Bearings, especially elastomer bearings

Abstract

Bearing (1), in particular elastomeric bearing (1), in the form of a bearing bushing extending along a longitudinal axis (X), a radial direction (R) perpendicular to the longitudinal axis (X), and a circumferential direction (U) rotating around the longitudinal axis (X), comprising an outer part (10) in the form of an outer ring, an inner part (15) radially within the outer part (10), and at least one support body (12) arranged radially between the outer part (10) and the inner part (15), characterized in that the support body (12) has at least one additional mass (13) extending at least substantially perpendicular to the support body (12) and being movable at least sectionally parallel to the support body (12) in the radial direction (R), wherein the bearing has a plurality of support bodies (12), each of which is arranged between the outer part (10) and the inner part (15), wherein several support bodies (12), in particular all support bodies (12),have at least one additional mass (13) which extends at least substantially perpendicular to the respective support body (12) and is movable at least sectionally parallel to the respective support body (12) in the radial direction (R), wherein the at least one additional mass (13) extends into a space between two support bodies (12).

Description

The present invention relates to a bearing, in particular an elastomeric bearing, according to the preamble of claim 1 and to a vehicle with such a bearing according to claim 10. Elastomeric elements have long been used in many technical fields to dampen vibrations between two rigid bodies. This includes land vehicles such as passenger cars and trucks, where such damping elements are used, for example, as engine mounts, transmission mounts, or shaft mounts. In each case, the elastomeric element is typically positioned between the engine, transmission, or shafts on one side and the vehicle chassis on the other, so that vibrations from the respective drivetrain component, such as the engine, transmission, or shaft, can be dampened or even eliminated relative to the vehicle chassis. Such bearings are usually designed according to static and low-frequency specifications, since on the one hand a certain static load of the component to be damped must be absorbed safely and permanently, and on the other hand the vibrations to be damped or eliminated are usually in a low-frequency range up to about 25 Hz. Higher-frequency vibrations always occur during operation, which are influenced by the static and low-frequency design. However, the high-frequency behavior of the bearing cannot be influenced without altering its static and low-frequency behavior. Therefore, such bearings are typically designed according to their static and low-frequency specifications, and the high-frequency behavior of the bearing is accepted as an inherent consequence. However, a disadvantage here is that the high-frequency excitations, for example from a vehicle's chassis, can generate acoustic phenomena that may disturb or irritate the driver. This can reduce driving comfort. DE 32 14 037 A1 describes a mounting for a motor vehicle which has a circumferential shape with a radially inner first elastic wall and a radially outer second elastic wall as well as an intermediate mass which is arranged between the first and second elastic wall. JP H03 - 117 137 U describes an anti-vibration body with an inner part and an outer part, as well as an elastic support body that has a protruding part to influence a resonant frequency. An object of the present invention is to provide a bearing of the type described above such that its high-frequency vibration behavior can be influenced, and in particular reduced. Specifically, the frequency of a first resonance point, and especially of a first and second resonance point, is to be reduced. Additionally or alternatively, the high-frequency vibration behavior of such a bearing is to be influenced more strongly than its low-frequency vibration behavior. This is to be made possible, in particular, for a bearing bushing. This is to be achieved, in particular, for an engine mount and / or for a transmission mount, especially for an engine mount bushing and / or for a transmission mount bushing. This is to be made possible, in particular, for use in an electrically powered vehicle. In particular, the dynamic stiffness of such a bearing is to be improved. The problem is solved according to the invention by a bearing with the features according to claim 1 and by a vehicle with the features according to claim 10. Advantageous embodiments are described in the dependent claims. The present invention therefore relates to a bearing, in particular an elastomeric bearing, comprising an outer part, an inner part, and at least one support element arranged between the outer part and the inner part. The bearing can, in particular, be an engine bearing, a gearbox bearing, or a shaft bearing. The bearing can, in particular, be designed as a bushing. The bearing according to the invention is characterized in that the support body has at least one additional mass which extends at least substantially perpendicular to the support body and is designed to be movable at least partially parallel to the support body. In other words, at least one support body of the bearing according to the invention has at least one body which represents an additional mass that is designed to be movable at least partially parallel to the support body in the radial direction. In particular, this additional mass can project into a space, which can be formed, for example, by the outer part, the inner part, and / or the support body, and be movable there at least partially as described above. The additional mass is preferably smaller in volume and / or weight, and in particular significantly smaller, than the support body itself.The bearing comprises a plurality of support bodies, each arranged between the outer and inner parts, wherein several support bodies, in particular all support bodies, have at least one additional mass which extends at least substantially perpendicular to the respective support body and is designed to be movable in the radial direction at least partially parallel to the respective support body. The at least one additional mass extends into a space between two support