Bearing bush

Abstract

Bearing bush (2) through which a central longitudinal axis (Z) extends, comprising an inner sleeve (4), an outer sleeve (6) which circumferentially surrounds the inner sleeve (4) to form an intermediate region (8), an elastomeric axial bearing (30) which is arranged in the intermediate region (8), and an elastomeric radial bearing (50) which is arranged in the intermediate region (8), wherein a connecting flange (10) with two end faces (12) is arranged on the outer circumference of the inner sleeve (4), wherein an axial bearing package (32a, 32b) of the axial bearing (30) is connected to each of the two end faces (12), wherein the bearing bush (2) is penetrated in the radial direction (R) by a bearing parting plane (L) or a bearing parting surface, wherein the axial bearing (30) is arranged on one side of the bearing parting plane (L) or the bearing parting surface, but the radial bearing (50) is not arranged, and side of the bearing parting plane (L) the radial bearing (50) but the axial bearing (30) is not arranged,wherein the elastomer bodies (31, 51) of the axial bearing (30) and the radial bearing (50) are separate bodies.,

Description

[0001] The invention relates to a bearing bush according to claim 1

[0002] Bearing bushes for axial and radial support are well known in practice. They comprise a total of three separately manufactured elastomer parts, with two axial bearings at the bushing end each having an elastomer part, and a radial bearing arranged between them having another elastomer part. However, two axial bearings are necessary to transmit high axial loads to one bearing in the compression direction. If the axial bearings were subjected to all axial forces in the tensile direction, premature failure would occur, as this bearing type is designed specifically for high compressive loads and exhibits a pronounced progressive stiffness behavior in the compression direction. The compression stage thus protects the opposite rebound stage.

[0003] To adjust the axial, radial, and torsional stiffness, bearing bushes are also known. Their axial bearings are subsequently mounted on the axial ends at the customer's site after the radial bearing has been pressed into its mounting structure. Prior assembly is often not possible because the required outer diameter of the axial bearing is larger than the mounting structure; thus, the bearing, which comprises three elastomer parts, cannot be fully inserted into or through the mounting structure.

[0004] DE 102017 111 668 A1 discloses a bearing bush comprising a core, an outer sleeve with projections, and an intermediate sleeve with counter-projections. An elastomer body is provided between the outer sleeve and the intermediate sleeve.

[0005] An elastic joint is known from FR 2 679 613 A1 and a sealed bearing is known from EP 0 039 114 A1.

[0006] The invention is therefore based on the object of creating a bearing bushing in which as few elastomer parts as possible are installed per bearing, thus requiring as few elastomer parts as possible to be vulcanized, which are then assembled into a bearing unit and which can be prefabricated before being secured to or in a receiving structure. Furthermore, it should be robustly designed and have a wide range of adjustable axial and radial stiffness properties.

[0007] Main features of the invention are defined in claim 1. Claimed embodiments are subject of claims 2 to 8.

[0008] According to the invention, a bearing bush is proposed through which a central longitudinal axis extends, comprising an inner sleeve, an outer sleeve which surrounds the inner sleeve circumferentially to form an intermediate region, an elastomeric axial bearing which is arranged in the intermediate region, and an elastomeric radial bearing which is arranged in the intermediate region, wherein a connecting flange with two end faces is arranged on the outer circumference of the inner sleeve, wherein an axial bearing package of the axial bearing is connected to each of the two end faces.

[0009] The connection flange for the axial bearing, which extends in the radial direction, means that the axial bearings previously arranged at the two bushing ends can now be spatially combined. The axial bearing encompasses both axial bearing assemblies or is formed from them. As a result, the bearing bush according to the invention can now comprise only two elastomer parts that are to be vulcanized separately, or an elastomer body in the axial bearing and an elastomer body in the radial bearing. If each axial bearing assembly is assigned a separate elastomer body, the inventive advantage of spatial combination is still realized, since the respective entire axial bearing assembly can be vulcanized as a single component. The elastomer bodies of the axial bearing and radial bearing are separate bodies according to the invention.Such a design not only reduces manufacturing costs because fewer parts need to be vulcanized, it also reduces pre-assembly costs because the bearing bush can be pre-assembled more easily.

[0010] The axial bearing is supported directly or indirectly on the inner sleeve via the connecting flange. The connecting flange acts as the central connection for the axial bearing to the inner sleeve. A thrust bearing assembly of the axial bearing is arranged on both axial sides of the connecting flange. The thrust bearing assemblies thus act in opposite directions in the axial direction. This ensures that, regardless of the axial load direction, exactly one thrust bearing assembly is always subjected to compressive stress, thus limiting the tensile stresses in the corresponding, other thrust bearing assembly. The connecting flange can be the only connection between the axial bearing and the inner sleeve. This reduces geometric complexity.

[0011] The design of the bearing bush according to the invention also allows it to be completely pre-assembled before being secured or pressed onto or into a receiving structure. Furthermore, the design results in a robust bearing bush that is widely adjustable in terms of its axial and radial properties.

[0012] Pre-assembly is understood to mean a process by which the bearing bush is completely manufactured. After pre-assembly, the bearing bush should be complete. Assembly is understood to mean a process by which the bearing bush is secured at or in its intended operational location. Such bearing bushes are typically pressed into a receiving structure, such as a receiving eye. The bearing bush is described in an unloaded state, with specific reference to load cases.

[0013] According to one conceivable embodiment of the bearing bush according to the invention, the inner sleeve has a hollow cylindrical section and an axially offset or adjacent section with or for the connection flange (flange section). The hollow cylindrical section can be assigned to the radial bearing and the section with or for the connection flange can be assigned to the axial bearing. This allows the radial bearing to be arranged in the hollow cylindrical section on the inner sleeve, for example by being pressed in place, and the axial bearing to be arranged in the section with the connection flange, for example by being vulcanized in place. Alternatively, the radial bearing can be arranged in the hollow cylindrical section on the inner sleeve, for example by being vulcanized in place, and the axial bearing to be arranged in the section for the connection flange, for example by being pressed in place. This spatial separation means that each of the two bearings can be assigned a separate section of the inner sleeve.

