BEARINGS AND VEHICLE SUSPENSION COMPREHENSIVE SUCH A BEARING

Description

[0001] The invention relates to a bearing for isolating vibrations along a dynamic main load direction, comprising a cylindrical sleeve, a core arranged in the sleeve, and an elastomeric body that resiliently connects the core to the sleeve. The invention further relates to a vehicle suspension comprising a first component that generates vibrations in a dynamic main load direction, a chassis, and a bearing as described above, which resiliently mounts the first component to the chassis.

[0002] Component bearings, such as rear axle differential bearings, transmission bearings, or bearings for an electric motor, are known from the prior art. The design of these bearings is currently adapted specifically for each application. Furthermore, linear or torsional vibration dampers are known from the prior art as separate and easily tunable components, as described, for example, in DE 2 716 485 C2.

[0003] KR 101 372 085 B1 discloses a bushing bearing in which intermediate plates are incorporated into a web to increase its stiffness. US 6 641 119 B2 discloses a bushing bearing in which mass elements are loosely arranged in a web to reduce unwanted resonance characteristics.

[0004] The object of the invention is to create a bearing in which a frequency range of good isolation can be easily set.

[0005] The problem is solved by the bearing according to claim 1 and by the vehicle suspension according to claim 9. Dependent claims 2 to 8 describe preferred embodiments of the bearing according to claim 1.

[0006] A bearing for isolating vibrations along a dynamic main load direction comprises a cylindrical sleeve, a core arranged within the sleeve, and an elastomer body that resiliently connects the core to the sleeve. The elastomer body has first webs arranged between the core and the sleeve in the dynamic main load direction, and second webs arranged at an angle, in particular perpendicular, to the first webs between the core and the sleeve. A mass element is arranged exclusively in the second webs. Furthermore, a mass element is arranged in each of the second webs. The mass element has a planar design and extends parallel to the sleeve. The sum of the lengths of the segments of the second webs in the radial direction is greater than the sum of the lengths of the first webs in the radial direction.

[0007] A vehicle suspension comprises a first component that generates vibrations in the main dynamic load direction, a chassis, and a bearing, as described above, which resiliently mounts the first component to the chassis. The first webs of the bearing extend in the direction of the main dynamic load direction.

[0008] The invention further relates to a vehicle with such a vehicle suspension.

[0009] The term "primary load direction" or simply "main load direction" refers to the direction in which the greatest dynamic vibrations are transmitted to the bearing under normal, intended operating conditions. This does not include maximum loads occurring during special events or crashes. Furthermore, the primary load direction does not necessarily coincide with the direction of the weight force. For the bearing, the primary load direction can be defined by the axis of symmetry that most closely aligns the second webs equipped with mass elements. Accordingly, these webs, each equipped with at least one mass element, can be referred to as the second webs, while the webs in the primary load direction can be called the first webs.

[0010] An advantage of the invention is that the first webs, which are preferably arranged in the main dynamic load direction, significantly determine the stiffness properties of the bearing in this direction. While the second webs also contribute to the stiffness in this direction, their influence is minimal. Therefore, it is possible, in particular, to change the mass of the mass element for the specific application without significantly affecting the stiffness of the bearing in the main dynamic load direction.

[0011] The mass element acts as a damping mass, reducing the dynamic stiffness of the bearing. This occurs just above an elastomer natural frequency of at least one of the second (elastomer) webs through the excitation of out-of-phase vibrations. The frequency range in which the isolation is improved depends on the inherent damping of the elastomer, i.e., the second web; a typical frequency range for good isolation is just above the natural frequency up to a factor of √2 times the natural frequency. Thus, it is possible to selectively reduce the dynamic stiffness of the bearing by varying the mass of the mass element within a defined frequency range, since the natural frequency ω With a nearly constant spring constant c, the mass element is approximately determined according to the following formula: ω = √ c / m .

[0012] Because this natural frequency can be adjusted by modifying the mass of the mass element, a standardized bearing can be used for various applications, i.e., for different frequency ranges with high isolation requirements. In summary, a uniform elastomer bearing design can be used and adapted for different isolation frequency ranges at a given stiffness c by adjusting the vibrating mass (mass element). The basic bearing design does not need to be changed. This simplifies the calculation and design of the bearing and, in some cases, can even enable the use of standardized components, thus allowing for a cost-effective design.

