by this defined length than the head spacing I3 between the radial projections 18 of the third arrangement O3.The head spacing I3 of the third arrangement O3 is smaller by this defined length than the head width A4 of the radial projection 20 of the fourth arrangement O4. The head width A4 of the radial projection 20 of the fourth arrangement O4 is smaller by this defined length than the head spacing I4 between the radial projections 18 of the fourth arrangement O4. The defined length is therefore a fixed dimension, resulting in uniform length differences. In this case, the lengths differ by the fixed dimension or a multiple thereof.

[0047] Although the diagram shows that the first arrangement O1 and the second arrangement O2 are diametrically opposed to each other, and that the third arrangement O3 and the fourth arrangement O4 are diametrically opposed to each other, the first and fourth arrangements O1, O4, as well as the second and third arrangements O2, O3, can also be diametrically opposed to each other.

[0048] In particular, arrangements O3 and O4 show that the section of the elastomer body 8 adjacent to a radial projection 18 in the direction of the central longitudinal axis Z and facing the bearing bush 2 has a longitudinal extent L1 that corresponds at most to the longitudinal extent L2 of the adjacent radial projection 18, where L2 is defined as the base width of the radial projection 18, but is not limited to it. This prevents the elastomer thickness on the outside of the radial projections 18 from becoming too large. If the radial projections 18 are oriented in the direction of the transverse center plane Q or are arranged towards each other on one side, the outer elastomer thickness and / or the radial elastomer thickness can become too large to allow for a suitable adjustment of the dynamic stiffness.To prevent the axial outer and / or radial elastomer thickness from becoming too large, at least one radial projection 18 can have a longitudinal extent L2 such that the radial projection 18 at least partially overlaps the connection area of ​​the elastomer element 8 on the side opposite the intermediate area 10 in the radial direction. The radial projection 18 is thus coincident in the radial direction R with the radially opposite connection area of ​​the elastomer element 8 on the outer tube 6, in particular with the main section 36. Preferably, the connection area of ​​the elastomer body 8, more preferably the connection area of ​​the main section 36, does not extend beyond a corresponding radial projection 18 on the outer tube 6 in the longitudinal direction. Such a longitudinal extent L2 of long radial projections 18 is shown in the first arrangement O1.

[0049] The following will only highlight the essential differences compared to bearing bushing 2 according to the Figures 1 to 3 to be addressed. Figures 4 to 6 Figure 1 shows a second embodiment of the bearing bushing according to the invention in a symmetrical configuration, wherein only a single arrangement O5 is realized, which is formed in each of the four webs 12. The bearing bushing 2 is thus not only mirror-symmetric about the transverse median plane Q, but also rotationally symmetric about the central longitudinal axis Z. Therefore, the Figures 5 and 6 identical. The radial projections 20 have a uniform head width A and a uniform head spacing I is applied between adjacent radial projections 18 on one side.

[0050] It can be seen that the base body 42 of the inner sleeve 4 has a uniform outer diameter Di along the longitudinal extent of its central region as the base region. At its end faces, the base body 42 has an outer diameter Di3 that is larger than the outer diameter Di at both ends.

[0051] The invention is not limited to one of the embodiments described above, but can be modified in a variety of ways. All features and advantages arising from the claims, the description, and the drawings, including design details, spatial arrangements, and process steps, can be essential to the invention both individually and in various combinations.

[0052] The invention encompasses all combinations of at least two features disclosed in the description, claims and / or figures.

