Outer sleeve for a bearing for a chassis of a vehicle, bearing, bearing arrangement, tool and method for pressing in a bearing

Abstract

Outer sleeve (14) for a bearing (100) for a chassis of a vehicle, wherein the outer sleeve (14) has at least two predefined tapers (13.1, 13.2), wherein the two tapers (13.1, 13.2) are spaced apart from one another in the width (BA) of the outer sleeve (14), wherein the at least two predefined tapers (13.1, 13.2) are designed to deform the outer sleeve (14) in regions under a predefined pressing pressure when the bearing (100) is pressed into a bearing seat (20), wherein each of the at least two predefined tapers (13.1, 13.2) has an outer recess (16.1, 16.2) and an inner recess (17.1, 17.2), wherein the outer recess (16.1, 16.2) is in the outer circumferential surface and the internal recess (17.1, 17.2) in the inner surface.

Description

[0001] The invention generally relates to the field of bearings, such as rubber-metal bearings, for a vehicle chassis. More specifically, the invention relates to an outer sleeve for a bearing for a motor vehicle chassis, a bearing with such an outer sleeve, a bearing assembly with such a bearing, a tool, and a method for pressing in such a bearing.

[0002] In automotive chassis, bearings such as rubber-metal mounts are essential for the chassis properties, as they determine the vehicle's elastokinematics. These mounts must absorb the forces and moments that occur during operation. Furthermore, rubber-metal mounts are used for acoustic and vibration isolation. The common design is the so-called round or bushing mount. Chemical adhesion promoters can create a permanent bond between the metal and the elastomer.

[0003] The elastomer is often made from natural rubber—also known as rubber. The other components of the bearing, such as the core and outer sleeve, are usually made of metal, preferably aluminum due to its lower specific weight and advantages in terms of manufacturing and processing.

[0004] The forces and moments occurring during driving must be absorbed by the bearing without axial forces causing the bearing to shift in its seat. Failure to ensure a tight fit can seriously compromise driving safety.

[0005] Bearings, and especially rubber-to-metal bearings, are generally designed in such a way that, based on experience, an interference fit is achieved by matching the diameter ratios of the bearing and bearing seat or by incorporating additional measures such as roughening. However, due to special, unexpected maneuvers, accidents, or a combination of unfavorable circumstances, a bearing may move out of its bearing seat or the expected insertion and removal forces may not be achieved during production.

[0006] For example, the bearing can be at least partially secured mechanically or chemically against slipping out, see, for example, DE 10 2018 106 365 A1. However, such measures always involve additional material and mechanical effort, which can sometimes significantly increase manufacturing costs and result in a substantial increase in costs.

[0007] From JP 2023- 23 490 A a vibration-damping bushing is known by which an input vibration in a feed direction of the bushing can be reduced.

[0008] From JP 2009- 270 586 A a vibration isolator and a vibration isolator assembly are known which can be used in motor vehicles and industrial machines.

[0009] From DE 201 15 183 U1 a rubber-mounted sleeve with a metal outer ring is known.

[0010] It is therefore an object of the present invention to at least partially remedy the disadvantages described above. In particular, the present invention aims to provide additional protection against the bearing slipping out without significantly increasing the material or manufacturing costs.

[0011] The above object is achieved by an outer sleeve for a bearing for a chassis of a vehicle having the features of claim 1, by a bearing having the features of claim 8, by a bearing arrangement having the features of claim 10, by a tool having the features of claim 12 and by a method for pressing in a bearing having the features of claim 13. Further features and details of the invention emerge from the subclaims, the description and the drawings. Features and details that are described in connection with the outer sleeve according to the invention naturally also apply in connection with the bearing according to the invention, the bearing arrangement, the tool and / or the method and vice versa, so that with regard to the disclosure of the individual aspects of the invention, reference is or can always be made reciprocal.

[0012] Embodiments of the invention advantageously provide an improved outer sleeve for a bearing for a vehicle chassis. Such an outer sleeve can increase the security against the bearing slipping out.

