DE102018221375A1 - Bearings, especially elastomer bearings - Google Patents

Abstract

The invention relates to a bearing (1), in particular an elastomer bearing (1), with an outer part (10), with an inner part (15) and with at least one support body (12) which is located between the outer part (10) and the inner part (15 ) is arranged. The bearing (1) is characterized in that the support body (12) has at least one additional mass (13) which extends at least substantially perpendicular to the support body (12) and is at least partially movable parallel to the support body (12).

Description

The present invention relates to a bearing, in particular an elastomer bearing, according to the preamble of patent claim 1 and a vehicle with such a bearing according to patent claim 11.

In many technical fields, elastomer elements have long been used to dampen vibrations between two rigid bodies. This also includes land vehicles such as passenger cars (cars) and trucks (trucks), in which such damping elements e.g. can be used as motor bearings, gearbox bearings or shaft bearings. In any case, the elastomer element is usually arranged between the engine, the transmission or the shafts on one side and the chassis of the vehicle on the other side, so that vibrations from the corresponding component of the drive train, such as from the engine, from the transmission or can be dampened or even repaid by the shaft against the chassis of the vehicle.

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 is to be absorbed safely and permanently, and the vibrations to be damped or to be eliminated are usually in a low-frequency range up to approx. 25 Hz.

High-frequency vibrations always occur during operation, which are influenced by the static or low-frequency design. However, the high-frequency behavior of the bearing cannot be influenced without changing the static or low-frequency behavior. Therefore, such bearings are usually designed according to their static and low-frequency specifications and the high-frequency behavior of the bearing is accepted.

However, it is disadvantageous that the high-frequency excitations e.g. acoustic phenomena can be generated in the chassis of a vehicle, which can disturb or irritate the driver. This can reduce driving comfort for the driver.

An object of the present invention is to provide a bearing of the type described in the introduction, so that its high-frequency vibration behavior can be influenced, in particular reduced. In particular, the frequency of a first resonance point, in particular 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 than its low-frequency vibration behavior. This should be made possible in particular for a bearing bush. This is to be achieved in particular for an engine mount and / or for a gearbox mount, in particular for an engine mount bushing and / or for a gearbox mount bushing. This should be made possible in particular for use in an electrically operated vehicle. In particular, the dynamic stiffness of such a bearing is to be improved.

The object is achieved by a bearing with the features according to claim 1 and by a vehicle with the features according to claim 11. Advantageous further developments are described in the subclaims.

The present invention thus relates to a bearing, in particular an elastomer bearing, with an outer part, with an inner part and with at least one support body which is 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 bush.

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 at least partially movable 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 which is at least partially movable parallel to the support body. In particular, this additional mass can be placed in a space which e.g. can be formed by the outer part, the inner part and / or the support body, protrude and be movable there at least in sections, as previously described. The additional mass is preferably made smaller in volume and / or weight and in particular significantly less than the support body itself.

The present invention is based on the knowledge that a further movable element of the support body, which is movable relative to this, can result in the eradication or damping of different vibration frequencies than the vibration frequencies, the eradication or damping of the support body is designed in itself. As a result, in particular higher-frequency vibrations can be damped or canceled out than can be done by the support body itself. The oscillation frequency, which is to be dampened or erased by the additional mass, can be formed by the formation of the additional mass in terms of shape, weight and / or arrangement on the Supported body influenced and so be designed for a specific frequency depending on the application. This can be done specifically in response to a resonance frequency.

The eradication or damping effect of the support body can thus be improved or expanded in order to overcome or at least reduce the disadvantages described at the outset, or to partially or completely solve the aforementioned task. In particular, the higher-frequency stiffness of the bearing can be specifically influenced and coordinated. The overall frequency position and in particular of higher-frequency vibrations, in particular of higher-frequency resonance frequencies, can be shifted. This can be done very simply and inexpensively using purely passive measures by using the additional masses. Influencing other properties of the bearing can also be avoided or at least kept to a minimum.

According to one aspect of the present invention, the additional mass is designed to counter-oscillate the supporting body. This can promote the implementation of the properties and advantages described above, and in particular can increase their effectiveness. The oscillation behavior of the bearing or of the support body can be changed by the counter-vibrations, so that its stiffness can be lowered 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 while at the same time being comparatively low in weight and / or at the same time being comparatively low in volume, so that the properties described above can be implemented with as little effort as possible or with a small movable weight or with little installation space required .

According to a further aspect of the present invention, the thickening pointing away from the supporting body is arranged at the end of the additional mass facing away from the supporting body. This can enable a particularly compact implementation of the properties described above. This can also enable the additional mass to move and vibrate as effectively as possible with respect to the supporting body.

