DE2838391A1 - RUBBER METAL BEARINGS, ESPECIALLY FOR THE PIVOTABLE LINKAGE OF A WHEEL GUIDE HANDLEBAR OR A AXLE JOINT ON THE ASSEMBLY OF A MOTOR VEHICLE - Google Patents

Description

VOLK SWAG ENWERK

SHARED COMPANY

¥ olfsburg
- 4 -

Our reference: K 2612
1702pt-gn-kl

Rubber-to-metal bearings, especially for the pivoting articulation of a wheel control arm or an axle group on the body of a motor vehicle

The invention relates to a rubber-metal bearing in the preamble of claim 1 specified genus.

Rubber-to-metal bearings of this type are used on a wide variety of technical niche areas are used when a first component is pivotably attached to a second component and at the same time the transmission of disruptive load surges or the noises caused by them should be avoided. Rubber-to-metal bearings are used in the various embodiments in particular for the pivotable Articulation of Eadführer members of motor vehicles used You have to be able to handle the compression and rebound the wheels occurring pivoting movements of the wheel guide members, d. H. the wheel control arm o. Ä. To perform, where the Rubber body is stressed on shear, and on the other hand, even on comparatively flat roads even with apparently the same = sustained cruising speed to absorb vibrations caused by micro-accelerations and micro-decelerations.

Rubber-to-metal bearings are - in special training - occasionally also used to additionally control the self-steering behavior of a

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Voriitiendor Vorjland: Toni Schmucker, Chairman - Horst Backsmann · Prol. Dr. techn. Ernst Fiala Dr. jur. Pete Frerk

dos Supervisory Board: Günter Hartwich Horst Münzner Dr. rer.pol. Werner P. Schmidt · Gottlieb M. Strobl · Prof. Dr. rer pol Friedner, Thomee

" ^{an5 S} '" ^{lbaum SHz der} G «« ll «hall: Wolfsburg District Court Weihburg HRB 215

Motor vehicle both "when cornering as auoh" during load changes to "influence. As is known, occurs in most motor vehicles when cornering due to existing elasticities in the wheel suspension, especially the rear axle under the influence of the lateral forces a tendency to oversteer on the wheels, which i. a. is undesirable. "To counteract this tendency to oversteer, it is known for the articulation on the body side ζ. Β. a transverse kerf, d. H. a wheel control arm, whose pivot axis runs roughly parallel to the vehicle's longitudinal axis, to use rubber-metal bearings of different flexibility and these to be dimensioned so that the wheel carrier when cornering to a substantially vertical axis is pivotable, which is seen in the direction of travel behind the axis of rotation of the wheel (z. B. DT-OS 23 36 787). For example, rubber-to-metal bearings are used for this, which under radial load as a result of the elastic material arranged recesses particularly flexible in certain directions (e.g. DT-GM 71 41159). When using semi-trailing arms, d. H. The wheels are articulated on the vehicle body via wheel control arms, the pivot axes of which are slightly oblique to the vehicle's longitudinal axis it is known for the articulation of the semi-trailing arm rubber-metal bearings use, which are axially particularly flexible, so that the trailing arm under the effect of occurring when cornering Centrifugal or lateral force is pivoted in the direction of toe-in.

The object of the invention is to create a rubber-metal bearing of the type mentioned in the preamble of claim 1, with the help of which the tendency to oversteer occurring when cornering is reduced or eliminated even in those wheel guide gates in which the pivot axis is transverse, ie at an angle of at least runs approximately 90 ^° to the longitudinal axis of the vehicle. In particular, rear so-called composite or coupling link axles or rear trailing arms with two bearing points on the body are considered.

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According to the invention, this object is achieved by the characterizing features of claim 1. The metal cans of the Rubber-to-metal bearings are designed in such a way that they - in conjunction with the rubber body - form a kind of slide ramp, so that when axial forces are introduced, such as those that occur when cornering, specific radial forces occur, through which the inner and the outer metal sleeve are specifically shifted radially against each other in a predetermined direction, what with appropriate adaptation of the two articulation points on the body side of the wheel guide members for the desired pivoting the wheel guide member leads.

Further advantageous configurations and developments of the invention that are essential to the invention are contained in the subclaims specified.

Although rubber-metal bearings have already been proposed (P 27 48 193.2), where the introduction of axial forces Radial forces also occur in a targeted manner, by means of which the inner and outer metal sleeves are deliberately moved into a predetermined one Direction are shifted radially against each other, but the rubber body itself is designed in a special way in these bearings. With these bearings, the possible radial displacement is often not - if the bearing dimensions are not to be too large as big as you would like it to be for technical reasons. Additional difficulties are caused by the local to Part of very high stresses in the rubber.