[0013] A first aspect of the present invention relates to an outer sleeve for a bearing for a vehicle chassis. The outer sleeve is, in particular, cylindrical. The outer sleeve has at least two predefined tapers. The two tapers are spaced apart from each other across the width of the outer sleeve. The at least two predefined tapers are configured to deform the outer sleeve in regions under a predefined pressure when the bearing, in particular the outer sleeve, is pressed into a bearing seat.

[0014] In other words, an outer sleeve can be provided with a specific contour and a specific deformation capacity. Contouring can be incorporated into the outer sleeve in the form of circumferential tapers. These tapers can be described as weak points, as their primary purpose is to yield when the bearing or outer sleeve is pressed into a bearing seat, allowing deformation of the outer sleeve. The resulting deformation of the outer sleeve can provide additional mechanical security against the bearing slipping out of the bearing seat. The resulting deformation is preferably plastic or irreversible.

[0015] The outer sleeve can be an outer sleeve of a rubber-metal bearing. The outer sleeve can therefore preferably be made of aluminum. The outer sleeve can be cylindrical and therefore have an inner circumferential surface and an outer circumferential surface, wherein the at least two tapers can be introduced into the contour of the outer sleeve starting from the inner circumferential surface and / or starting from the outer circumferential surface. The width of the outer sleeve generally refers to the extent in the axial direction of the outer sleeve and the bearing. The at least two tapers are preferably arranged closer to the two end faces of the outer sleeve than from the center in the axial direction of the outer sleeve.

[0016] The outer sleeve described above and below can thus advantageously ensure non-slip mounting of the bearing in a bearing seat. The outer sleeve, in particular the deformable outer sleeve, can provide mechanical slip resistance. Such an outer sleeve can advantageously secure the bearing to the bearing seat flush with the outside. The additional mechanical security achieved in this way can be easily integrated into the bearing joining process, and no additional operations are required. Furthermore, no additional mechanical elements are required to provide additional mechanical securing of the bearing in the bearing seat.

[0017] According to one embodiment of the outer sleeve, the outer sleeve is foldable, bendable, and / or bendable at the at least two predefined tapers. In particular, the outer sleeve can be foldable, bendable, and / or bendable in such a way that a clamp is created that can clamp onto the bearing seat and thus provide additional mechanical fastening in the axial direction. The outer sleeve can be foldable, bendable, and / or bendable at the at least two predefined tapers, in particular during pressing with a predetermined pressing pressure and / or with a predetermined force.

[0018] According to the invention, each of the at least two predefined tapers has an outer recess and an inner recess. The respective outer recess is located in the outer surface, and the respective inner recess is located in the inner surface. The recesses can also be troughs. It should be noted that these are not bulges or protrusions.

[0019] According to one embodiment of the outer sleeve, the distance between the two respective outer recesses of the at least two predefined tapers is greater than the distance between the two respective inner recesses of the at least two predefined tapers. This allows the deformation of the outer sleeve to be predefined more accurately. In particular, this makes it possible to achieve a predefined bend, a predefined kink, and / or a predefined folding of the outer sleeve in the radially outward direction. Deforming the outer sleeve outwards, i.e., away in the radial direction, can advantageously enable mechanical fastening of the outer sleeve or the bearing to the bearing seat.

[0020] According to one embodiment of the outer sleeve, the outer recess(es) and / or the inner recess(es) have a V-shaped cross-section. Alternatively, the recesses can form a groove with a conical section. Other cross-sections for the recesses are also conceivable. The cross-section of the outer recesses can differ from the cross-section of the inner recesses. The depth of the recesses can correlate with the deformability of the outer sleeve. If the outer sleeve is intended to be deformable even at low pressing pressures or forces, the recesses can have a larger cross-section, e.g., be deeper, than recesses intended to enable deformation of the outer sleeve at higher pressing pressures or forces.

[0021] According to one embodiment of the outer sleeve, the respective at least two predefined tapers extend over the entire circumference of the outer sleeve. In other words, the at least two predefined tapers are circumferential on the outer sleeve. This further increases the security against the outer sleeve or bearing slipping out of the bearing seat. In fact, the mechanical security that can be ensured by such a deformable outer sleeve can extend over the entire circumference of the outer sleeve.