bodies. The present invention is based on the understanding that an additional movable element of the support body, which is movable relative to it, can dampen or eliminate vibration frequencies other than those for which the support body itself is designed. This allows, in particular, higher-frequency vibrations to be dampened or eliminated more effectively than can be achieved by the support body itself. The vibration frequency to be dampened or eliminated by the additional mass can be influenced by the design of the additional mass with regard to its shape, weight, and / or arrangement on the support body, and thus tailored to a specific frequency depending on the application. This can be done, in particular, specifically to achieve a resonant frequency. The damping effect of the support structure can thus be improved or extended to overcome or at least reduce the disadvantages described above, or to partially or completely solve the aforementioned problem. In particular, the higher-frequency stiffness of the bearing can be specifically influenced and tuned. The overall frequency response, and especially that of higher-frequency vibrations, particularly higher-frequency resonance frequencies, can be shifted. This can be achieved very simply and cost-effectively through purely passive measures using the additional masses. Furthermore, any influence on other properties of the bearing can be avoided or at least minimized. According to one aspect of the present invention, the additional mass is designed to produce a counter-vibration to the supporting body. This can promote the realization of the previously described properties and advantages and, in particular, enhance their effect. The counter-vibrations can modify the vibration behavior of the bearing or the supporting body, so that its stiffness can be reduced or increased. According to a further aspect of the present invention, the additional mass has a thickening pointing away from the supporting body. This can lead to a particularly pronounced amplitude of the movement of the additional mass with a comparatively low weight and / or a comparatively small volume, so that the properties described above can be implemented with the least possible effort, low moving weight, and / or low required installation space. According to a further aspect of the present invention, the thickening pointing away from the support body is arranged at the end of the additional mass pointing away from the support body. This can enable a particularly compact implementation of the properties described above. It can also allow for the most effective possible mobility or vibration capability of the additional mass relative to the support body. According to a further aspect of the present invention, the additional mass has a web-like extension that connects the support body to the thickening. This can increase the relative mobility of the thickening of the additional mass relative to the support body, so that the effect of this movement can also be increased without increasing the weight of the additional mass for the same purpose. This can also avoid the increase in the installation space required for the additional mass that might otherwise be necessary. According to a further aspect of the present invention, the additional mass is designed to influence a predetermined frequency of the bearing, in particular a resonant frequency, by means of its mobility parallel to the supporting body. Such a design can be implemented depending on the application and, for example, by calculation, simulation, or iterative testing. Changing a resonant frequency can particularly effectively influence the vibration behavior of the bearing. According to a further aspect of the present invention, the additional mass is formed integrally with the support body. This can enable a secure connection and / or simpler manufacturing than with a one-piece design consisting of two separately manufactured and subsequently joined elements. According to a further aspect of the present invention, the support body and / or the additional mass is made of an elastomeric material. This can enable a vibration-damping or vibration-absorbing effect using simple, robust, and / or cost-effective means. According to a further aspect of the present invention, the bearing has a plurality of support elements, each arranged between the outer and inner parts, wherein several support elements, and in particular all support elements, have at least one additional mass which extends at least substantially perpendicular to the respective support element and is designed to be movable at least partially parallel to the respective support element. The plurality of support elements allows their effect to be utilized multiple times. Equipping several, and in particular all, support elements with an additional mass as described above can enable the corresponding multiple use of this effect. According to a further aspect of the present invention, at least two additional masses are configured differently. This allows different movements or vibrations of the two additional masses to be implemented, so that different frequencies can be dampened or eliminated. This can increase the versatility of the present invention. The present invention also relates to a vehicle, in particular a land vehicle, with at least one bearing as described above, wherein the bearing is arranged between a vibration-generating component and another component of the vehicle. This allows the properties and advantages described above to be implemented and utilized in a vehicle, and in particular in a land vehicle such as a passenger car and / or a truck. Two exemplary embodiments and further advantages of the invention are explained below in connection with the following figures. Figure 1 shows a schematic cross-section of a known bearing in the form of a bearing bushing; Figure 2 shows a schematic cross-section of a bearing according to the invention in the form of a bearing bushing according to a first exemplary embodiment; Figure 3 shows a detail view of Figure 2; Figure 4 shows a schematic perspective view of a bearing according to the invention in the form of a bearing bushing according to a second exemplary embodiment; Figure 5 shows a schematic cross-section of Figure 4; and Figure 6 shows a detail view of Figure 5. The above figures are