In the drawing there are four Alis guide examples in a schematic representation of the invention reproduced, which are explained in more detail with reference to the following description.

In Figure 1 is the plan view and the section along the plotted Section line of a first rubber-metal bearing shown according to the invention. The outer metal sleeve of this camp

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is numbered with 1 and the inner metal sleeve with 2. The elastic rubber body that connects the two metal bushes and is vulcanized onto both metal bushes is numbered 3. The outer surfaces of the inner and outer metal sleeves 1 and 2 facing the rubber body 3 run obliquely to the bearing axis A of the rubber-metal bearing. In relation to the bearing axis A, they represent lateral surfaces of oblique circular cylinders. The inner metal bushing 2 Ir ^ nn with its central bore 23 forming the bearing axis A, for example, are connected to a bearing pin arranged on the vehicle body of a motor vehicle, while the outer metal bushing 1 is concentric with its to the bore 23 arranged outer lateral surface can be pressed into the bearing eye of a wheel control arm or an axle assembly. It can be seen that the two metal sleeves 1 and 2 are displaced radially against each other when axial forces are introduced into the bearing due to their lateral surfaces running obliquely to the bearing axis A. In FIG. 1 it was assumed that an axial force F ₁ acts on the outer metal bushing 1, which is connected, for example, to a wheel control arm, which creates a corresponding reaction force F .. ¹ on the inner metal bushing, which is connected to a bearing pin as mentioned above 2 has the consequence. Taking into account the direction of inclination selected in the illustrated embodiment of the lateral surfaces resting on the rubber body 3, an outer metal sleeve is formed in the plane of the drawing _{as a result of the axial force F 1 introduced}

-χ · radial force F shifting to the left. The magnitude of the radial force F and thus the magnitude of the relative radial displacement of the metal sleeves depends on the selected inclination of the metal sleeves, the thickness of the rubber and the hardness of the rubber. It can be seen that a radial force acting in the opposite direction is generated when the axial force F _{1 is introduced} into the outer metal sleeve 1 from the other end face. The rubber-metal bearing shown in Figure 1 is there-

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11

equally effective for both directions of force.

While the rubber body 5 of the rubber shown in Figure 1 = metal bearing connects the two metal sleeves with each other along their entire circumference, are the two metal sleeves 1 or 2 and the rubber body 3 in the rubber-metal bearing shown in Figure 2 is designed so that the rubber « body "the two metal sleeves are connected to one another only along a circumferential area of less or approximately 180 ° det, wherein the metal sleeves 1 and 2 have lateral surfaces of oblique circular cylinders only in this area. in the remaining circumferential area, the two metal sleeves are not connected to one another. The first consequence of this is that, in contrast to FIG. 1, the desired radial displacement occurs only in one direction. Is it desirable or it is necessary that a radial displacement in the other direction occurs with the corresponding direction of force, then two sub-bearings can be axially joined directly to one another to form an overall bearing that the diagonally to the bearing = axis A extending lateral surface areas are arranged offset from one another 180 °, both on the bearing axis A. as well as to the butt joint B between the two part bearings. In Figure 2 is a composite of such part bearings Total warehouse shown. The individual parts of the upper part of the warehouse are identical to those already used in FIG Numbers and those of the lower second part of the warehouse are provided with corresponding numbers supplemented by an apostrophe. Essentially This results in the same mode of operation for this overall bearing as for the rubber-metal bearing shown in FIG. where the ratio between the axial force introduced and the radial displacement force achieved is in turn dependent on the selected Data of the items depends. Since the bevels of the jacket surfaces connected to the rubber body are at the overall bearing shown in Figure 2 are opposite to the incline shown in Figure 1, results in the same direction

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tion of the introduced axial force F * a compared to Figure 1 acting in the opposite direction radial Force F *.