[0014] According to another conceivable embodiment of the bearing bush according to the invention, at least one radial clearance can be assigned to the axial bearing. This allows the axial bearing to undergo corresponding radial deformations under radial loads. A radial clearance can also be arranged on the radial inner side, and a radial clearance can also be arranged on the radial outer side of the axial bearing. The axial bearing is supported in the axial direction and should be protected from radial loads as much as possible. This serves to extend the service life. The respective radial clearance can extend over the entire axial extent of the corresponding axial bearing package.

[0015] According to another conceivable embodiment of the bearing bush according to the invention, at least one axial clearance can be assigned to the radial bearing, so that the radial bearing can undergo corresponding axial deformations under axial loads. An axial clearance can also be arranged on both axial sides of the radial bearing. The radial bearing is supported in the radial direction and should be protected from axial loads as much as possible. This serves to extend its service life.

[0016] According to another conceivable embodiment of the bearing bush according to the invention, the axial bearing can be integrally connected to the connecting flange, for example, by vulcanization. The axial bearing assemblies can be vulcanized to the connecting flange. This also simplifies manufacturing. The inner sleeve can be inserted into a cavity, and the axial bearing with the axial bearing assemblies can be formed in one go and arranged on the connecting flange.

[0017] According to a further conceivable embodiment of the bearing bush according to the invention, the connecting flange can protrude into the intermediate region over a distance that lies in the range of 50% to 99% of the intermediate region's radial extension, preferably in the range of 85% to 95% of the intermediate region's radial extension. This allows, on the one hand, large end faces for arranging the axial bearing to be realized, but on the other hand, a gap or radial distance can be formed between the outer circumference of the connecting flange and the outer sleeve, whereby the connecting flange can form a radial stop. Depending on the dimensioning, the gimbal angle or the progression of the gimbal stiffness can be adjusted via the size of the gap or radial distance. It is conceivable that the connecting flange is provided with an elastomer coating on its outer circumference. The elastomer coating can connect the two axial bearing assemblies to one another.The elastomer coating serves to prevent noise during radial contact when a radial stop is formed.

[0018] According to a further conceivable embodiment of the bearing bush according to the invention, the connecting flange can have flat, preferably continuously flat, end faces that extend perpendicular to the central longitudinal axis. The end faces each point in opposite axial directions.

[0019] According to a further conceivable embodiment of the bearing bush according to the invention, the connecting flange can be an annular disc connecting flange which extends in the circumferential direction around the central longitudinal axis in the manner of an annular disc.

[0020] According to another conceivable embodiment of the bearing bush according to the invention, the connecting flange can be formed integrally with the inner sleeve, i.e., in one piece. A corresponding joining process is thus omitted. This allows for a long service life and secure support.

[0021] According to another conceivable embodiment of the bearing bush according to the invention, the connecting flange can be formed integrally with a flange support, for example, a flange sleeve, i.e., from a single piece. The flange support is a separate part from the inner sleeve. The connecting flange is therefore designed as a separate part from the inner sleeve. The flange support can be connected to the inner sleeve, for example, by means of a material bond or by pressing. This embodiment has the advantage that, with the flange support, a smaller part is inserted into the vulcanization cavity compared to the long inner sleeve, which leads to a lower mold height, simplified loading and demolding of the vulcanization mold, and reduced energy costs during vulcanization.

[0022] According to a further embodiment of the bearing bush according to the invention, at least one of the axial bearing assemblies, preferably each of the axial bearing assemblies, can have a connecting structure, preferably a connecting ring disk, at its axial end region. The connecting ring disk can delimit the respective axial bearing assemblies in the axial direction. The respective connecting ring disk can, for example, be supported against other components, for example against the outer sleeve, the outer sleeve shoulder, the radial bearing and / or the mounting sleeve, and thus bring the respective axial bearing assemblies into an axial force flow with the respective component. The connecting structure can be free of a coating, in particular an elastomer coating, at least in sections on its side facing away from the axial bearing. This improves the axial force flow because no elastomer is interposed.

[0023] According to another conceivable embodiment of the bearing bush according to the invention, the connection structure can have at least one thickening and / or bulging extending circumferentially relative to the central longitudinal axis or locally, which can extend in the axial direction, preferably facing the connection flange. The thickening(s) and / or bulging(s) can be circular segment-shaped in longitudinal section. Thus, the respective connection structure can also be used for stiffness adjustment.

[0024] According to a further embodiment of the bearing bush according to the invention, an annular gap can be formed between the inner sleeve and each axial bearing assembly, wherein each annular gap can preferably be designed without undercuts in the axial direction. The undercut-free annular gaps considerably simplify the manufacture of a vulcanized axial bearing, since the axial bearing or its axial bearing assemblies can be easily demolded. Each annular gap can, viewed longitudinally, have parallel side walls radially inward and radially outward. At least one of the annular gaps can extend in the axial direction from an axial end region of the corresponding axial bearing assembly to the connecting flange or an elastomer skin present there. The elastomer skin can be manufacturing-related. This allows the corresponding axial bearing assembly to be given the greatest possible internal radial clearance.

[0025] In terms of service life, it is fundamentally disadvantageous if elastomer bodies do not have a molded rubber runout. In particular, compressive loads lead to bulging of the elastomer bodies and, as a result, to wrinkling and thus to premature failure. With the bearing bush according to the invention, however, any compressive deformation that occurs, particularly in the axial bearing, can be very low due to its high axial rigidity. Instead, the axial bearing can be primarily subjected to shear loads due to high torsion angles. This also allows the disadvantageous absence of undercuts (for example, omitting rubber runouts) of the annular gaps to be neglected. This finding also advantageously serves to design the axial bearing, which fulfills the function of the two axial bearings previously provided at the bushing end, in a cost-effective and production-friendly manner and to provide it with a long service life.