[0013] This effect, whereby the reduction in stiffness in a frequency range can be set largely independently of the bearing's stiffness in the main dynamic load direction, also makes it possible to manufacture a bearing where the stiffness in the main dynamic load direction can be set largely independently of the frequency range with good isolation. This decoupling of the properties that are intertwined in a conventional bearing significantly simplifies the bearing design.

[0014] Since the dynamic stiffness is reduced just above the elastomer's natural frequency, as the elastomer, which vibrates out of phase with the excitation, compensates for parts of the excitation in this frequency range, such a bearing is characterized by a particularly good isolation effect in the frequency range of the deliberately reduced dynamic stiffness up to approximately √2 times the elastomer's natural frequency.

[0015] The mass element can oscillate not only in the main dynamic load direction, but also in an axial direction. Thus, an out-of-phase oscillation in the axial direction, just above the axial natural frequency of the vibration system consisting of the second web and the mass element, can also be used to reduce the dynamic stiffness and thus improve isolation.

[0016] The bearing can be specifically described as an aggregate mount. It can be part of a vehicle suspension system, to which the first component can be attached to a chassis. This first component could, for example, be a differential, a transmission, or an electric motor. The vibrations generated by the first component can be produced, for instance, by the engagement of gears within the first component. These vibrations are transmitted primarily in the main dynamic load direction. The main dynamic load direction is thus determined by the first component and can therefore be easily identified.

[0017] The vehicle suspension can be part of a vehicle. The vehicle suspension can also be referred to as a vehicle unit.

[0018] The chassis according to the present invention is used in the manner customary in the prior art. The load-bearing parts of vehicles are referred to as chassis, frame, subframe, or undercarriage. The chassis is an element of the vehicle to which the first component is attached. A bearing is provided to prevent the transmission of vibrations generated by the first component to the chassis. The bearing connects the first component to the chassis in a resilient manner.

[0019] The chassis or first component has, in particular, a cylindrical receptacle into which the bearing is inserted. An outer surface of the cylindrical sleeve thus engages with the cylindrical receptacle of the chassis or first component. The cylindrical sleeve therefore serves to attach the bearing to the chassis or first component.

[0020] The core preferably has a through-opening extending in an axial direction. A bolt can be inserted through this opening, allowing the core to be attached to the first component or the chassis. Nuts or other fasteners can be used to securely fix the bolt or other fastening element to the first component or the chassis.

[0021] A radial direction is perpendicular to the axial direction. A circumferential direction extends around the axial direction. The cylindrical sleeve preferably extends in both the axial and circumferential directions. The sleeve is preferably ring-shaped in a cross-sectional view.

[0022] The core preferably has an outer surface that corresponds as closely as possible to the curvature of the outer surface of the sleeve. While the curvatures of the corresponding surfaces may be identical, the center of curvature is shifted approximately by the radial extent of the webs arranged between the corresponding surfaces. If the intersection points of these four core surfaces of the same curvature but with different centers of curvature are now provided with rounded transitions, the core's outer surface in a cross-sectional view approximates an ellipse.

[0023] However, it is also possible that the outer surface of the core is more circular or more rectangular in a cross-sectional view.

[0024] Preferably, the core has projections that extend axially and radially, which serve as path limits transverse to the dynamic main load direction and / or in the dynamic main load direction.

[0025] The core is resiliently connected to the sleeve by means of the elastomer body. The term "elastomer body" is intended to encompass any material or component that enables a resilient attachment of the core to the sleeve. Therefore, the elastomer body is not limited to a body made of elastomer; other materials are conceivable. The elastomer body is most commonly made of rubber.

[0026] The elastomer body preferably has two first webs and two second webs, each extending in the radial direction. In particular, the two first webs are provided on opposite sides of the core, so that the first webs extend longitudinally along a radial direction. Similarly, the second webs are arranged on opposite sides of the core. Here too, it is possible for the two second webs to extend along a radial direction. However, it is also possible for the two second webs to be arranged at an angle of less than 180° to each other.

