DE2838391C2 - Rubber-to-metal bearings for the storage of a wheel guide member - Google Patents

Description

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

Rubber metal bearing for the storage of a wheel guide member , 1111 The structure of a motor vehicle must be able to handle, on the one hand, the when driving in and out of the wheels due to the swiveling movements of the wheel guide elements. i.e. the wheel guide arm or the like, to be carried out, whereby the rubber body is stressed on shear, and on the other hand also on comparatively even roads with apparently constant travel speed due to micro-accelerations to absorb vibrations caused by micro-bulges.

Rubber-metal bearings are also used - in special designs - to additionally influence the self-steering behavior of a motor vehicle both when cornering and when changing loads. It is known that most motor vehicles tend to oversteer when cornering due to the elasticity present in the wheel suspension, especially the rear axle, under the action of animal lateral forces on the wheels. which is generally undesirable. In order to counteract this tendency to oversteer, it is known to use an anti-skid linkage / ... for example, a wishbone, ie a rail guide link. whose

The pivot axis runs approximately parallel to the longitudinal axis of the vehicle. Rubber-to-metal bearings of different To use / .en compliance and to measure it in such a way that that the wheel carrier can be pivoted about a substantially vertical axis when cornering in the direction of travel seen behind the axis of rotation of the wheel (z. II. DE-OS 23 36 787). For this purpose, for example, Ciummimetall-Lagcr used, which under radial influence of l.asia particularly due to the recesses arranged in the elastic material in certain directions are flexible (e.g. DE-GM 71 41 159).

When using semi-trailing arms, d. H. Via wheel control arms, the pivot axes of which are somewhat oblique to the longitudinal axis of the vehicle run, articulated wheels on the vehicle body, it is also known for the body-side articulation to use the trailing arm rubber-metal Lagc-r, which are particularly flexible axially, so that the Semi-trailing arm under the effect of centrifugal or lateral force in the direction of toe-in when cornering is pivoted.

In the non-prepublished DE-OS 27 48 193 is also already a Gurrimirrietall warehouse for storage a wheel guide member described in de-J between an outer and an inner metal sleeve arranged and vulcanized thereon elastic rubber bodies - With respect to the bearing axis of the rubber-metal bearing - at least partially not rotationally symmetrical is trained. With this rubber-metal bearing, radial forces occur when axial forces are introduced on, through which the inner and outer metal sleeves are shifted in a targeted manner in a predetermined direction will. The possible radial displacement is with them - the bearing dimensions should not be too big - often not as big as it is from technical engineering Reasons would be desirable. Also, under certain circumstances, very high local stresses can occur in the Gurr.micorper.

The object of the invention is to provide a rubber-metal bearing of the type mentioned in the preamble of claim 1 Art to create, with the help of which while maintaining acceptable storage dimensions and avoiding them particularly high local stresses in the rubber body, the tendency to oversteer occurring when cornering a motor vehicle can be dismantled or removed even with such wheel guide members can, where the pivot axis is transverse. d. h at an angle of at least approximately 90 ″ to the longitudinal axis of the vehicle runs. In particular, rear so-called composite or coupling link axles are considered here or on the rear trailing arm with two mounting parts.

According to the invention, this object is achieved by the characterizing features of claim 1. The metal bushings of the rubber meiall bearing are so designed that they - in connection with the rubber body - form a kind of slide ramp, so that when axial forces are introduced, such as those when cornering occur, targeted radial forces occur, by means of which the inner and outer metal sleeves are directed radially against one another in a predetermined direction be shifted, which with appropriate adaptation of the two Aufbauseitencn articulation points Wheel guide members leads to the desired pivoting of the wheel guide member.

Further advantageous embodiments of the invention and further developments of the invention are in specified in the subclaims.

In tier drawing are in schematic representation four exemplary embodiments of the invention reproduced, which are based on the following description explained.