[0026] According to a further embodiment of the bearing bushing according to the invention, at least one of the axial bearing assemblies, preferably each of the axial bearing assemblies, can comprise a stiffening ring washer. The stiffening ring washer can be partially or completely embedded in the elastomer body of the respective axial bearing assemblies. The stiffening ring washer serves to stiffen the corresponding axial bearing assemblies and also reduces bulging of the elastomer body under compressive load in the axial direction. It is conceivable that the stiffening ring washer is arranged centrally in the axial bearing assemblies, viewed in the axial direction, to enable uniform bulging.

[0027] According to a further conceivable embodiment of the bearing bush according to the invention, at least one of the stiffening rings can have at least one thickening and / or bulging extending circumferentially relative to the central longitudinal axis or locally, extending in the axial direction, facing and / or away from the connecting flange. The thickening(s) and / or bulging(s) can be circular segment-shaped in longitudinal section. This allows the respective stiffening ring to also be used for stiffness adjustment.

[0028] According to the bearing bush according to the invention, the bearing bush is penetrated in the radial direction by a bearing parting plane or a bearing parting surface, with the axial bearing being arranged on one side of the bearing parting plane or the bearing parting surface, but not the radial bearing, and the radial bearing being arranged on the other side of the bearing parting plane, but not the axial bearing. The bearing parting plane can run perpendicular to the central longitudinal axis. This design enables large torsion angles due to the spatial concentration of the axial bearings and the spatial separation from the radial bearing. This also allows the bearing bush to advantageously fulfill a ball joint function. For this, a bearing must be flexible with regard to torsion and gimbal motion, while at the same time being rigid with regard to translational deflections. An elastomer bearing subjected purely to shear loads can generally have low rigidity.In contrast, an elastomer bearing subjected to compressive and tensile loads can generally exhibit high rigidity. For the ball-and-socket joint function, the gimbal stiffness and the pivot point should be located in the radial bearing, while the axial bearing should only impede rotation about this pivot point to a very small extent. Due to the lever arm, gimbal-rigid elastomer bodies should therefore be located as close as possible to this pivot point, while with increasing distance from this pivot point, an elastomer body should only be subjected to shear loads in the event of a gimbal deflection (and possibly rotation). While a ball-and-socket joint function can certainly be achieved to a certain extent using conventional bearing bushes, their design (two axial bearings at each end or one axial bearing on each side of the radial bearing) is complex and expensive to manufacture.

[0029] According to another conceivable embodiment of the bearing bush according to the invention, the radial bearing can be pressed onto the inner sleeve. The radial bearing can be manufactured as such and / or pressed onto the hollow cylinder section. Advantageously, the axial bearing can therefore be arranged or formed first, and only then can the radial bearing be arranged.

[0030] According to another conceivable embodiment of the bearing bush according to the invention, the outer sleeve can be manufactured in one piece. The outer sleeve can be an unslotted sleeve. Because the axial bearing and the radial bearing are arranged and designed according to the invention, only a simple outer sleeve can be used to circumferentially seal the bearing bush. The outer sleeve can be easily flanged or rolled on and secure the bearings and / or axially preload at least one of the bearings.

[0031] According to a further conceivable embodiment of the bearing bush according to the invention, the radial bearing can comprise a stiffening sleeve, wherein preferably a contouring, thickening(s) and / or bulging can be formed on the stiffening sleeve, extending in the circumferential direction with respect to the central longitudinal axis or partially. The contouring(s), thickening(s) and / or bulging(s) can face towards and / or away from the inner sleeve. The contouring(s), thickening(s) and / or bulging(s) can be circular segment-shaped in longitudinal section. As a result, the respective stiffening sleeve can also be used to adjust stiffness. It is conceivable that the stiffening sleeve is arranged centrally in the radial bearing, viewed in the radial direction, in order to enable uniform bulging.

[0032] According to a further conceivable embodiment of the bearing bush according to the invention, the radial bearing can have a mounting sleeve on the inner circumference and / or a mounting sleeve on the outer circumference, wherein contours, thickenings, and / or indentations can preferably run circumferentially or partially with respect to the central longitudinal axis on at least one of the mounting sleeves. The contour(s), thickening(s), and / or indentation(s) can face towards and / or away from the inner sleeve. The contour(s), thickening(s), and / or indentation(s) can be circular segment-shaped in longitudinal section. This means that the respective mounting sleeve can also be used to adjust stiffness. However, the mounting sleeve(s) also serve to facilitate the manufacturability of the radial bearing and its subsequent arrangement on the inner sleeve. The radial bearing can be easily pressed onto the inner sleeve using the mounting sleeve on the inner circumference.The outer sleeve can be easily attached or placed on the outer peripheral mounting sleeve.

[0033] According to another conceivable embodiment of the bearing bush according to the invention, the inner peripheral mounting sleeve and / or the flange support can be flush with the inner sleeve at the bearing bush end. The end faces of the inner peripheral mounting sleeve and / or the flange support and the inner sleeve thus lie in one plane. This increases the contact surface at the end.

[0034] According to a further embodiment of the bearing bush according to the invention, the inner sleeve can have a shoulder on the outer circumference against which the radial bearing or the axial bearing can bear. The shoulder can extend in the circumferential direction. The shoulder can easily define an axial end position for the radial bearing or the axial bearing as a positioning stop, so that complex adjustment is no longer necessary during pre-assembly. The correct end position of the respective bearing is reached as soon as it bears against the shoulder. With regard to the radial bearing, it is conceivable that the mounting sleeve on the inner circumference bears against the shoulder on the outer circumference. The mounting sleeve on the inner circumference can then fulfill another function. During pre-assembly, the radial bearing can be fixed against the shoulder on the outer circumference by reshaping the outer sleeve.With regard to the axial bearing, it is conceivable that the flange carrier rests against the outer peripheral shoulder.