[0022] According to one embodiment of the outer sleeve, the outer sleeve is slotted. In other words, the preferred design is not the classic round bushing, but rather the so-called slotted bearing. This allows the use of strip material for the outer sleeve. This also makes it very easy to incorporate contouring, i.e., tapering, into the outer sleeve during production.

[0023] According to one embodiment of the outer sleeve, the outer sleeve is flattened, beveled, and / or rounded on a first end face and / or a second end face, in particular flattened, beveled, and / or rounded on the inside. This allows the deformability of the outer sleeve to be predefined more precisely. Furthermore, bending, folding, and / or buckling of the outer sleeve at the at least two predefined tapers in a radially outward direction can be carried out more precisely. The bending in a radially outward direction can thus be supported by the flattened, beveled, and / or rounded first and / or second end face of the outer sleeve. The mechanical anti-slip properties that can be provided by the deformation of the outer sleeve can thus be improved.

[0024] A second aspect of the present disclosure relates to a bearing for a chassis of a vehicle. The bearing comprises a bearing core, a rubber body arranged around the bearing core, and a metallic outer sleeve arranged around the rubber body, as described above and below.

[0025] All advantages explained above with regard to the outer sleeve apply equally to the bearing according to the invention.

[0026] According to one embodiment of the bearing, the bearing further comprises an intermediate sleeve arranged between the outer sleeve and the rubber body.

[0027] A third aspect of the present invention relates to a bearing assembly for a power plant of a motor vehicle. The bearing assembly comprises a bearing, as described above and below, and a bearing seat. The bearing is seated in the bearing seat, and the outer sleeve of the bearing is deformed at the respective at least two predefined tapers.

[0028] According to one embodiment of the bearing arrangement, the bearing is secured flush with the outside of the bearing seat, in particular in a non-slip manner.

[0029] A fourth aspect of the present invention relates to a tool for pressing a bearing, as described above and below, into a bearing seat. The tool comprises a punch, a counterpart, and a spring arranged in the punch. The spring is configured to support deformation of the outer sleeve during the pressing-in of the bearing.

[0030] A fifth aspect of the present invention relates to a method for pressing a bearing, as described above and below, into a bearing seat, in particular by means of a tool, as described above and below, comprising the following steps: • Positioning the bearing on a first side of the bearing seat, • Positioning the punch and spring on the bearing, with the punch in contact with the outer sleeve of the bearing, • Positioning the counterpart of the tool on the second side of the bearing seat opposite the first, • Applying a pressing pressure in the pressing direction on the punch to press the bearing into the bearing seat, wherein when applying the pressing pressure the at least two tapers of the outer sleeve lead to a deformation of the outer sleeve, and • When a predefined counterforce exerted by the counterpart is reached, stop applying the pressing pressure.

[0031] All features described above and below with respect to one aspect of the present invention apply equally to all other aspects of the present invention.

[0032] Further advantages, features, and details of the invention will become apparent from the following description, which describes embodiments of the invention in detail with reference to the drawings. The features mentioned in the claims and in the description may be essential to the invention individually or in any combination. They show: Fig. 1 a schematic representation of a bearing according to an embodiment, Fig. 2 a schematic representation of a bearing arrangement according to an embodiment, Fig. 3 a schematic perspective view of an outer sleeve according to an embodiment, Fig. 4 a flattened cross-section of an outer sleeve according to an embodiment, Fig. 5 to 7 a schematic representation of flattened cross sections of an outer sleeve according to different embodiments, Fig. 8 a schematic representation of a bearing according to an embodiment, Fig. 9 a schematic representation of a bearing arrangement according to an embodiment, and Fig. 10 a schematic representation of a method step of a method according to an embodiment.

[0033] Similar, similarly acting, identical, or identically functioning elements are provided with the same reference numerals in the figures. The figures are merely schematic and not drawn to scale.