In Fi g. 1 shows the top view and the section along the line of intersection of a first rubber-metal bearing according to the invention. The outer metal sleeve of this bearing is marked with t and the inner metal sleeve with 2 bc / il'fcrt. The two metal cans !! 1 and 2 connecting and vulcanized elastic rubber bodies are numbered with 3. The outer surfaces of the inner and outer metal bushings 1 and 2 facing the rubber body 3 run at an angle to the bearing axis A of the rubber-metal bearing. With respect to the bearing axis A , they represent lateral surfaces inclined circular cylinders. The inner metal sleeve 2 can be connected with its central bore 23 forming the bearing axis A, for example, with a bearing pin arranged on the vehicle body of a motor vehicle, while the outer metal sleeve 1 with its concentric to the bore 23 arranged outer jacket surface in the bearing eye /: ies Radführung-! CTikcis b / w. can be fitted into an axis system. 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 Fi g. 1 it was assumed that an axial force F acts on the outer metal bushing 1, which is connected to a wheel control arm, for example, which results in a corresponding reaction force Fi 'on the inner metal bushing 2, which is connected to a bearing pin as mentioned above. Taking into account the embodiment shown in the! As a result of the axial force Fi introduced, a radial force F which shifts the outer metal sleeve to the left in the plane of the drawing forms from the chosen direction of inclination of the lateral surfaces resting on the rubber body 3. The size of the radial force F and thus the size of the relative Rad.alver displacement of the metal bushings I and 2 depends on the bevel chosen, 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 Fi comes from the other end face

> is inserted into the outer metal sleeve 1. This in F i g. The Giimmimeutll-Lagcr I shown is therefore for both Direction of force equally effective.

While the Gunimi body 3 of the in F i g. 1 shown Gimimimeiall-l. Camps along the two menill tins

What connects them to one another in their minded extent are the two metal cans ^ 1 b / w. 2 as well as the rubber body 3 in the case of the one shown in FIG. 2 gc / cigtcn rubber-to-metal bearings vi formed that the Guirmikbody 3 the two Mctallbf'chi.-n I and 2 only along a peripheral area of

) connects less or approximately 180 with each other, the metal lenses 1 and 2 nu "in this area Have lateral surfaces of inclined circles / cylinders. The two metal rifles are in the rest of the surrounding area 1 and 2 .licht in connection with each other. That

The first consequence of i is that the desired radial displacement on the contrary * «! / to F i g. I only go one way occurs. It is desirable! or necessary that with appropriate Force direction also a radial displacement occurs in the other direction, then two can

. Tcillager be axially unmivelbar so joined to a Gcsaintlag <_T that the obliquely / ur Lagerachsc Λ extending Manielflächenbereiche 1 OEO "geaeneinaniler \ crscl / l · anireordni are! .Mil / vnr Kui-mM

related to the bearing axis A as well as to the butt joint H between the two partial bearings. In Fig. 2 shows an overall bearing made up of such sub-bearings. The individual parts of the upper part of the warehouse are provided with the numbers already used in FIG. 1 and those of the lower second part of the warehouse with corresponding numbers supplemented by an apostrophe I. The rubber bearing shown in FIG F ig. I are opposite to the incline shown, there is a radial force F acting in the opposite direction compared to FIG. 1 with the same direction of the axial force introduced.

In the exemplary embodiments according to FIGS. 1 and 2, the inclined lateral surfaces of the two metal sleeves I and 2, which are connected to the rubber body 3, are arranged within the actual bearing body. In the exemplary embodiments according to FIGS. 3 and 4, these inclined lateral surfaces causing the radial displacement are arranged axially next to the actual bearing body, the in FIG. 4 bearing shown is composed of two sub-bearings. These rubber-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 adjoining this is a two-part first bearing area in which the two metal bushings represent truncated cones 12 and 22 with respect to their jacket surfaces facing the rubber body 3. The rubber body extends - with reference to the bearing angle A - only in a peripheral area of less than 180 ° with an axial extension 31 between these two truncated cones in the exemplary embodiment shown according to FIG. 3, the outer metal sleeve 1 is designed as 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 a body that is symmetrical in terms of rotation and consists of a cylindrical first area and an axially adjoining, exists only in a circumferential area of less than 180 "conical cone-shaped widening second area. It is of course also possible to design both metal sleeves as rotationally symmetrical bodies and only the extension 31 of the rubber body 3 protruding into the frustoconical area to a circumferential area of less than 180" restrict. As shown in Fig.4. Both metal bushes 1 and 2 can also be designed as only rotationally symmetrical bodies, each with a cylindrical first area 11 or 21 and an axially adjoining second area that only widens in a frustoconical manner in a circumferential area of less than 180 '. Which of these variants is used ultimately depends on the manufacturing conditions in each individual case. In terms of their functionality, these bearings - provided they have the same dimensions - are the same. These Gurnrnimetali-LagCT are as single bearings only effective in one direction. If a corresponding radial displacement is also to be achieved for the axial forces introduced in the opposite direction, then as in FIG. 2 has already been shown and explained, in turn, two sub-bearings are axially joined directly to one another to form a total bearing, as shown in FIG. 4 is shown.