[0035] According to a further embodiment of the bearing bush according to the invention, the outer sleeve can have a shoulder on the outer circumference against which a receiving eye can rest and / or a shoulder on the inner circumference against which the axial bearing can rest. The shoulder can extend in the circumferential direction of the bearing bush. This makes it possible to provide more radial installation space for the axial bearing. This enables greater axial rigidity to be achieved. Alternatively, the shoulder can be used to reduce the outer diameter of the radial bearing to a diameter necessary for its function. This makes it possible to minimize the inner diameter of the receiving structure and thus its entire geometry. This leads to a particularly compact and cost-effective overall solution. One of the connecting ring disks of the axial bearing can rest on the shoulder on the inner circumference.The shoulder(s) can be arranged axially between the two bearings (radial bearing and thrust bearing), thus supporting spatial separation. The shoulders can complement each other to reduce the required installation space.

[0036] According to a further conceivable embodiment of the bearing bush according to the invention, the outer sleeve can firstly be pot-shaped in one axial end region and / or secondly be plastically formed in one axial end region or thirdly be plastically formed in both axial end regions. Each embodiment can serve to fix the outer sleeve. Depending on the design of the outer sleeve, the two bearings (radial bearing and axial bearing) can be clamped against one another. According to the first aspect, the outer sleeve can already be provided with the pot-shaped end region during its own production, for example by deep drawing. In the case of the pot-shaped end region, the outer sleeve can be shaped radially inward on the end region side, for example at right angles to the central longitudinal axis.During pre-assembly, this outer sleeve can be placed onto the two bearings (radial bearing and axial bearing) and then formed or reshaped accordingly in the pot-like end area opposite each other in order to clamp the two bearings (radial bearing and axial bearing) against each other. An end area produced by deep drawing can also extend much further inwards in the radial direction than an end area simply formed inwards by calibration or rolling. This allows for more radial overlap with the connecting ring disk of the axial bearing. This can also make its axial guidance more pronounced. According to the second aspect, the outer sleeve can only be plastically formed in the axial end area after it has been placed onto the two bearings (radial bearing and axial bearing). According to the third aspect, the sleeve can only be plastically formed at both ends after it has been placed onto the two bearings (radial bearing and axial bearing).In this case, the outer sleeve can initially be cylindrical, and a cost-effective outer sleeve can be used instead of a more expensive deep-drawn outer sleeve. In this case, both end sections must be plastically formed to axially clamp the bearings (radial bearing and thrust bearing) against each other.

[0037] According to another conceivable embodiment of the bearing bush according to the invention, the axial bearing assemblies can be designed with mirror symmetry or mirror asymmetrical alignment with respect to the connecting flange. Mirror symmetry serves to achieve symmetrical axial bearing detection. Mirror asymmetry can also be used for adjustment. Since the compressive properties in the elastomer body dominate over the tensile properties, an asymmetry of the axial bearing detection can be adjusted in this way. This increases design freedom.

[0038] According to a further embodiment of the bearing bush according to the invention, one of the mounting sleeves of the radial bearing, preferably the outer peripheral mounting sleeve, can bear against the axial bearing so that it can be in axial force flow with the axial bearing and / or can be axially clamped by means of the outer sleeve, thus supporting both bearings (radial bearing and axial bearing) against each other in the axial direction. It is conceivable for the corresponding mounting sleeve to bear directly against one of the outer sleeves of the axial bearing. In this way, the radial bearing can be axially secured on the outer peripheral side and the axial bearing can be axially preloaded at the same time in a simple manner. If both bearings (radial bearing and axial bearing) were manufactured separately, this design is quite cost-effective. In this way, the radial bearing can be axially secured on the outer peripheral side and the axial bearing can be axially preloaded at the same time in a simple manner.This is more cost-effective than separately clamping and preloading the bearing. However, it also has another effect. Being able to preload the thrust bearing axially reduces the tendency of the non-compressive thrust bearing side to lift off. This lift off could cause unwanted noise.

[0039] The resulting pivot point can advantageously be influenced by the axial positioning of the two bearings relative to each other and / or their respective design. The further this pivot point can be positioned toward the radial bearing, the lower the desired small, rotation-induced compressive stresses in the axial bearing. Viewed longitudinally, the outer sleeve can rotate relative to the inner sleeve around the pivot point.According to a further embodiment of the bearing bush according to the invention, viewed longitudinally, an imaginary rotation circle with an associated pivot point on the central longitudinal axis of the bearing bush is tangent to a first line that runs perpendicular to the central longitudinal axis and through the connecting flange, wherein the associated pivot point can lie between a second line that runs perpendicular to the central longitudinal axis and through a constriction point of an elastomer body of the radial bearing facing the axial bearing, and a third line that runs perpendicular to the central longitudinal axis and through the axial center of the radial bearing. The pivot point is the center of the corresponding rotation circle. The advantage of placing the pivot point there is the low induction of compressive stresses in the axial bearing, which should be avoided wherever possible in favor of low gimbal stiffness.The elastomer body of the radial bearing can have a constriction pointing in the axial direction, which can, for example, have an approximately parabolic longitudinal section. The constriction point facing the axial bearing, which defines the location of the second line, can be the constriction of the elastomer bearing of the radial bearing that is furthest away from the third line in the axial direction. The constriction point can be located on the constriction, preferably at the shortest distance from the third line. It is preferably conceivable that the corresponding rotation circle or first rotation circle (with first pivot point) in the radial direction corresponds at most to the outer diameter of a radially innermost part of the elastomer body of the radial bearing.