[0034] Fig. 1 shows a schematic representation of a bearing 100 according to an embodiment. The bearing 100 of the Fig. 1 comprises a bearing core 10, a rubber body 12, and an outer sleeve 14. The outer sleeve 14 is preferably made of aluminum. It can therefore be a rubber-metal bearing. Fig. 1 shows a cross-section along the radial axis of the bearing 100. The bearing 100 is therefore symmetrical about the axial axis in a cross-sectional view. The bearing 100 of the Fig. 1 is designed or constructed to be pressed in the axial direction into a bearing seat 20. The pressing direction R is schematically indicated by an arrow in Fig. 1 shown.

[0035] The outer sleeve 14 has at least two predefined tapers 13.1, 13.2, which are spaced apart from one another in the width BA of the outer sleeve 14, i.e., along the axial axis. The at least two predefined tapers 13.1, 13.2 are configured to deform the outer sleeve 14 in regions under a predefined pressing pressure when the bearing 100 is pressed in the pressing direction R into a bearing seat 20. The outer sleeve 14 is foldable, kinkable, and / or bendable at the at least two predefined tapers 13.1, 13.2. The at least two tapers 13.1, 13.2 preferably extend over the entire circumference of the outer sleeve 14. In other words, the tapers 13.1, 13.2 are circumferential. In addition, the tapers 13.1, 13.2 in the embodiment of the Fig. 1 parallel to the end face 15.1, 15.2 of the outer sleeve 14, or run parallel to the end face 15.1, 15.2 of the outer sleeve 14.

[0036] Fig. 2 shows a schematic representation of a bearing assembly 200 according to an embodiment. The bearing assembly 200 has a bearing seat 20 in which the bearing 100 is seated. Unless otherwise described, the bearing 100 of the Fig. 2 the same elements and / or components as the bearing 100 of the Fig. 1. As it is in Fig. As can be seen in Figure 2, the two tapered portions 13.1, 13.2 have caused the outer sleeve 14 of the bearing 100 to bend, specifically in such a way that the outer sleeve 14 can ensure mechanical security against the bearing 100 slipping out of the bearing seat 20. The outer sleeve 14 has deformed and / or bent, particularly outwardly, i.e., in the radial direction. The portion of the outer sleeve 14 located in the bearing seat 20 preferably remains intact and therefore does not need to be supported.

[0037] It may prove advantageous to adjust the distance between the at least two tapers 13.1, 13.2 to the width Bs of the bearing seat 20, so that the bending and / or deformation at the outer edges or the end face 15.1, 15.2 of the bearing seat 20 can be generated by pressing the bearing 100 into the bearing seat 20. The width BA of the outer sleeve 14 (see Fig. 1) is therefore preferably larger than the width Bs of the bearing seat 20.

[0038] Fig. Figure 3 shows a schematic perspective view of an outer sleeve 14 according to an embodiment. Unless otherwise described, the outer sleeve 14 of the Fig. 3 the same elements and / or components as the outer sleeve 14 of the Fig. 1 and Fig. 2. The outer sleeve 14 of the Fig. 3 has a slot 18. This can be referred to as a slotted outer sleeve 14. The outer sleeve 14 has a first end face 15.1 and a second end face 15.2. The at least two predefined tapers 13.1, 13.2 each have an inner recess 17.1, 17.2 and an outer recess 16.1, 16.2. The inner recesses 17.1, 17.2 are arranged in the inner surface of the outer sleeve 14, and the outer recesses 16.1, 16.2 are arranged in the outer surface.

[0039] Fig. 4 shows a flattened cross-section of an outer sleeve 14 according to an embodiment. Unless otherwise described, the outer sleeve 14 of the Fig. 4 the same elements and / or components as the outer sleeve 14 of the Fig. 1 to 3. The outer recesses 16.1, 16.2 are spaced apart from one another by a predetermined distance A. The inner recesses 17.1, 17.2 are spaced apart from one another by a predetermined distance I, wherein the distance A between the outer recesses 16.1, 16.2 is greater than the distance I between the inner recesses 17.1, 17.2. This can advantageously enable the bending and / or at least partial deformation of the outer sleeve 14 to occur outwards. The inner and / or outer recesses 16.1, 16.2 can have a V-shaped cross-section. Other cross-sections for the recesses 16.1, 16.2, 17.1, 17.2 are also conceivable. For example, the recesses 16.1, 16.2, 17.1, 17.2, whether the inner and / or outer recesses 16.1, 16.2, 17.1, 17.2, can be groove-shaped. The inner and outer recesses 16.1, 16.2 can be formed with different depths. In particular, the outer recesses 16.1, 16.2 can, for example, extend over half the thickness of the outer sleeve 14, wherein the thickness can be measured in the radial direction of the bearing 100.