In the exemplary embodiments according to FIGS. 1 and 2 are the inclined lateral surfaces of the two metal bushings 1 and 2 connected to the rubber body 3 within the actual bearing body arranged. In the examples According to FIGS. 3 and 4, these inclined lateral surfaces causing the radial displacement are axially adjacent the actual bearing body arranged, wherein the in Figure 4 The bearing shown is composed of two sub-bearings. These Rubber-to-metal bearings each have a first bearing area in which the two metal sleeves 1 and 2 form concentrically arranged, straight cylinders 11 and 21, respectively. Axially on it then a second storage area is provided in which the two metal bushings with respect to their rubber body 3 facing lateral surfaces represent truncated cones 12 and 22, respectively. The rubber body extends in relation to the bearing axis A - only in a range of less than 180 with an axial extension 31 between these two truncated cones. In the exemplary embodiment shown in FIG. 3, the outer metal sleeve 1 is a rotationally symmetrical body with a cylindrical first area and an axially adjoining, frustoconically widening second area, while the inner metal sleeve 2 is only partially rotationally symmetrical Represents body, which consists of a cylindrical first area and an axially adjoining it, only in widening in a frustoconical manner to a circumferential area of less than 180 ° second area consists. It is of course also possible to design both metal sleeves as rotationally symmetrical bodies and only the one in the frustoconical area protruding extension 31 of the rubber body 3 on a peripheral area limit of less than 180. As shown in Figure 4, both metal sleeves 1 and 2 can be used as only partially

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rotationally symmetrical body, each with a cylindrical first area 11 or 21 and an axially adjoining it, frustoconical only in a circumferential range of less than 180 widening second area are formed. Which of these variants is used depends on the individual case ultimately depends on manufacturing conditions. These bearings are correct in terms of their functionality - provided they have the same dimensions - match. These rubber-to-metal bearings are also effective as individual bearings in only one direction. Should one corresponding radial displacement can also be achieved for the axial forces introduced in the opposite direction, then, as already shown and explained in FIG. 2, two sub-bearings must again be axially joined directly to one another to form an overall bearing as shown in FIG.

The greatest possible radial displacement is achieved in the bearings shown in FIGS. In terms of stress, however, the most favorable conditions for the rubber body J exist when the frustoconical surface area 12 of the outer metal sleeve 1 is more inclined towards the bearing axis A than that of the inner metal sleeve 2, in such a way that the fictitious cone tips of these two truncated cone areas are at least approximately the same Point of the bearing axis A come to rest. It therefore depends on the individual application which dimensioning is the most favorable for the inclination of the truncated cone surfaces.

The exemplary embodiments shown in FIGS. 3 and 4 enable a particularly good radial displacement due to their strongly inclined sliding surfaces outside the actual bearing body and they also allow for good noise isolation to accommodate the necessary large rubber layer thickness «,

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TJm is the displacement ratio between axial and radial force To further improve it is possible and in the rest of the Figures 3 imcL 4 shown, the rubber body 3 in the cylindrical To provide the first storage area with preferably kidney-shaped recesses 32.

From the embodiments shown it can be seen that the Direction of radial displacement from the installation position of the rubber-metal bearing and depends on the direction of the applied axial force. If the rubber-metal bearings according to the invention for the swiveling articulation of a wheel control arm or an axle group (e.g. twist beam axle or coupling link axle) on the Structure of a motor vehicle are used, then to achieve the desired self-steering behavior, the respective Installation conditions must be taken into account. In Figure 5 ·. is schematic one part, namely the left part of a so-called coupling link axle, which essentially consists of two rear wheels load-bearing trailing arms and a rigid, but torsionally flexible transverse strut connecting the two trailing arms with one another consists. Only the left trailing arm 6 with the left rear wheel 5 mounted on it and the cross strut 7 are shown Coupled link axle assembly is articulated to the vehicle body 4, which is only indicated, via rubber-metal bearings of the type described above. What is indicated is a sub-store of the type shown in Pigur 3, with the one usually provided for the sake of simplicity kidney-shaped recesses · has been omitted. The outer metal sleeve, not numbered further, is torsion-proof in a bearing eye of the trailing arm 6 and the inner metal sleeve, which is also not further numbered, rotatably with an am Vehicle body 4 attached bearing bolts 8 connected. The linkage of the right trailing arm, not shown, takes place in a corresponding manner, with the rubber-metal bearing installed in mirror image is. The bearing axis A runs transversely to the longitudinal axis of the vehicle. The direction of travel of the vehicle is indicated by an unspecified one Arrow 'indicated. In Figure 5 is to explain the mode of operation

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assumed that a lateral force F acts on the wheel 5, as occurs, for example, when driving through a right-hand bend. Correspondingly, on the rubber-metal bearing, the force F. on the outer metal sleeve and ^ ^{0 on the inner metal sleeve}

slave

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Deviating from the application described with reference to FIG the "stressed rubber-metal bearings can of course also use to achieve other defined deflections of wheel guide members. For example, it is conceivable that the To train wishbones of a front axle by using such a rubber-metal bearing so that the wishbone moves when the speed changes due to the forces then acting on the wheel, at least approximately only shifts in the longitudinal direction of the vehicle and as a result, fewer undesirable lane changes occur.