[0040] There can be an axial distance between the second line and the third line, at which the resulting pivot point or gimbal pivot point preferably occurs. It is advantageous if the resulting pivot point or gimbal pivot point is located between the second and third pivot points. The diameter of the second rotation circle (with second pivot point) corresponds exactly to the outer diameter of the elastomer body of the radial bearing. The radius of the third rotation circle (with third pivot point), on the other hand, is defined by the axial distance between the first and third lines. It has been shown that a beneficial relationship between the two bearings can be represented by the diameter of the rotation circle. The larger the affected rotation circle, the lower the compressive stresses induced in the axial bearing.

[0041] To position a pivot point as desired, the positioning can be determined, for example, by the axial distance between the bearings or the axial distance from the connecting flange to the radial bearing. To position a pivot point as desired, the design can be determined, for example, by the choice of material, in particular the coordination of the elastomer stiffness in the axial and / or radial bearing, the elastomer body pitch, the use of stiffening sleeves, and / or the longitudinal and / or radial extension of elastomer bodies.

[0042] According to a further conceivable embodiment of the bearing bush according to the invention, the elastomer body of the axial bearing can be cylindrical at least in sections on the outer circumference and / or radially curved (with a curvature) at least in sections. Such a section can extend in the axial direction between two elements comprising a connecting flange, a connecting ring disk, and a stiffening ring disk. A cylindrical section can be manufacturing-related, although in this case a curvature can be omitted in favor of simplified manufacturability. When loading a vulcanization tool, omitting a curvature-inducing tool geometry can simplify loading, for example, with stacked components with respect to gravity. A curvature serves to extend the service life of the elastomer.The elastomer body of the axial bearing preferably has at least one cylindrical or at least one curved section, thus achieving an optimum between manufacturability and service life. More preferably, the elastomer body of the axial bearing has only a single such cylindrical section. It is also conceivable to have only a single such cylindrical section per axial bearing package. The cylindrical section can be arranged on the side of a stiffening ring disk on the elastomer body which is facing away from the connecting flange in the axial direction. Such a cylindrical section on the side facing the radial bearing leads to an extension of the service life, since the expansions during cardanic action are lower there. The remaining sections can have curved sections.

[0043] 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. They show: Fig. 1 the left side of a longitudinal sectional view of a bearing bush of the first embodiment according to the invention; Fig. 2 the left side of a longitudinal sectional view of a bearing bush according to the invention of a second embodiment; Fig. 3 the left side of a longitudinal sectional view of a bearing bush of the third embodiment according to the invention; Fig. 4 the left side of a longitudinal sectional view of a bearing bush according to the invention of the fourth embodiment, and Fig. 5 the left side of the longitudinal section of the bearing bush according to the invention according to Fig. 1 with further geometric references.

[0044] In the figures, identical or corresponding elements are each designated by 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 identical or corresponding reference numerals, unless explicitly excluded. The disclosures contained in the entire description are analogously transferable to identical parts with identical reference numerals or identical component designations. The positional information chosen in the description, such as top, bottom, side, etc., also relates to the directly described or illustrated figure and, in the event of a change in position, is to be transferred analogously to the new position.Furthermore, individual features or combinations of features from the different embodiments shown and described can represent independent, inventive or inventive solutions.

[0045] Starting from a central longitudinal axis Z, which extends in the axial direction A, a radial direction R extends. A circumferential direction U extends around the central longitudinal axis Z. The bearing bush 2 is described in the unloaded state and after pre-assembly and assembly, with load cases being referred to separately.

[0046] Fig. Figure 1 shows only the left half of a longitudinal sectional view of a bearing bush 2 according to the invention in a first embodiment. This bearing bush 2 is constructed identically to the other side of the central longitudinal axis Z.

[0047] The bearing bush 2 comprises an inner sleeve 4 with a central bore 5 in the axial direction A for securing a fastening means (not shown). The inner sleeve 4 has a connecting flange 10 on its outer circumference. The connecting flange 10 protrudes from the inner sleeve 4 in the radial direction R like an annular disk and extends in the circumferential direction U around the central longitudinal axis Z. The connecting flange 10 is formed integrally with the inner sleeve and has two end faces 12, which each face opposite axial directions A. The two end faces 12 are flat and run parallel to one another and at right angles to the central longitudinal axis Z. The inner sleeve 4 has a shoulder 16 on its outer circumference, which is assigned to a radial bearing 50 and leads to a diameter jump. In the axial direction to one side of the shoulder 16, the inner sleeve 4 has a hollow cylinder section 56 which has a cylindrical outer peripheral surface.In the axial direction to the other side of the shoulder 16, the inner sleeve 4 has a flange section 58, which has the connecting flange 10. An imaginary bearing parting plane L runs between these sections 56, 58 and through the shoulder 16.

[0048] The bearing bush 2 also comprises a one-piece and unslotted outer sleeve 6, which circumferentially surrounds the inner sleeve 4, forming an intermediate region 8. The outer sleeve 6 has a shorter extension in the axial direction A than the inner sleeve 4 and has a constant diameter between its two end regions. In its axial end region, which lies radially adjacent to the flange section 58 of the inner sleeve 4, it is pot-shaped, for example by deep drawing. In the opposite axial end region, which lies radially adjacent to the hollow cylindrical section 56 of the inner sleeve 4, the outer sleeve 6 is plastically formed, for example by calibration or rolling. It can be seen that the outer sleeve 6 is mounted in a receiving structure 60.

[0049] It can be seen that the connecting flange 10 extends into the intermediate region 8. The intermediate region 8 has a radial extent, but this is greater than the radial extent of the connecting flange 10. The connecting flange 10 can, for example, protrude into the intermediate region 8 over a distance that corresponds to 95% of the intermediate region's radial extent. A gap 11 or a radial distance is formed between an elastomer-coated outer circumference of the connecting flange 10 and the outer sleeve 6, which defines a radial clearance. The connecting flange 10 thus serves as a radial stop 64 for the outer sleeve 6. The outer-circumferential gap 11 or radial clearance extends continuously in the circumferential direction U and in the axial direction A between two connecting ring disks 34a, 34b.