[0040] Fig. 5 to 7 show schematic representations of flattened cross sections of an outer sleeve 14 according to different embodiments. Unless otherwise described, the outer sleeves 14 of the Fig. 5 to 7 the same elements and / or components as the outer sleeve 14 of the Fig. 1 to 4. The first end face 15.1 and / or the second end face 15.2 of the outer sleeve 14 can be beveled and / or rounded. This has the advantage that a desired or predefined bending or deformation of the outer sleeve 14 can be better controlled and / or supported. The bevel 19.1 and / or rounding 19.2 is therefore preferably arranged on the inside of the outer sleeve 14.

[0041] Fig. Figure 8 shows a schematic representation of a bearing 100 according to an embodiment. Unless otherwise described, the bearing 100 of the Fig. 8 the same elements and / or components as the outer sleeve 14 of the Fig. 1 and Fig. 2. The camp 100 of the Fig. 8 further includes an intermediate sleeve 11. The design of an intermediate sleeve 11 is inherent in the bearing design and is generally not required for rubber-metal bearings.

[0042] Fig. Fig. 9 shows a schematic representation of a bearing arrangement 200 according to an embodiment. Unless otherwise described, the bearing arrangement of the Fig. 9 the same elements and / or components as the bearing arrangement 200 of the Fig. 2. The bearing 100 is pressed into the bearing seat usually by means of a punch 22 of a tool 23 in the pressing direction R, which presses on the outer sleeve 14 of the bearing 100 at a contact point K, in particular on an end face 15.1, 15.2 of the outer sleeve 14. In practice, the pressing-in process is continued until a force limit is reached. This is reached when approaching a counterpart 26 of the tool 23 and indicates that the bearing 100 can no longer be pushed into the bearing seat 20. This concludes the pressing-in process. As a result of friction, an increase in force in the axial direction can occur. The punch 22 of the tool 23 presses on the end face 15.1, 15.2 of the outer sleeve 14 and causes the at least two tapers to act as predetermined buckling points and / or as predefined weak points. The outer sleeve 14 bends at at least two predefined tapers 13.1, 13.2, in particular at the recesses 16.1, 16.2, 17.1, 17.2 and is further folded due to the force exerted by the plunger 22. To prevent the fold from folding over, a spring element or spring 24 engaging in the inner recess 17.1, 17.2 supports it. This spring 24, arranged and / or secured in the plunger 22, also accommodates the bearing 100.

[0043] Fig.10 shows a schematic representation of a method step of a method according to an exemplary embodiment. In the method step of a method for pressing a bearing 100 into a bearing seat 20 shown here, a pressing pressure, or a force, is applied in the pressing direction R to the punch 22 of the tool 23. Upon application of the pressing pressure S1, the at least two tapers 13.1, 13.2 of the outer sleeve 14 lead to a deformation or bending of the outer sleeve 14. In other words, the previously folded side of the outer sleeve 14 is pushed through completely. The outer sleeve 14 comes into contact with the counterpart 26 of the tool 23, which is positioned at a predefined distance from the bearing seat 20 to allow the travel of the outer sleeve 14. The folding process can begin at the counterpart 26 of the tool 23 and continue until complete unfolding or bending has occurred or the force limit required for this has been reached.The bearing 100 is now secured flush with the outside (see step S2). The bearing 100 sits in the bearing seat 20 with the stamped outer sleeve 14. List of reference symbols 10 bearing core 11 Intermediate sleeve 12 rubber bodies 13.1, 13.2 Rejuvenation 14 Outer sleeve 15.1 first front side 15.2 second front side 16.1, 16.2 external recess 17.1, 17.2 internal recess 18 slot 19.1 Bevel 19.2 Rounding 20 bearing seat 22 stamps 23 tools 24 springs 26 counterpart 100 warehouses 200 bearing arrangement A Distance between the outer recesses I Distance between the inner recesses R Pressing direction BA Width of the outer sleeve Bs Width of the bearing seat