According to a further aspect of the present invention, the additional mass has a web-like extension which connects the supporting body to the thickening. This can increase the relative mobility of the thickening of the additional mass relative to the supporting 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 resulting increase in the installation space of the additional mass.

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 resonance frequency, by its mobility parallel to the supporting body. Such a design can take place depending on the application and e.g. be implemented through calculation, simulation and iterative tests. The change in a resonance frequency can influence the vibration behavior of the bearing particularly effectively.

According to a further aspect of the present invention, the additional mass is formed in one piece with the supporting body. This can allow a secure connection and / or a simpler manufacture than in the case of a one-piece design with two separately manufactured and subsequently connected elements.

According to a further aspect of the present invention, the support body and / or the additional mass is formed from an elastomeric material. This can enable a vibration-damping or vibration-damping effect with simple, robust and / or inexpensive means.

According to a further aspect of the present invention, the bearing has a plurality of support bodies, which are each arranged between the outer part and the inner part, wherein a plurality of support bodies, in particular all support bodies, have at least one additional mass, each of which is at least substantially perpendicular to the respective one Carrying body extends and is at least partially movable parallel to the respective supporting body. Due to the plurality of supporting bodies, their effect can be used several times per se. Providing several and in particular all supporting bodies 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 designed differently. As a result, different movements or vibrations of the two additional masses can be implemented, so that different frequencies can be damped or canceled out. This can increase the variety of effects 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, the bearing being arranged between a vibration-generating component and a further component of the vehicle. As a result, the properties and advantages described above can be implemented and used in a vehicle and in particular in a land vehicle such as a car and / or a truck.

• 1 einen schematischen Querschnitt eines bekannten Lagers in Form einer Lagerbuchse;
• 2 einen schematischen Querschnitt eines erfindungsgemäßen Lagers in Form einer Lagerbuchse gemäß eines ersten Ausführungsbeispiels;
• 3 eine Detailansicht der 2;
• 4 eine schematische perspektivische Ansicht eines erfindungsgemäßen Lagers in Form einer Lagerbuchse gemäß eines zweiten Ausführungsbeispiels;
• 5 einen schematischen Querschnitt der 4; und
• 6 eine Detailansicht der 5.

Two exemplary embodiments and further advantages of the invention are explained below in connection with the following figures. It shows:

• 1 a schematic cross section of a known bearing in the form of a bearing bush;
• 2nd a schematic cross section of a bearing according to the invention in the form of a bearing bush according to a first embodiment;
• 3rd a detailed view of the 2nd ;
• 4th is a schematic perspective view of a bearing according to the invention in the form of a bearing bush according to a second embodiment;
• 5 a schematic cross section of the 4th ; and
• 6 a detailed view of the 5 .

The above figures are described in cylindrical coordinates with a longitudinal axis X , one to the longitudinal axis X vertical radial direction R and one around the longitudinal axis X circumferential direction U .

1 shows a schematic cross section of a known bearing 1 in the form of a bearing bush 1 , which in this case is more precisely a gearbox bearing bush 1 is. The bearing bush 1 has an outer part 10th on which is the outer ring 10th is cylindrical. Radially inside the outer ring 10th has the bearing bush 1 an inner part 15 on which as the inner part 15 is essentially cylindrical. The outer ring 10th is intended to be fixedly connected to a first rigid body, for example in the form of a chassis, for example a car or truck (not shown). The inside part 15 is intended to be fixedly connected to a second rigid body, for example 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 mounted 16 of the inner part 15 be connected with this fixed.

Radially between the outer ring 10th and the inner part 15 are four supporting bodies 12 arranged which the outer ring 10th and the inner part 15 connect each other. The four supporting bodies 12 are in the circumferential direction U arranged substantially evenly and spaced substantially evenly apart, so that there are four spaces 14 form, each radially outward through a portion of the outer ring 10th , radially inwards through a section of the inner ring 15 as well as in the circumferential direction U on each side through one of the four supporting bodies 12 be limited.

The supporting body 12 are each made of an elastomeric material such as rubber and the same elastomeric material, so that they also as an elastomeric support body 12 , as elastomer parts 12 or as struts 12 or as elastomer struts 12 can be designated. The elastomeric support body 12 can essentially by elastic deformations in the radial direction R Carry out movements and thereby tensile or compressive forces between the outer ring 10th and the inner part 15 record, tape. This can dampen or eradicate vibrations between the outer ring 10th and the inner part 15 cause.

The elastomeric support body 12 Usually arranged and designed, in particular shaped, that the static load associated with the inner part 15 is fixedly connected by the elastomeric supporting bodies 12 can be included. This also applies to low-frequency vibrations caused by the elastomeric support body 12 can be absorbed and steamed or redeemed. In addition, however, such known bushings 1 or their elastomeric supporting bodies 12 no higher-frequency vibrations are damped or eradicated.