[0050] The bearing bush 2 also includes an elastomeric axial bearing 30 with an elastomer body 31, which is arranged in the intermediate region 8 and comprises two axial bearing assemblies 32a, 32b. Each of the two axial bearing assemblies 32a, 32b is connected to one of the two end faces 12, whereby the axial bearing assemblies 32a, 32b are thus spatially combined. The axial bearing 30 is arranged in the region of the flange section 58; the section with the connecting flange or the flange section 58 is therefore assigned to the axial bearing 30. The axial bearing assemblies 32a, 32b are designed and arranged mirror-symmetrically with respect to the connecting flange 10.

[0051] Each of the axial bearing assemblies 32a, 32b has a connection structure in the form of the respective connection ring disk 34a, 34b at its axial end region. The connection ring disks 34a, 34b are free of a coating, in particular an elastomer coating, on their side facing away from the axial bearing 30. The connection ring disks 34a, 34b have an elastomer coating radially inward and radially outward, and they rest against the outer sleeve 6 via the radially outer elastomer coating. The connection ring disk 34a of the axial bearing assemblies 32a is axially supported against an outer peripheral mounting sleeve 54b of a radial bearing 50. The connection ring disk 34b of the axial bearing assemblies 32b is axially supported against the pot-shaped end region of the outer sleeve 4 and radially against the cylindrical section of the outer sleeve 4.

[0052] Each of the axial bearing assemblies 32a, 32b has a stiffening ring disk 36, which is embedded in the elastomer body 31, but is free of an elastomer coating on the radial outside. An elastomer coating is formed radially on the inside. The stiffening ring disks 36 are each arranged centrally in the respective axial bearing assemblies 32a, 32b, as viewed in the axial direction A, here centrally between the connecting flange 10 and the connecting ring disk 34a, 34b.

[0053] Between the inner sleeve 4, which is provided with a manufacturing-related elastomer skin 62 in the flange section 58, and each axial bearing assembly 32a, 32b, an annular gap 14 is formed in the radial direction R, which defines a radial clearance. It can be seen that each annular gap 14 is designed without undercuts in the axial direction A. Furthermore, each annular gap 14 has parallel side walls radially inward and outward when viewed longitudinally. Each annular gap 14 extends in the axial direction A from an axial end region of the corresponding axial bearing assembly 32a, 32b to the connecting flange 10 or the elastomer skin 62 present there.

[0054] The bearing bush 2 also comprises the elastomeric radial bearing 50 with an elastomer body 51, which is also arranged in the intermediate region 8. The radial bearing 50 has a mounting sleeve 54a on its inner circumference, by means of which the radial bearing 50 is pressed onto the inner sleeve 4. The mounting sleeve 54a also bears against the shoulder 16, which acts as a positioning stop here, and terminates with the inner sleeve 4 at the bearing bush end, whereby the end faces of the inner circumference mounting sleeve 54a and the inner sleeve 4 lie in one plane. The radial bearing 50 has a mounting sleeve 54b on its outer circumference, by means of which the radial bearing 50 bears against the outer sleeve 6. It can be seen that the outer sleeve 6 rests against the outer circumference mounting sleeve 54b in its end region on the mounting sleeve side, whereby the radial bearing 50 is axially clamped.Both mounting sleeves 54a, 54b are provided with a manufacturing-related elastomer skin 68 on their mutually facing sides.

[0055] The radial bearing 50 comprises a stiffening sleeve 52 embedded in the elastomer body 51 and dividing it into two parts. The stiffening sleeve 52 can be free of an elastomer coating at its axial edges and / or can be arranged centrally in the radial bearing 50 as viewed in the radial direction R. In the axial direction A, a gap 66 is formed on each side of the stiffening sleeve 52, defining an axial clearance. Each of the gaps 66 extends continuously in the circumferential direction U and in the radial direction R between the two mounting sleeves 54a, 54b.

[0056] It is now apparent that on one axial side of the bearing parting plane L the axial bearing 30 is arranged, but the radial bearing 50 is not arranged, and on the other axial side of the bearing parting plane L the radial bearing 50 is arranged, but the axial bearing 30 is not arranged.

[0057] With reference to Fig. 2, to avoid repetition, only the differences to Fig. 1 are described.

[0058] Fig. Figure 2 shows only the left half of a longitudinal sectional view of a bearing bush 2 according to the invention in a second embodiment. This bearing bush 2 is constructed identically to the other side of the central longitudinal axis Z.

[0059] The axial bearing 30 now comprises two different axial bearing assemblies 32a, 32b, which are therefore mirror-asymmetrical to the connecting flange 10. While the axial bearing assemblies 32b remain the same, the axial bearing assemblies 32a are now designed without a stiffening ring disk. The connecting ring disk 34a of the axial bearing assemblies 32a now has a thickened portion 70 extending centrally in the radial direction R in the circumferential direction U relative to the central longitudinal axis Z. This thickened portion 70, viewed longitudinally, is circular segment-shaped and extends in the axial direction A toward the connecting flange 10, i.e., facing the connecting flange 10. The axial bearing assemblies 32a also have a smaller extension in the axial direction A than the axial bearing assemblies 32b. The annular gap 14 associated with the axial bearing assemblies 32a is also correspondingly axially shortened.

[0060] The radial bearing 50 is also modified, wherein the stiffening sleeve 52 has a thickening 72 running centrally in the axial direction A in the circumferential direction U with respect to the central longitudinal axis Z. The thickening 72 is circular segment-like in longitudinal section and extends in the radial direction R in the direction of the outer sleeve 6, i.e., away from the inner sleeve 4.