described in cylindrical coordinates with a longitudinal axis X, a radial direction R perpendicular to the longitudinal axis X, and a circumferential direction U around the longitudinal axis X. Fig. 1 shows a schematic cross-section of a known bearing 1 in the form of a bearing bushing 1, which in this case is more precisely a transmission bearing bushing 1. The bearing bushing 1 has an outer part 10, which is cylindrical as an outer ring 10. Radially inside the outer ring 10, the bearing bushing 1 has an inner part 15, which is essentially cylindrical as an inner part 15. The outer ring 10 is designed to be rigidly connected to a first rigid body, e.g., in the form of a chassis, for example, of a car or truck (not shown). The inner part 15 is designed to be rigidly connected to a second rigid body, e.g., in the form of an engine of the car or truck (not shown). The engine can be an internal combustion engine, a hybrid engine, or an electric motor. The engine can be rigidly connected to the inner part 15 by means of a receptacle 16. Radially between the outer ring 10 and the inner part 15, four support bodies 12 are arranged, each connecting the outer ring 10 and the inner part 15. The four support bodies 12 are arranged in a substantially uniform distribution along the circumferential direction U and at substantially uniform intervals from each other, so that four gaps 14 are formed, each of which is bounded radially outwards by a section of the outer ring 10, radially inwards by a section of the inner ring 15, and in the circumferential direction U on each side by one of the four support bodies 12. The support elements 12 are each made of an elastomeric material such as rubber, and are therefore also referred to as elastomeric support elements 12, elastomeric parts 12, or shock absorbers 12. The elastomeric support elements 12 can undergo elastic deformation, primarily in the radial direction R, thereby absorbing tensile or compressive forces between the outer ring 10 and the inner part 15. This can dampen or eliminate vibrations between the outer ring 10 and the inner part 15. The elastomeric support elements 12 are typically arranged and designed, in particular shaped, such that the static load, which is rigidly connected to the inner part 15, can be absorbed by the elastomeric support elements 12. This also applies to low-frequency vibrations, which can be absorbed and damped or eliminated by the elastomeric support elements 12. However, higher-frequency vibrations cannot be damped or eliminated by such known bearing bushings 1 or their elastomeric support elements 12. Fig. 2 shows a schematic cross-section of a bearing 1 according to the invention in the form of a bearing bushing 1 according to a first embodiment. Fig. 3 shows a detailed view of Fig. 2. The bearing bushing 1 according to the first embodiment shown in Figs. 2 and 3 corresponds essentially to the known bearing bushing 1 of Fig. 1, with the difference that the two elastomeric support bodies 12, which are arranged at the bottom left and bottom right in the illustrations of Figs. 1 and 2, each have an additional mass 13 facing each other, which is formed integrally with the respective elastomeric support body 12 and thus made of its elastomeric material. Each additional mass 13 has a web-like extension 13a, which extends in the circumferential direction U into the space 14 and widens at its end to a thickening 13b in the radial direction R, which is spherical in shape. The two additional masses 13, and in particular their end-end thickenings 13b, can vibrate parallel to the respective support body 12, essentially in the radial direction R, which can lead to counter-vibrations to the vibrations of the elastomeric support bodies 12 themselves. This can result in the damping or cancellation of vibrations of higher frequencies than is possible by the elastomeric support bodies 12. This can enable the damping or cancellation of further, and in particular higher-frequency, vibrations than is currently known from the use of the elastomeric support bodies 12 alone. The end-end thickenings 13b of the additional masses 13 can increase the amplitude of these counter-vibrations, thereby enabling particularly effective damping or cancellation of further, and especially higher-frequency, vibrations. This can also be implemented in a comparatively compact manner. Fig. 4 shows a schematic perspective view of a bearing 1 according to the invention in the form of a bearing bushing 1 according to a second embodiment. Fig. 5 shows a schematic cross-section of Fig. 4. Fig. 6 shows a detailed view of Fig. 5. In this case, an additional mass 13 is arranged on each elastomeric support body 12, as previously described with reference to the first embodiment. Two additional masses 13 are arranged facing each other in the same gap 14, with the additional masses 13 being contained in the two lateral gaps 14. The properties of the invention described above can also be implemented in this way. The four spaces 14 each have a stop element 17, which is made of the same elastomeric material as the elastomeric support bodies 12 on the inner part 15 and is oriented radially outwards towards the inside of the outer ring 10. This allows for damped elastic contact between the inner part 15 and the outer ring 10 if vibrations with sufficiently large amplitudes occur between the inner part 15 and the outer ring 10. The outer ring 10 has three connecting elements 11 in the form of locking elements 11 or locking lugs 11, which are evenly distributed in the circumferential direction U, i.e., offset from each other by 120°. The locking lugs 11 can interact with corresponding locking receptacles of the first rigid body, such as the chassis (not shown), to connect the bearing bushing 1 to it in a fixed manner. Reference symbol list (part of the description) R radial direction U circumferential direction X longitudinal axis 1 bearing; elastomeric bearing; bearing bushing; gear bearing bushing 10 outer part; outer ring 11 connecting elements; locking elements; locking lugs 12 (elastomeric) support body; elastomeric part; (elastomeric) struts 13 additional masses of the support bodies 12 13a web-like extension of the additional mass 13 13b (end-side) thickening of the additional mass 13 14 gap 15 inner part; inner part 16 receptacle 17 elastomeric stop elements