^r . The greatest possible radial displacement is achieved with the in FIGS. 3 and 4 is achieved when the frustoconical outer surface areas 12 and 22 of the two metal bushings I and 2 are inclined at least approximately equally with respect to the bearing axis 4.

in terms of stress, however, the most favorable conditions for the rubber body 3 are then present. when the frustoconical jacket surface area 12 of the outer metal sleeve I is more inclined towards the bearing axis A than that of the inner metal sleeve 2, namely

ι i such that the fictitious spherical tips of these two truncated cone areas come to lie at least approximately in the same point of the bearing axis A. It therefore depends on the individual application which dimensioning is the most favorable for the inclination of the Kegeistumplllflächen

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

To Cms shift ratio between axial and It is also possible to further improve radial force borrowed and in ile fig. 3 and 4, the rubber body 3 in the cylindrical first bearing area, each with preferably kidney-shaped recesses 32 strand.

From the exemplary embodiments shown, it can be seen that the direction of the radial displacement depends on the installation position of the rubber-metal bearing and on the direction of the axial force. If the rubber-metal bearings according to the invention are used for the pivoting articulation of a wheel control arm or an axle assembly (e.g. twist beam axle or Koppelknkerachsc) on the body of a motor vehicle, the respective installation conditions must therefore be taken into account in order to achieve the desired self-steering behavior. In Fig. 5 a part, namely the left part of a so-called coupling link axle is shown, which consists essentially of two trailing arms supporting the rear wheels and a rigid but torsionally flexible cross strut connecting the two trailing arms. Only the left trailing arm 6 with the left rear wheel 5 mounted on it and the cross strut 7 are shown. A part bearing of the type shown in FIG. 3 is indicated, the kidney-shaped recesses usually provided not being shown for the sake of simplicity. The outer metal bushing, which is not numbered further, is connected in a torsion-proof manner in a bearing eye of the trailing arm 6 and the inner metal bushing, which is also not further numbered, is connected to a bearing bolt 8 attached to the vehicle body 4. The articulation of the right trailing arm, not shown, takes place in a corresponding manner, with the Giimmimciall bearing being installed in mirror image. The bearing axis A runs transversely to the longitudinal axis of the vehicle. The direction of travel of the vehicle is indicated by an arrow that is not numbered. In Fig. 5 is

To explain the mode of operation, it is assumed that the wheel 5 is attacked by a Seiienkrafi, as it cnistehi, for example, when driving through a right-hand bend. F.ntsprechcnd are most Gummimet.ill-Lagcr to the outer metal can and the force F effective on the inner \ metal bushing the associated Kcaktionskraft / V, the fintsprechend mil to F i g in connection. Explanations made to I to 4, with this constellation of facilities and with the present installation direction of the rubber-metal bearing, a displacement force F acting on the outer metal bushing and acting in the direction of travel occurs. How is to be understood. this causes a slight pivoting of the entire axle system, in the direction of toe-in; in the shown Alis guide example something in the clock / ei- r, gersinn. When driving through a left curve, the corresponding conditions would take place on the right trailing arm, not shown further. If, in deviation from the in FIG. 5 an; iiis j \ jjp \ Tciüiigern / liSümmeTigcscizic. Stock c ;;; - jw speaking F i g. 4 or F i g. 2 is used, then the trailing arm is not only shifted in the direction of travel on the wheel on the outside of the curve - as in FIG. 5 -. but at the same time, on the wheel on the inside of the bend, the trailing arm is shifted in the opposite direction, opposite to the direction of travel. As has already been stated, the rubber-metal bearings of the type shown in FIG. 5 and in FIG. 3 can only bring about a substantial radial displacement in one direction, namely when the one between the inclined metal bushing parts If this part is subjected to tensile stress, a noticeable shift does not take place. It can be seen that in the assumed load case of the ("fig tensile stress occurs, so that a displacement of the outer metal sleeve can not take place. Corresponding conditions occur at the shown bearings when driving through a left turn, where the plotted in w Fig. 5 forces F, F \ and F \ would each act in the opposite direction.