[0027] According to the invention, the second webs are arranged at an angle of 90° (in particular ± 5° ± 10°) to the first webs. A non-perpendicular arrangement, i.e., not equal to 90° ± 10° or 90° ± 5°, is also possible, but not claimed; for example, the angle between the first web and the second web is 70° or 75°. Preferably, the second webs are arranged symmetrically about a plane of symmetry defined by the main dynamic load direction and the axial direction of the bearing.

[0028] The first and second webs contribute to the stiffness of the bearing in the main dynamic load direction. Since the first webs extend parallel to the main dynamic load direction, they are compressed and stretched by vibrations in this direction. The second webs are compressed and stretched by a force applied essentially perpendicular to the main dynamic load direction. During vibrations in the main dynamic load direction, the second webs are not compressed or only slightly stretched, but are instead subjected to shear stress. Therefore, compared to the first webs, the second webs tend to contribute less to the stiffness in the main dynamic load direction.

[0029] The mass element is characterized by having a higher density than the material of the elastomer body, particularly the second web. Specifically, the density of the mass element is greater than the density of the second web. The mass element is made, for example, of metal, preferably aluminum or steel.

[0030] The mass element acts as a damping mass, which, when subjected to vibrations in the main dynamic load direction, oscillates essentially parallel to that direction. However, due to the arrangement of the mass element in the second web and the cylindrical design of the bearing, a circumferential component of the mass element's movement can also be incorporated.

[0031] The volume of the mass element is significantly smaller than the volume of the second web, in particular by a factor of five, ten, or fifty. Optionally, it extends substantially in a plane parallel to a plane defined by the axial direction and the main dynamic load direction. The thickness of the mass element perpendicular to this plane, however, is in this embodiment at most as thick as its extension in the other directions, if the mass element is a sphere or a rod. Consequently, the mass element has little influence on the stiffness of the second web in the shear direction, i.e., in the main dynamic load direction and the axial direction. Thus, the mass element hardly alters the stiffness of the bearing in the main dynamic load direction and the axial direction.

[0032] By appropriately selecting the material of the mass element and its size, the mass of the mass element can be adjusted independently of the other components of the bearing, since the stiffness of the second web in the dynamic main load direction is only slightly affected by the presence of the mass element.

[0033] The natural frequency is selected via the mass of the mass element, which acts as a damper, such that it is slightly lower than the frequency range of the vibrations of the first component that can be effectively isolated. This results in a significant reduction in stiffness, sometimes even below the static stiffness in the frequency range to be isolated. Consequently, the bearing is particularly flexible just above its natural frequency, enabling correspondingly good vibration isolation. The other components of the bearing, such as the sleeve, the core, the first webs, and in many cases also the second webs, require little or no modification.

[0034] By placing a mass element in each of the second webs, a symmetrical bearing design can be achieved with respect to an axis of symmetry that runs through the first webs along the main dynamic load direction. Furthermore, it is possible to increase the total mass of the oscillating system, since two mass elements are provided. In particular, the two mass elements are identical.

[0035] It is further preferred that the center of mass of the mass element in the radial direction between the sleeve and the core approximately coincides with a position in the radial direction between the sleeve and the core of a maximum vibration amplitude of the first order vibration of the second web.

[0036] During vibrations in the main dynamic load direction, the second webs are deflected in the main dynamic load direction, i.e., essentially perpendicular to its radial extent. In a first-order vibration, a half-wave thus forms in the second web, the amplitude of which oscillates approximately parallel to the main dynamic load direction. The position in the radial direction at which the amplitude of the vibration is maximized is called the position of maximum vibration amplitude of the first-order vibration of the second web. The center of mass of the respective mass element is preferably located near or exactly at this position in the radial direction. "Approximately coincides" means, in particular, that the deviation from ideal coincidence is no more than 5%, 10%, or 15% of the length of the second web in the radial direction.

[0037] This ensures that during a first-order vibration of the second bridge, the mass element is deflected to a maximum degree, resulting in a large damping effect at the natural frequency and thus a large reduction in dynamic stiffness and therefore good isolation in a frequency range just above the natural frequency.