Claims

[1] Outer sleeve (14) for a bearing (100) for a chassis of a vehicle, wherein the outer sleeve (14) has at least two predefined tapers (13.1, 13.2), wherein the two tapers (13.1, 13.2) are spaced apart from one another in the width (BA) of the outer sleeve (14), wherein the at least two predefined tapers (13.1, 13.2) are designed to deform the outer sleeve (14) in regions under a predefined pressing pressure when the bearing (100) is pressed into a bearing seat (20), wherein each of the at least two predefined tapers (13.1, 13.2) has an outer recess (16.1, 16.2) and an inner recess (17.1, 17.2), wherein the outer recess (16.1, 16.2) is in the outer surface and the inner recess (17.1, 17.2) is in the inner surface. [2] Outer sleeve (14) according to claim 1, wherein the outer sleeve (14) is foldable, bendable and / or bendable at the at least two predefined tapers (13.1, 13.2). [3] Outer sleeve (14) according to one of the preceding claims, wherein the distance (A) between the two respective outer recesses (16.1, 16.2) of the at least two predefined tapers (13.1, 13.2) is greater than the distance (I) between the two respective inner recesses (17.1, 17.2) of the at least two predefined tapers (13.1, 13.2). [4] Outer sleeve (14) according to one of the preceding claims, wherein the outer recess(es) (16.1, 16.2) and / or the inner recess(es) (17.1, 17.2) have (have) a V-shaped cross-section. [5] Outer sleeve (14) according to one of the preceding claims, wherein the respective at least two predefined tapers (13.1, 13.2) extend over the entire circumference of the outer sleeve (14). [6] Outer sleeve (14) according to one of the preceding claims, wherein the outer sleeve (14) is slotted. [7] Outer sleeve (14) according to one of the preceding claims, wherein the outer sleeve (14) is flattened, bevelled and / or rounded on a first end face (15.1) and / or a second end face (15.2), in particular on the inside. [8] Bearing (100) for a chassis of a vehicle, comprising a bearing core (10), a rubber body (12) arranged around the bearing core (10) and a metallic outer sleeve (14) arranged around the rubber body (12) according to one of the preceding claims. [9] Bearing (100) according to claim 8, further comprising an intermediate sleeve (11) arranged between the outer sleeve (14) and the rubber body (12). [10] Bearing arrangement (200) for a power plant of a motor vehicle, comprising a bearing (100) according to one of claims 8 and 9 and a bearing seat (20), wherein the bearing (100) is seated in the bearing seat (20) and the outer sleeve (14) of the bearing (100) is deformed at the respective at least two predefined tapers (13.1, 13.2). [11] Bearing arrangement (200) according to claim 10, wherein the bearing (100) is secured externally flush with the bearing seat (20), in particular is secured in a non-slip manner. [12] Tool (23) for pressing a bearing (100) according to one of claims 8 and 9 into a bearing seat (20), comprising a punch (22), a counterpart (26) and a spring (24) arranged in the punch (22), wherein the spring (24) is designed to support a deformation of the outer sleeve (14) when the bearing (100) is pressed in. [13] Method for pressing a bearing (100) according to one of claims 8 and 9 into a bearing seat (20), in particular by means of a tool (23) according to claim 12, comprising the following steps: • Positioning the bearing (100) on a first side of the bearing seat (20), • Positioning the punch (22) and the spring (24) on the bearing (100), wherein the punch (22) is in contact with the outer sleeve (14) of the bearing (100), • Positioning the counterpart (26) of the tool (23) on the second side of the bearing seat (20) opposite to the first, • (S1) applying a pressing pressure in the pressing direction (R) to the punch (22) in order to press the bearing (100) into the bearing seat (20), wherein, upon application of the pressing pressure, the at least two tapers (13.1, 13.2) of the outer sleeve (14) lead to a deformation of the outer sleeve (14), and • (S2) when a predefined counterforce exerted by the counterpart (26) is reached, stop applying the pressing pressure.

Images