Claims

Bearing (1), in particular elastomeric bearing (1), in the form of a bearing bushing extending along a longitudinal axis (X), a radial direction (R) perpendicular to the longitudinal axis (X), and a circumferential direction (U) rotating around the longitudinal axis (X), comprising an outer part (10) in the form of an outer ring, an inner part (15) radially within the outer part (10), and at least one support body (12) arranged radially between the outer part (10) and the inner part (15), characterized in that the support body (12) has at least one additional mass (13) extending at least substantially perpendicular to the support body (12) and being movable at least sectionally parallel to the support body (12) in the radial direction (R), wherein the bearing has a plurality of support bodies (12), each of which is arranged between the outer part (10) and the inner part (15), wherein several support bodies (12), in particular all support bodies (12),have at least one additional mass (13) which extends at least substantially perpendicular to the respective support body (12) and is movable at least sectionally parallel to the respective support body (12) in the radial direction (R), wherein the at least one additional mass (13) extends into a space between two support bodies (12). Bearing (1) according to claim 1, characterized in that the additional mass (13) is designed to perform a counter-oscillation to the support body (12). Bearing (1) according to claim 1 or 2, characterized in that the additional mass (13) has a thickening (13b) pointing away from the support body (12). Bearing (1) according to claim 3, characterized in that the thickening (13b) pointing away from the support body (12) is arranged at the end of the additional mass (13) pointing away from the support body (12). Bearing (1) according to claim 3 or 4, characterized in that the additional mass (13) has a web-like extension (13a) which connects the support body (12) with the thickening (13b). Bearing (1) according to one of the preceding claims, characterized in that the additional mass (13) is designed to influence a predetermined frequency of the bearing (1), in particular a resonance frequency, by its mobility parallel to the support body (12). Bearing (1) according to one of the preceding claims, characterized in that the additional mass (13) is formed integrally with the support body (12). Bearing (1) according to one of the preceding claims, characterized in that the support body (12) and / or the additional mass (13) is made of an elastomeric material. Bearing (1) according to one of the preceding claims, characterized in that at least two additional masses (13) are designed differently. Vehicle, in particular land vehicle, with at least one bearing (1) according to one of the preceding claims, wherein the bearing (1) is arranged between a vibration-generating component and a further component of the vehicle.

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