Notwithstanding that based on the FIG. 5 described application, the stressed rubber-metal bearings of course also use to achieve other defined deflections of wheel guide members. For example, it is conceivable to use a control arm of a front axle To train rubber-metal bearing so that the wishbone is in speed changes due to the w then acting on the wheel forces at least approximately only shifts in the longitudinal direction of the vehicle and thereby fewer unwanted lane changes occur.

For this purpose 2 sheets of drawings

Claims (13)

Patent claims: 1. Rubber-metal bearing for the storage of a wheel guide member, with an elastic rubber body arranged between an outer and an inner metal bushing and vulcanized onto it, which - with respect to the bearing axis of the rubber-metal bearing - is at least partially not rotationally symmetrical. the inner and outer metal bushes being shifted radially against each other in a specific direction when axial forces are introduced into the bearing, characterized in that, in order to achieve the desired radial displacement of both metal bushes (1, 2), the outer surfaces of the inner rubber body (3) facing and the outer metal sleeve (I ₁ 2) - with respect to the bearing axis (A) of the rubber-metal bearing - run at least partially Oiräg. 2. Gurnrnirneiaü-bearing according to claim 5, characterized in that the lateral surfaces represent oblique circular cylinders or sections thereof with respect to the bearing axis (A) of the rubber meiall-l ^ agers. 3. rubber-metal bearing according to claim 2, characterized in that the rubber body (3) the two Metal cans (I, 2) connects to one another only along a circumferential area of approximately 180 ' and that the metal bushes in this area are jacket surface! ·. : n have oblique circular cylinders. 4. Rubber-to-metal bearing narh claim 1, characterized by a first bearing area in which the Metallbüchscn (1,2) are straight cylinders (11, 2t) arranged in a concise manner, and an axially dar- r> adjoining second bearing area in which The metal bushes represent conical sockets (12, 22) with respect to their outer surfaces facing the rubber body (3), the rubber body - in relation to the bearing axis (A) - only in a circumferential area of less than 180 'with an axial extension (31) between the two truncated cones (! 2, 22) extends. 5. rubber-metal bearing according to claim 4, characterized in that the two metal sleeves (1, 2) r> as a rotationally symmetrical body with a cylindrical first area and an axially adjoining it, frustoconically widening second area are formed. 6. rubber-metal bearing according to claim 4, characterized in that the outer metal sleeve (1) as a rotationally symmetrical body with a cylindrical first area and an axially adjoining, frustoconical widening second area and that the inner metal sleeve (2) as γ, A rotationally symmetrical body with a cylindrical first area and an axially adjoining second area which only widens in a frustoconical manner in a circumferential area of less than 180 ". wi 7. rubber-metal bearing according to claim 4, characterized in that the two metal sleeves (1,2) • Partly rotationally symmetrical body with a cylindrical body first area and an axially adjoining only in a range of t, -, less than 180 "kcgelsiumpffoniiig expanding / wide area are formed. 8. Gummimciall-l.iiger according to ilen claims 4 to 7, characterized in that the frustoconical Surface areas (12, 22) of the two metal bushings (1, 2) are at least approximately the same are strongly inclined towards the bearing axis ^. 9. rubber metal bearing according to claims 4 to 7, characterized in that the frustoconical jacket 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), such that the fictitious cone tips at least approximately in the same point of the bearing axis (obligation. 10. rubber metal bearing according to claims 4 to 9, characterized in that the rubber body (3) is provided with kidney-shaped recesses (32) in the cylindrical first bearing area. 11. Rubber-metal bearing according to claim 1, characterized in that two sub-bearings according to one of claims 3 to 10 are axially directly joined to one another to form an overall bearing that their mantle surface area extending obliquely to the bearing axis (A) - as well as on the bearing axis (A) ) as well as related to the butt joint ^ - are arranged offset by 180 ° from one another. 12. Rubber-metal bearing according to one of claims 1 to 11, characterized in that when installed in the vehicle, the bearing axis (A) are aligned transversely to the longitudinal axis of the vehicle and the bevels of the lateral surfaces such that the resulting radial displacements of the metal sleeves (1,2) run at least approximately horizontally. 13. Guinmime'.all camp according to claim 12, characterized characterized in that the direction of radial displacement of the individual rubber-to-metal bearings in each case to that of the other rubber-to-metal bearings of the articulated wheel guide member or the axle group is matched. that this when driving through a curve in the direction of toe-in is pivoted.