[0038] The position of the maximum amplitude of the second web's deflection depends primarily on its length and shape. Once this position is determined, the natural frequency, and thus the area of ​​particularly low dynamic stiffness of the bearing in the main dynamic load direction, can be adjusted by changing the mass of the mass element. Adjusting the mass element's position in the radial direction to accommodate the changed mass is not necessary.

[0039] It is preferred that the mass element divides the second web, in particular perpendicular to the main dynamic load direction, into two sections.

[0040] The mass element can, for example, take the form of a sheet of metal. To change the mass of a flat or sheet-shaped mass element, various materials can be used, such as aluminum or steel.

[0041] Furthermore, the mass of the planar mass element can be varied by adjusting its thickness. For example, in its planar configuration, the mass element has a thickness of 2 mm in the radial direction, although this thickness can preferably be varied between 1 mm and 5 mm to adjust the mass. Varying the thickness of the mass element has only a very minor influence on the stiffness of the second web in the shear direction, i.e., in the main dynamic load direction, as long as the thickness of the mass element is small relative to the thickness of the second webs. The resonance frequency can thus be changed by a factor of up to 2.If, at the same time, the material of the mass element is changed, for example from aluminum to steel, which also results in a change by a factor of, for example, 1.7, overall changes of up to a factor of 3 to 4 can be achieved without significantly changing the stiffness of the bearing in the main dynamic load direction.

[0042] According to the invention, the mass element, in its planar configuration, is curved parallel to the sleeve. In this way, the second web can be subdivided by the mass element such that the local thicknesses along the circumferential direction can be set to a largely constant radial dimension. In particular, it is provided that the mass element divides the second web into two parts. This means that the mass element has a planar configuration that is larger than the second web in the circumferential and / or axial direction. The second mass element projects beyond the second web in the circumferential and / or axial direction.

[0043] It is preferred that the second web has a recess in which the mass element is arranged. This means that the integration of the mass element hardly increases the stiffness transverse to the main dynamic load direction; the recess, in conjunction with the placed mass element, can even be designed such that the stiffness is reduced compared to the geometry of the second web without a recess. It is further preferred that the mass element is held in a form-fit manner, particularly by the recess. For example, the recess has a size that is smaller than the size of the mass element, so that the mass element is held in a force-fit manner. Furthermore, it is possible for the recess to achieve a form-fit with the mass element. Thus, in this embodiment, it is not necessary to vulcanize the mass element to the second web. This represents another method of attaching the mass element to the second web.

[0044] For example, in unclaimed embodiments where the mass element is spherical, the recess can have a spherical protrusion in the second web, which is connected to the surroundings by one or more channels. In this way, the mass element can be inserted into the protrusion. With a rod-shaped embodiment of the mass element, the mass element can be held in the second web by frictional engagement. With an annular embodiment of the mass element, the mass element can be placed in a recess extending around the outside of the second web. Thus, the mass element can also be held against the second web by positive engagement.

[0045] It is preferred that the mass element has an extent in the main dynamic load direction which is smaller than the extent of the second web in the main dynamic load direction at the location of the mass element, in particular half, one-third, or one-quarter. This design is intended to ensure that the second web is not divided into two sections by the mass element.

[0046] The sum of the lengths of the segments of the second webs in the radial direction is greater than the sum of the lengths of the first webs in the radial direction. This means that the principle underlying the invention can be used for a wide variety of configurations of the first and second webs.

[0047] It is preferred that the mass element arranged in a second web has a different mass than the mass element arranged in the other second web.

[0048] This allows for a reduction in dynamic stiffness at two different frequencies. Therefore, the bearing can be designed in this way to provide good isolation in two different frequency ranges.

[0049] According to the invention, the bearing has a stop which limits the deflection of the core relative to the sleeve in the dynamic main load direction and / or perpendicular to the dynamic main load direction, wherein the stop preferably has a projection arranged on the core.