[0061] The outer peripheral mounting sleeve 54b has a concavity 74 extending in the circumferential direction U relative to the central longitudinal axis Z, centered in the axial direction A. The concavity 74 is circular segment-like in longitudinal section and extends in the radial direction R toward the outer sleeve 6, i.e., away from the inner sleeve 4. Thickening 72 and concavity 74 are centered relative to each other in the axial direction A to optimize the gimbal properties and protect the elastomer body 51.

[0062] With reference to Fig. 3, to avoid repetition, only the differences to Fig. 1 are described.

[0063] Fig. Figure 3 shows only the left half of a longitudinal sectional view of a bearing bush 2 according to the invention in a third embodiment. This bearing bush 2 is constructed identically to the other side of the central longitudinal axis Z.

[0064] The outer sleeve 6 is now plastically formed at both ends in its two axial end regions, thus eliminating the need for a deep-drawn, pot-shaped end region. It can be seen that the outer sleeve 6 then extends inward for a shorter distance in the radial direction R and covers the connecting ring disk 34b for a significantly shorter distance.

[0065] The outer sleeve 6 now also includes a shoulder 18 on the outer circumference, against which the receiving structure 60, which can be a receiving eye, rests. The outer sleeve 6 now also includes a shoulder 20 on the inner circumference, against which the axial bearing 30 rests by means of the connecting ring disk 34a. The shoulders 18, 20 complement each other and lead to a diameter jump of the outer sleeve 6. The outer diameter of the mounting sleeve 54b is reduced.

[0066] With reference to Fig. 4, to avoid repetition, only the differences to Fig. 1 are described.

[0067] Fig. Figure 4 shows only the left half of a longitudinal sectional view of a bearing bush 2 according to the invention in a fourth embodiment. This bearing bush 2 is constructed identically to the other side of the central longitudinal axis Z.

[0068] The connecting flange 10 is now formed as a separate part from the inner sleeve 4. The axial bearing 30 comprises a flange carrier, which is designed as a flange sleeve 78 and integrally houses the connecting flange 10. The flange sleeve 78 is pressed onto the inner sleeve 4, resting against the shoulder 16 of the inner sleeve 4, which is now assigned to the axial bearing and also serves as a positioning stop. The flange sleeve 78 terminates at the bearing bush end with the inner sleeve 4, whereby the end faces of the flange sleeve 78 and the inner sleeve 4 lie in the same plane.

[0069] The radial bearing 50 is now designed without an inner peripheral mounting sleeve and is vulcanized directly onto the inner sleeve 4. Therefore, the inner sleeve 4 now also has an elastomer skin 68 on the outer peripheral side in the hollow cylinder section 56.

[0070] Each stiffening ring disc 36 of the axial bearing packages 32a, 32b now has, in the radial direction R, two thickened portions 76 extending centrally in the circumferential direction U with respect to the central longitudinal axis Z, which, viewed longitudinally, are circular segment-like and extend in the axial direction A, one of the thickened portions 76 facing the connecting flange 10 and one of the thickened portions 76 facing away from the connecting flange 10.

[0071] Only in Fig. 4, but also shown in the other figures, are outer circumferential concavities 38a of the axial bearing 30. In addition, Fig. 4 now shows a single cylindrical section 38b of the elastomer body 31. The indentations 38a or the cylindrical section 38b are arranged in sections between the connecting flange 10, a connecting ring disk 34a, 34b, and / or a stiffening ring disk 36.

[0072] Fig. 5 shows the bearing bush 2 of the Fig. 1 in identical view. In Fig. 5, however, further geometric references are shown, which in Fig. 1 are omitted for reasons of clarity. These geometric references can also apply analogously to the other designs and bearing bushes 2 shown.

[0073] Fig. 5 shows a first line S1, which runs perpendicular to the central longitudinal axis Z and centrally through the connection flange 10. Also shown is the third line S3, which also runs perpendicular to the central longitudinal axis Z and through the axial center of the radial bearing 50. Furthermore, a second line S2 is shown, which also runs perpendicular to the central longitudinal axis Z and passes through the constriction point E in a constriction 42 of the elastomer body 51. If the radial bearing 50 has multiple constrictions 42, for example, if multiple elastomer tracks are present, the constriction point E is located in the constriction 42 that has a maximum axial distance from the third line S3. The constriction point E is therefore located on the side of the radial bearing 50 facing the axial bearing 30 and has a shortest axial distance to the first line S1. An axial distance D2 exists between the second line S2 and the third line S3.

[0074] Fig. 5 also shows a first pivot point P1, which lies equally on the central longitudinal axis Z and the first line S1. The pivot point P1 is the center of the associated first rotation circle K1, the diameter of which is dimensioned such that it lies tangentially to S1. Also visible is a third pivot point P3, which lies simultaneously on the central longitudinal axis Z and the third line S3. The third pivot point P3 is the center of the associated third rotation circle K3, whose diameter is dimensioned such that it also lies tangentially to S1. Axially between the pivot points P1 and P3 lies a second pivot point P2 on the central longitudinal axis Z. The second pivot point P2 is the center of the associated second rotation circle K2. The second pivot point P2 is defined by the largest radial diameter of the elastomer body 51. The position of point P2 on the central longitudinal axis Z must be chosen so that the second turning circle K2 is also tangential to S1.It is preferred that a resulting pivot point lies in that half of the axial distance D2 which is remote from the axial bearing 30. In . Fig. 5, such a pivot point would be found between P2 and P3. The first line S1 is, by definition, the tangent to each of the circles K1, K2, and K3.