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COPY

Claims (13)

VOLKSWAGENWERK SHARED COMPANY Wolf sburg our reference: K 2612 % \. 8.78 17Q2pt-gn-kl AHSPEÖ CHE M .J rubber-to-metal bearing with a metal sleeve arranged between an outer and an inner metal sleeve and vulcanized onto it elastic rubber body, characterized in that the rubber body (3) facing Jacket surfaces of the inner and outer Metair bushes (1, 2) at least partially at an angle to the bearing axis (A) of the rubber-metal bearing run in such a way that the inner and outer metal bushes "when axial forces are introduced into the bearing in a targeted manner predetermined sighting are shifted radially against each other. 2. Good metal bearing according to claim 1, characterized in that the lateral surfaces in relation to the Bearing axis (A) of the rubber-metal bearing represent the lateral surfaces of oblique circular cylinders or sections thereof. 3. rubber-metal bearing according to claim 2, characterized in that the rubber body (3) the two metal sleeves (1, 2) only along a peripheral range of approximately 180 ° connects with each other and that the metal sleeves have lateral surfaces in this area oblique circular cylinders. 4. Gummimet all ^ -bearing according to claim 1, characterized by a first storage area in which the metal cans (1, 2) concentrically arranged, straight cylinders (11, 21) 030012/0111 Chairman of the Board of Directors: Toni Schmucker, Chairman · Horst Backsmann · Prof. Dr. techn. Ernst Fiale ■ Dr. yes, Peter Frerk de «Supervisory Board: Günter Harwich ■ Horst Münzner · Dr. rer.pol. Werner P. Schmidt ■ Gottlieb M. Strobl · Prof. Or. Rer. pole. Friedrich Thomee Hans Birnbaum Seat of the company: Wolfiburg District Court Woltsburg HRB represent, and an axially adjoining second bearing area in de. the metal sleeves with respect to their rubber body (5) facing Represent lateral surfaces of truncated cones (12, 22), with the rubber body - in relation to the bearing axis (A) - only in a circumferential area of less than 180 ° with an axial port set (3I) between the two truncated cones (12, 22). 5. rubber-metal bearing according to claim 4> characterized in that the two metal sleeves (1, 2) as a rotationally symmetrical body with a cylindrical first area and an axially adjoining, frustoconically widening second region are formed. 6. Rubber-metal bearing according to claim 4 » characterized in that the outer metal sleeve (1) is a rotationally symmetrical body with a cylindrical first area and one axially adjoining it, frustoconical expanding second area and that the inner metal sleeve (2) as partially rotationally symmetrical Body with a cylindrical first area and an axially adjoining it, only in a circumferential area of less designed as a frustoconical widening second area 180 ° is. 7. rubber-metal bearing according to claim 4> characterized in that the two metal sleeves (1, 2) as a partially rotationally symmetrical body with a cylindrical first Area and an axially adjoining it, only widening in a frustoconical manner in a circumferential area of less than 180 ° second area are formed. 8. Rubber-to-metal bearing according to claims 4 "to 7» characterized in that the frustoconical lateral surface areas (12, LJ) of the two metal sleeves (1, 2) at least approximately are equally inclined towards the bearing axis (A). 030012/0111 9. rubber-metal bearing according to claims 4 to 7 »characterized in that the frustoconical lateral surface area (12) of the outer metal sleeve (1) is more inclined towards the bearing axis (A) than that of the inner metal sleeve (2), in such a way that their fictitious cone tips are at least approximately in the same point of the bearing axis (A). 10. Rubber-metal bearing according to claims 4 to 9 » characterized in that the rubber body (3) in the cylindrical first storage area is provided with kidney-shaped recesses (32). 11. rubber-metal bearing according to claim 1, characterized in that two part bearings according to one of the claims 3 to 10 are axially joined directly to one another to form an overall bearing that their inclined to the bearing axis (a) Outer surface areas - related to both the bearing axis (A) and the butt joint (B) - offset by 180 ° from one another are arranged. 12. Rubber-metal bearing according to one of claims 1 to 11, characterized by its application for pivoting articulation a wheel control arm or an axle assembly on the structure of a Motor vehicle, the bearing axles (A) aligned transversely to the vehicle longitudinal axis and the rubber-to-metal bearings are installed in such a way that the resulting radial displacement of the metal sleeves (1, 2) runs at least approximately horizontally. 13. rubber-metal bearing according to claim 12, characterized in that the direction of the radial displacement of the individual rubber-metal bearing in each case to that of the remaining rubber-metal bearings of the wheel guide arm or the axle assembly is coordinated that this when driving through a curve in the direction Toe-in is pivoted. 030012/0111