[0050] The stop is designed to limit the deflection of the core in the main dynamic load direction, thus preventing damage to the first web caused by excessive elongation of the first web in this direction. Furthermore, the stop can also prevent unwanted stress on the second web, such as excessive deflection of the second web perpendicular to the main dynamic load direction. For this purpose, the stop can have a projection located on the core and / or the sleeve. Preferably, the core projects at an angle of approximately 45° to the main dynamic load direction to simultaneously create a limit in the main dynamic load direction and perpendicular to it.

[0051] It is preferred that the stop comprises four projections arranged on the core, with each pair of two projections arranged on either side of the first webs.

[0052] Optionally, four projections form the stop, with the projections being arranged on both sides of the first webs. Preferably, the projections are arranged symmetrically about an axis of symmetry that runs through the first webs. Opposite the projections, for example a core or a sleeve, a rubber body can be arranged to dampen the impact of the projection.

[0053] The invention is explained in more detail with reference to the accompanying drawings. These show Figure 1 is a schematic representation of a vehicle in which a vehicle suspension is schematically provided; Figure 2 is a cross-sectional view of a bearing in a fixed position; Figure 3 is a cross-sectional view of a first embodiment of the bearing; Figure 4 is a further cross-sectional view of the bearing of Figure 3, in which the vibration conditions are sketched; Figure 5 a cross-sectional view of a further embodiment of the bearing according to the invention; Figure 6 a cross-sectional view of a further embodiment of an unclaimed bearing; and Figure 7 a diagram showing the stiffness of the bearing as a function of the frequency of the vibrations for different masses of a mass element and in comparison to a conventional bearing.

[0054] Figure 1 Figure 1 shows a schematic view of a vehicle 10, in which a vehicle suspension 12 is schematically depicted. The position and size of the vehicle suspension 12 do not correspond to the actual dimensions but serve only for illustration. The vehicle suspension 12 comprises a chassis 14, a first component 16, and a bearing 20. The chassis 14 of the vehicle 10 is only partially shown.

[0055] The first component 16, such as a gearbox, a rear axle differential, or an electric motor, is attached to the chassis 14. For this purpose, the chassis 14 has a receptacle 18 with a cylindrical inner surface. A bearing 20 is provided in the receptacle 18 and is connected to a suspension 26 of the first component 16 by means of a bolt (not shown) and nuts (not shown) (see in particular...). Figure 2 The bearing 20 allows a spring-loaded attachment of the first component 16 to the chassis 14.

[0056] The first component 16 generates vibrations along a dynamic main load direction HL, which is, for example, parallel to the force of gravity. The vibrations of the first component 16 can be generated by gear meshing of gears that comprise the first component 16. The vibrations generated by the first component 16 are particularly pronounced at a specific frequency. The bearing 20 is provided to isolate these frequencies generated by the first component 16.

[0057] As this is shown Figures 2 and 3 As can be seen, the bearing 20 comprises a cylindrical sleeve 28, a core 30, and an elastomer bearing 32. The sleeve 28 can have the form of a cylindrical body, preferably extending in an axial direction A. The sleeve 28 can be, as shown in the Figures 3 to 6 shown to be circular in cross-section.

[0058] The core 30 has a through-opening 34 which extends in the axial direction A. The bolt can be passed through the through-opening 34. The core 30 is, as shown in the Figures 2 to 6 The core 30 is shown assembled in one piece. It is attached to the sleeve 28 by means of the elastomer body 32. The elastomer body 32 allows for a resilient mounting of the core 30 on the sleeve 28. The elastomer body 32 is not limited to an elastomeric material, but can be made of any material that allows for a resilient attachment of the core 30 to the sleeve 28.

[0059] The bearing 20 can further be provided with a stop 36, which limits the deflection of the core 30 relative to the sleeve 28 perpendicular to the dynamic main load direction HL and / or in the dynamic main load direction HL. The stop 36 can have one or two (see Figure 5 ), four (see Figures 3 and 6) or have more projections 38. The projections 38 can be arranged on the core 30 or on the sleeve 28. Preferably, the projections 38 are formed integrally with the core 30. In particular, the projections 38 project from the core 30 at an angle of 45° to the main dynamic load direction HL. This allows the deflection of the core 30 relative to the sleeve 28 to be limited both in the main dynamic load direction HL and perpendicular to it. The projections 38 are preferably arranged symmetrically about an axis of symmetry that runs centrally through the bearing 20 and parallel to the main dynamic load direction HL. This means that, in this embodiment, the projections 38 are arranged on both sides of the first webs 38.