[0075] A bearing bushing in which the resulting pivot point is the first pivot point P1 is comparatively hard and exhibits comparatively high compressive stresses in the axial bearing 30 during a cardanic movement of the bearing around P1. The radius of the associated first circle K1 is as large in the radial direction R as the axial distance between the constriction point E of the elastomer body 51 of the radial bearing 50 and the line S1. A bearing bushing in which the resulting pivot point is the second pivot point P2 is comparatively softer and exhibits comparatively lower compressive stresses in the axial bearing 30 during a cardanic movement around the point P2. The radius of the associated second circle K2 is as large in the radial direction R as the outer diameter D1 of the elastomer body 51 of the radial bearing 50.A bearing bushing in which the resulting pivot point is the third pivot point P3 is comparatively soft and exhibits comparatively low compressive stresses in the axial bearing 30 during a cardanic movement around the point P3. The radius of the corresponding third circle K3 is as large in the radial direction R as the axial distance from S1 to S3. The location of the pivot points P1, P2, and P3 in . Fig. 5 are for illustrative purposes.

[0076] The invention is not limited to one of the above-described embodiments, but can be modified in a variety of ways. All features and advantages apparent from the claims, the description, and the drawings, including structural details, spatial arrangements, and method steps, may be essential to the invention both individually and in a wide variety of combinations.

[0077] The scope of the invention includes all combinations of at least two of the features disclosed in the description, the claims and / or the figures.

[0078] To avoid repetition, features disclosed by the device should also be considered as disclosed by the method and claimable. Likewise, features disclosed by the method should be considered as disclosed by the device and claimable. List of reference symbols 2 bearing bush 4 inner sleeve 5 Hole 6 Outer sleeve 8 Intermediate area 10 Connection flange 11 gap 12 Frontal surface 14 Annular gap 16 paragraph 18 paragraph 20 paragraph 30 thrust bearings 31 elastomer bodies 32a thrust bearing package 32b thrust bearing package 34a Connecting ring disc 34b Connecting ring disc 36 Stiffening ring disc 38a Vault 38b cylindrical section 40 front side 42 Constriction 50 radial bearings 51 elastomer bodies 52 stiffening sleeve 54a Mounting sleeve 54b Mounting sleeve 56 hollow cylinder section 58 flange section 60 Recording structure 62 Elastomer skin 64 Radial stop 66 gap 68 Elastomer skin 70 Thickening 72 Thickening 74 Vaulting 76 Thickening 78 flange sleeve A axial direction D1 outer diameter D2 axial distance E Constriction point K1 turning circle K2 turning circle K3 turning circle L Storage separation level P1 pivot point P2 pivot point P3 pivot point R Radial direction S1 line S2 line S3 line U circumferential direction Z central longitudinal axis

Claims

[1] Bearing bush (2) through which a central longitudinal axis (Z) extends, comprising an inner sleeve (4), an outer sleeve (6) which circumferentially surrounds the inner sleeve (4) to form an intermediate region (8), an elastomeric axial bearing (30) which is arranged in the intermediate region (8), and an elastomeric radial bearing (50) which is arranged in the intermediate region (8), wherein a connecting flange (10) with two end faces (12) is arranged on the outer circumference of the inner sleeve (4), wherein an axial bearing package (32a, 32b) of the axial bearing (30) is connected to each of the two end faces (12), wherein the bearing bush (2) is penetrated in the radial direction (R) by a bearing parting plane (L) or a bearing parting surface, wherein the axial bearing (30) but the radial bearing (50) is not arranged on one side of the bearing parting plane (L) or the bearing parting surface and on the other side of the bearing parting plane (L) the radial bearing (50) is arranged, but the axial bearing (30) is not arranged,wherein the elastomer bodies (31, 51) of the axial bearing (30) and the radial bearing (50) are separate bodies., [2] Bearing bush (2) according to claim 1, characterized by that at least one of the axial bearing assemblies (32a, 32b), preferably each of the axial bearing assemblies (32a, 32b), has a connecting structure at its axial end region, preferably a connecting ring disc (34a, 34b). [3] Bearing bush (2) according to one of the preceding claims, characterized by that an annular gap (14) is formed between the inner sleeve (4) and each axial bearing package (32a, 32b), wherein preferably each annular gap (14) is formed without undercuts in the axial direction (A). [4] Bearing bush (2) according to one of the preceding claims, characterized by that at least one of the axial bearing assemblies (32a, 32b), preferably each of the axial bearing assemblies (32a, 32b), comprises a stiffening ring disc (36). [5] Bearing bush (2) according to one of the preceding claims, characterized by that the inner sleeve (4) has a shoulder (16) on the outer circumference against which the radial bearing (50) or the axial bearing (30) rests. [6] Bearing bush (2) according to one of the preceding claims, characterized by that the outer sleeve (6) has a shoulder (18) on the outer circumference side against which a receiving eye can rest and / or has a shoulder (20) on the inner circumference side against which the axial bearing (30) rests. [7] Bearing bush (2) according to one of the preceding claims, characterized by that a mounting sleeve (54b) of the radial bearing (50) rests against the axial bearing (30) so that it can be in axial force flow with the axial bearing (30) and / or can be axially clamped by means of the outer sleeve (6) and thus both bearings (30, 50) are supported against each other in the axial direction (A). [8] Bearing bush (2) according to one of the preceding claims, characterized bythat, viewed longitudinally, an imaginary circle of rotation (K1, K2, K3) with an associated pivot point (P1, P2, P3) on the central longitudinal axis (Z) of the bearing bush (2) is tangent to a first line (S1) which runs perpendicular to the central longitudinal axis (Z) and through the connecting flange (10), and the associated pivot point (P1, P2, P3) lies between a second line (S2) which runs perpendicular to the central longitudinal axis (Z) and through a constriction point (E) of the elastomer body (51) of the radial bearing (50) facing the axial bearing, and a third line (S3) which runs perpendicular to the central longitudinal axis (Z) and through the axial center of the radial bearing (50).

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