2nd shows a schematic cross section of a bearing according to the invention 1 in the form of a bearing bush 1 according to a first embodiment. 3rd shows a detailed view of the 2nd .

The bearing bush 1 according to the first embodiment of the 2nd and 3rd corresponds essentially to the known bearing bush 1 of the 1 with the difference that the two elastomeric supporting bodies 12 which in the representations of the 1 and 2nd An additional mass is arranged at the bottom left and bottom right, facing each other 13 have, which are in one piece with the respective elastomeric support body 12 and is thus formed from the elastomeric material. Any additional mass 13 has a web-like extension 13a on which is in the circumferential direction U in the space 14 extends into and ends at a thickening 13b in the radial direction R widened, which is spherical.

The two additional masses 13 and in particular their thickened ends 13b can be parallel to the respective support body 12 essentially in the radial direction R Carry out vibrations, which counter-vibrations to the vibrations of the elastomeric support body 12 can lead themselves. This can result in damping or eradication of vibrations of a higher frequency than is the case with the elastomeric support body 12 is possible. This can enable the damping or eradication of further and, in particular, higher-frequency vibrations than was previously possible through the use of the elastomeric support body 12 is known per se.

The end-side thickenings can 13b the additional masses 13 increase the amplitude of these counter-vibrations and thereby enable a particularly effective damping or eradication of the further and in particular the higher-frequency vibrations. This can also be implemented in a comparatively compact manner.

4th shows a schematic perspective view of a bearing according to the invention 1 in the form of a bearing bush 1 according to a second embodiment. 5 shows a schematic cross section of the 4th . 6 shows a detailed view of the 5 .

In this case there are elastomeric supports on each 12 one additional mass each 13 arranged as previously described with reference to the first embodiment. Two additional masses 13 are in the same space 14 arranged facing each other, in this case the two lateral spaces 14 the additional masses 13 exhibit. The properties according to the invention described above can also be implemented in this way.

The four spaces 14 each also have a stop element 17th on, each of the same elastomeric material as the elastomeric support body 12 on the inner part 15 formed and each radially outward to the inside of the outer ring 10th is aligned. This allows a damped elastic contact between the inner part 15 and outer ring 10th be made possible if vibrations with correspondingly large amplitudes between the inner part 15 and the outer ring 10th occur.

The outer ring 10th has three fasteners 11 in the form of locking elements 11 or of detents 11 which in the circumferential direction U evenly distributed, that is, offset by 120 ° to each other. The latches 11 can interact with the corresponding snap-in receptacle of the first rigid body, such as the chassis (not shown), around the bearing bush 1 to connect with this fixed.

Reference symbol list

R

radial direction

U

Circumferential direction

X

Longitudinal axis

1

Camp; Elastomeric bearings; Bearing bush; Gearbox bearing bush

10th

Outer part; Outer ring

11

Fasteners; Locking elements; Latches

12

(elastomeric) support body; Elastomer part; (elastomeric) struts

13

Additional dimensions of the support body 12

13a

web-like extension of the additional mass 13

13b

(End) thickening of the additional mass 13

14

Space

15

Inner part; inner part

16

admission

17th

elastomeric stop elements

Claims (11)

Bearing (1), in particular elastomer bearing (1), with an outer part (10), with an inner part (15), and with at least one support body (12) which is arranged between the outer part (10) and the inner part (15), characterized in that the support body (12) has at least one additional mass (13) which extends at least substantially perpendicular to the support body (12) and is at least partially movable parallel to the support body (12). Bearing (1) according to Claim 1 , characterized in that the additional mass (13) is designed to perform a counter-vibration to the supporting body (12). Bearing (1) according to Claim 1 or 2nd , characterized in that the additional mass (13) has a thickening (13b) pointing away from the supporting body (12). Bearing (1) according to Claim 3 , characterized in that the thickening (13b) pointing away from the supporting body (12) is arranged at the end of the additional mass (13) pointing away from the supporting body (12). Bearing (1) according to Claim 3 or 4th , 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 supporting body (12). Bearing (1) according to one of the preceding claims, characterized in that the additional mass (13) is formed in one piece with the supporting 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 formed from an elastomeric material. Bearing (1) according to one of the preceding claims, characterized by a plurality of support bodies (12) which are each arranged between the outer part (10) and the inner part (15), a plurality of 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 at least partially movable parallel to the respective support body (12). Bearing (1) according to one of the preceding claims, characterized in that at least two additional masses (13) are designed differently. Vehicle, especially land vehicle, with at least one bearing (1) according to one of the preceding claims, the bearing (1) being arranged between a vibration-generating component and a further component of the vehicle.

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