[0060] The elastomer body 32 optionally has two first webs 40, two second webs 42, and at least one mass element 44. The first webs 40 are arranged opposite each other and each extends in the radial direction R, in particular parallel to the main dynamic load direction HL. The second webs 42 are arranged according to the embodiment shown. Figures 3 and 4The second webs 42 are arranged perpendicular to the main dynamic load direction HL and also extend in the radial direction R. In the illustrated embodiment, the sum of the lengths of the segments of the second webs 42 in the radial direction R is greater than the sum of the lengths of the first webs 40 in the radial direction R. The core 30 can have an elliptical cross-sectional shape, with the longitudinal axis of this ellipse extending along the main dynamic load direction HL and the shorter side perpendicular to it. Due to this design, the stiffness of the first webs 40 in the main dynamic load direction HL is higher than the stiffness of the second webs 42 in the main dynamic load direction HL. Furthermore, in general and in particular due to the properties described in the Figures 3 and 4In the illustrated embodiment of the second webs 42, the second webs 42 contribute relatively little to the stiffness of the bearing 20 in the dynamic main load direction HL. However, the invention is not limited to this embodiment. The length of the second webs 40 in the radial direction R can be less than the length of the first webs 38 in the radial direction R.

[0061] The at least one mass element 44 is provided in the second web 42. In the embodiments shown in the figures, two mass elements 44 are provided, with one mass element 44 being provided in every second web 42. The mass element 44 has a density that is greater than the density of the second web 42. The mass element 44 can, for example, be made of metal, in particular aluminum or steel. In the embodiments shown in the Figures 3 to 5 In the embodiment shown, the mass element 44 is vulcanized to the second webs.

[0062] The mass element 44 is positioned in the radial direction R between the core 30 and the sleeve 28 such that a center of mass 46, as shown in the Figure 4 The second web 42 is arranged at a location where a first order of the natural frequency of the second web 42 exhibits its maximum amplitude. When the core 30 is deflected relative to the sleeve 28, each of the second webs 42 exhibits a vibration in the main dynamic load direction HL. A first order of this vibration exhibits a half-wave whose maximum amplitude is located approximately at or equal to the height in the radial direction R at which the center of mass 46 is located. Such an arrangement of the mass element 44 results in the mass element 44 oscillating with maximum out-of-phase amplitude above the natural frequency of the second web 42, and the reduction in dynamic stiffness is also maximized.

[0063] The vibration of the mass element 44 occurs primarily along the main load direction HL, but due to the design of the bearing 20 as a cylindrical element, it can also exhibit components in the circumferential direction U, as indicated by the double arrow in Figure 4 is marked.

[0064] The mass element 44 has in the embodiments according to Figures 3 to 5 a planar design, in particular the mass element 44 has the form of a sheet. The mass element 44 has such dimensions in both the circumferential direction U and in the axial direction A that the mass element 44 projects beyond the second web 42 in the circumferential direction U and / or in the axial direction A. The mass element 44 thus divides the second web 42 into two sections or parts along the radial direction R. The mass element 44 can, as in the Figures 3 to 5The mass element 44 is shown to be curved parallel to the sleeve 28. However, this is not mandatory. The mass element 44 can also extend parallel to the main dynamic load direction HL.

[0065] The embodiment of bearing 20 according to Figure 5 differs from the embodiment of bearing 20 according to Figures 3 and 4 only due to the differences described below. The second webs 42 according to the embodiment of Figure 5 are not arranged perpendicular to the main dynamic load direction HL, but at an angle other than 90°. In this case, at an angle of approximately 75° to the main dynamic load direction HL. Both the second webs 42 and the mass elements 44 are arranged largely symmetrically about an axis of symmetry that runs through the first webs 40. Furthermore, only two projections 38 are provided on the core 30.