[0053] To avoid repetition, features disclosed by the device itself shall also be deemed disclosed by the process and be claimable. Likewise, features disclosed by the process shall be deemed disclosed by the device itself and be claimable. Reference symbol list

[0054] 2 Bearing bushing 4 Inner core 6 Outer tube 8 Elastomer body 10 Intermediate area 12 Web 14 Circumferential side 16 Inner side 18 Radial projection 20 Radial projection 22 Head section 24 Extension 26 Outer flank 28 End face 30 Through-hole 32 Groove 34 Longitudinal clearance 36 Main section 38 Collar section 40 End face 42 Base body 44 Base body 46 Foot section A, A1, A2, A3, A4 Head width b Spacing Da Outer diameter Da2 Diameter of circle Di Outer diameter Di2 Diameter of circle Di3 Outer diameter I, I1, I2, I3, I4 Head spacing L1 Longitudinal extent L2 Longitudinal extent O1, O2, O3, O4, O5 Arrangement Q Transverse center plane

Claims

1. Bushing (2) through which a central longitudinal axis (Z) extends, comprising an inner core (4) which extends along the central longitudinal axis (Z), an outer tube (6), which is arranged circumferentially relative to the inner core (4) so as to form an intermediate region (10), at least one elastomeric body (8) which is arranged between the inner core (4) and the outer tube (6) in the intermediate region (10), wherein the elastomeric body (8) has webs (12) extending in the radial direction (R) relative to the central longitudinal axis (Z), which span the intermediate region (10), wherein at least one of the webs (12) is associated with an arrangement (O1, O2, O3, O4, O5) of radial projections (18, 20), which is arranged on the circumferential side (14) of the inner core (4) and on the inner side (16) of the outer tube (6), wherein the radial projections (18, 20) from the respective side (14, 16) project into the elastomeric body (8) in the radial direction (R), wherein both arrangements (O1, O2, O3, O4, O5) are mirror-symmetrical with respect to a transverse central plane (Q) or to a separate transverse plane, characterised in that the arrangements (O1, O2, O3, O4, O5) arranged diametrically opposite one another with respect to the central longitudinal axis (Z) are of different designs.

2. Bushing (2) according to claim 1, characterised in that adjacent radial projections (18, 20) are arranged offset from one another in the direction of the central longitudinal axis (Z) on respective opposite sides (14, 16), wherein the bushing (2) preferably comprises at least one inner projection arranged on the inner core (4) and at least one outer projection arranged on the outer tube (6).

3. Bushing (2) according to one of the preceding claims, characterised in that the radial projections (18, 20) arranged on respective opposite sides (14, 16) do not overlap in the radial direction (R).

4. Bushing (2) according to one of the preceding claims, characterised in that there is a direct minimum distance (b) between radial projections (18, 20) arranged on respective opposite sides (14, 16).

5. Bushing (2) according to one of the preceding claims, characterised in that the arrangement (O1, O2, O3, O4, O5) comprises at least two radial projections (18, 20) arranged on one side (14, 16) and at least one radial projection (18, 20) arranged on the other side (14, 16).

6. Bushing (2) according to one of the preceding claims, characterised in that a distance, preferably a head distance (I, 11, 12, 13, 14), is formed between radial projections (18) adjacent on one of the sides (14), and / or the at least one radial projection (20) arranged on the respective other of the sides (16) has an extension width in the direction of the central longitudinal axis (Z), preferably a head width (A, A1, A2, A3, A4).

7. Bushing (2) according to one of the preceding claims, characterised in that the longitudinal section of one of the sides (14) between adjacent radial projections (18) there corresponds to the longitudinal section of at least one head section (22) of a radial projection (20) arranged on the respective other side (16), preferably centrally with respect to the adjacent radial projections (18).

8. Bushing (2) according to one of the preceding claims, characterised in that at least one of the radial projections (18, 20) has a trapezoidal cross-section, preferably that of an isosceles trapezium.

9. Bushing (2) according to one of the preceding claims, characterised in that the webs (12) are offset by 45°, 60°, 90°, 120° or 180° relative to the central longitudinal axis (Z) and / or, viewed in the longitudinal direction, an imaginary extension (24) of at least one outer flank (26) of a web (12) passes through the central longitudinal axis (Z).

10. Bushing (2) according to one of the preceding claims, characterised in that the radial projections (18, 20) arranged on one of the sides (14, 16) have equal radial distances from the central longitudinal axis (Z) in respect of diametrically opposed arrangements (O1, O2, O3, O4, O5).