[0066] The embodiment of bearing 20 according to Figure 6differs from the embodiments of bearing 20 according to the Figures 3 and 4 except for the following differences. The mass element 44 has a circular cross-section and can therefore assume the form of a sphere or a rod, wherein the second web 42 has a recess 48 in which the mass element 44 is positively locked. For this purpose, the recess 48 can be connected to the surroundings of the second web 42 by a passage through which the mass element 44 can be inserted into the recess 48. The mass element 44 according to Figure 6 It is therefore not vulcanized to the second pier 42.

[0067] It is also possible for the mass element 44 to be rod-shaped or ring-shaped. Furthermore, the mass element 44 can be held in the second web 42 by frictional engagement. For this purpose, the recess 48 can have an inner dimension that is smaller than the outer dimension of the mass element 44. In the case of a ring-shaped mass element 44, it can also be placed around the outside of the second web 40 and held there by means of a groove-shaped, circumferential recess 48 by positive engagement.

[0068] Furthermore, it is possible that the mass of the mass element 44 of one second bridge 42 differs from the mass of the mass element 44 of the other second bridge 42.

[0069] The operating principle of the bearing 20 is as follows. The first component 16 generates vibrations in the main dynamic load direction HL, which runs parallel to the extent of the first webs 40. As a result, the first webs 40 bear a significant portion of the dynamic load. When the core 30 deflects relative to the sleeve 28 due to vibrations in the main dynamic load direction HL, the mass elements 44 begin to move, as shown in Figure 4 shown to oscillate. This oscillation has a natural frequency which is determined by the mass of the mass element 44 as well as by the stiffness of the second webs 42 parallel to the main dynamic load direction. HLis determined. If the frequency of the vibrations is slightly higher than the natural frequency of the web 42 with the contained mass element 44, the latter oscillates out of phase with the excitation. This results in two opposing force vectors: one from the excitation amplitude and the total spring stiffness of the bearing 20, and the other from the out-of-phase oscillating displacement amplitude of the mass element 44, or the damper mass, and the stiffnesses with which the damper mass is connected by the second web 42. The sum of both force vectors yields the resultant force. The resultant dynamic stiffness, in turn, is the quotient of this resultant force and the original displacement. Thus, a significant reduction in dynamic stiffness in the main dynamic load direction can occur. HL in this frequency range. Due to the reduction in the dynamic stiffness of bearing 20 in the main dynamic load direction. HLCertain frequencies of the vibrations caused by the first component 16 can be isolated particularly effectively.

[0070] Previously, it was necessary to provide a new bearing 20 design for each frequency range requiring particularly good isolation, in which the elastomer body 32 had to be tuned according to the required stiffness and natural frequencies. This was very complex, since the natural frequencies of the elastomer body 32 resulted automatically from the geometry adapted to the stiffness requirements of the bearing 20. Tuning or adjusting the natural frequency via the geometry of the elastomer body 32, in turn, had a significant impact on the resulting stiffness. This is no longer necessary with the bearing 20 according to the invention, since the adjustment of stiffness and natural frequencies are largely decoupled from each other.To change the natural frequency of mass element 44 and thus adapt the bearing 20 to the critical, easily isolated frequency range of the vibrations of the first component 16, it is only necessary to change the mass of mass element 44. This also simplifies the design of a new bearing 20, as the stiffness in the main dynamic load direction can be adjusted. HL Good isolation can be planned largely independently of the frequency range. Coupling effects between these two effects need not be considered, or only to a limited extent.

[0071] The adjustment can be achieved by specifying different materials for the mass element 44. Furthermore, the thickness or other dimensions of the mass element 44 can be changed. Changing the material of the mass element 44, as well as changing its thickness or dimensions, has no or only a minor influence on the stiffness of the second web 42 in the main dynamic load direction HL. Nevertheless, the natural frequency of the mass element 44 can be changed by a factor of 4. Moreover, changing the mass element 44 has little influence on the static stiffness of the bearing 20, since the first web 40 does not need to be changed, or only slightly, due to the change in the mass element 44, and the influence of the mass element 44 on the stiffness of the second webs 42 in the main load direction is negligible. HLor thrust direction is also small. Thus, the natural frequency of the bearing 20 can be changed by a relatively simple adjustment of the mass element 44, without having to significantly modify other components of the bearing 20. Adapting the isolation range of the bearing 20 to the problem frequency of the vibrations of the first component 16 can therefore be achieved in a simple manner.

[0072] The influence of the material of mass element 44, and thus of its mass, on the dynamic stiffness is from Figure 7Clearly visible. The dashed line represents the frequency-dependent stiffness of the bearing 20 in the main load direction HL for a mass element 44 made of steel and formed as a sheet, while the dotted-dashed line refers to a bearing 20 for a mass element 44 made of aluminum and formed as a sheet. The two bearings 20 differ only in the material of the mass element 44 and thus in the mass of the mass element 44. Due to the difference in the mass of the mass element 44, the following results in Figure 7 A clearly visible shift in the frequency range of the reduced stiffness is evident. The reduction in stiffness of the two bearings 20 is particularly noticeable in comparison to the stiffness of a conventional bearing without a mass element 44, as represented by the solid line (measured stiffness) and the fine dashed line (extrapolated stiffness).

[0073] If the masses of the mass elements 44 of one and the other second web 42 are unequal, isolation effects can be generated with the bearing 20 in two different frequency ranges. Here, too, an adjustment of the respective natural frequencies can be achieved by adjusting the mass of the mass elements 44. Reference symbol list

[0074] 10 Vehicle 12 Vehicle suspension 14 Chassis 16 First component 18 Mount 20 Bearing 26 Suspension 28 Sleeve 30 Core 32 Elastomer body 34 Through opening 36 Stop 38 Projection 40 First web 42 Second web 44 Mass element 46 Center of mass 48 Recess Aaxial direction R Radial direction U Circumferential direction HL Dynamic main load direction

Claims

1. Bearing for isolating vibrations along a dynamic main load direction (HL), comprising a cylindrical sleeve (28), a core (30) disposed within the sleeve (28), and an elastomeric body (32) resiliently connecting the core (30) to the sleeve (28), wherein the elastomeric body (32) has first webs (40) which are arranged in the dynamic main load direction (HL) between the core (30) and the sleeve (28) and resiliently connect the core (39) and the sleeve (28), and second webs (42) which also resiliently connect the core (39) and the sleeve (28) and are arranged at an angle perpendicular to the first webs (40) between the core (30) and the sleeve (28), wherein a mass element (44) is arranged in at least one of the second webs (42), wherein the mass element (44) is curved in its flat design so as to run parallel to the sleeve (28), wherein the bearing comprises a stop (36) which limits the deflection of the core (30) relative to the sleeve (28) in the dynamic main load direction (HL) and / or perpendicular to the dynamic main load direction (HL).

2. Bearing according to claim 1, characterised in that the centre of mass (46) of the mass element (44) in a radial direction (R) between the sleeve (28) and the core (30) approximately coincides with a position in the radial direction (R) between the sleeve (28) and the core (30) with a maximum vibration amplitude of the first-order vibration of the second web (42).

3. Bearing according to claim 1 or 2, characterised in that the mass element (44) separates the second web (42) into two parts.

4. Bearing according to claim 1 or 2, characterised in that the second web (42) has a recess (48) in which the mass element (44) is arranged.

5. Bearing according to claim 4, characterised in that the mass element (44) is held in the recess (48) by a positive fit.

6. Bearing according to one of claims 1 to 5, characterised in that the mass element (44) of one second web (42) has a different mass than the mass element (44) of the other second web (42).

7. Bearing according to one of the preceding claims, characterised in that the stop (36) comprises a projection (38) arranged on the core (30) and / or the sleeve (28).

8. Bearing according to claim 7, characterised in that the stop (36) comprises four projections (38) arranged on the core (30), with a pair of two projections (38) arranged on either side of the first webs (40).

9. Vehicle suspension comprising a first component (16) that generates vibrations in a main dynamic load direction (HL), a chassis (14), and a bearing (20) according to one of the preceding claims, which resiliently supports the first component (16) on the chassis (14), wherein the first webs (40) of the bearing (20) extend in the dynamic main load direction (HL).