FR2670549A1 - SUPPORT LEVEL. - Google Patents

Abstract

The invention relates to a support bearing for the elastic assembly of two parts of a vehicle, in particular for connecting an auxiliary frame to a vehicle body, with an outer bearing element (18) which can be fixed to one of the vehicle parts and an inner bearing member (20) attachable to the other vehicle part, the bearing members (18,20) each having, from the same front end of the bearing, a peripheral face portion (c) extending with the same obliquity inwards, to which is connected a peripheral face part (b) parallel to the axis (56), and with rubber bodies (24,26) inserted between the two bearing elements and vulcanized to the two bearing elements (18,20) at least in the region of the peripheral face portions (b) parallel to the axis (56). According to the invention, the inner bearing element (20) is made in one piece and has a rhombic section, the outer bearing element (18) has casing parts (41,44; 48,52 ) parallel to the rhombus faces (42,46; 50,54) of the inner bearing member (20), and the rubber bodies (24,26) are associated in the manner of spacers to the rhombus faces (41 , 42; 44.46; 48.50; 52.54) and vulcanized on the latter.

Description

Support The present invention relates to a support bearing for

  the elastic assembly of two parts of a vehicle, in particular for

  connect an auxiliary frame to a vehicle body, with an element

  outer bearing element which can be fixed to one of the vehicle parts and an inner bearing element which can be fixed to the other vehicle part, the bearing elements each having, from

  from the same front end of the bearing, a part of the peripheral face

  risk extending with the same obliquity inwards, to which a peripheral face part parallel to the axis is connected, and with rubber bodies introduced between the two bearing elements and vulcanized on the two bearing elements at the less in the region of

  peripheral face parts parallel to the axis.

  Support bearings of this type are known and used for

  connect the front and rear auxiliary frames to the vehicle body

  particular types 190 E from Mercedes-Benz AG.

  In these support bearings, the rubber bodies of the vulcanized spacer type between the external element and the internal element

  bearing extend relative to the installation position of the

  tying, obliquely along their entire length, from above to

  outside down inside.

  These are mainly the angle of obliquity of the rubber bodies.

  chouc, their dimensioning and the quality of the rubber which determines

  the bearing flexibilities in radial directions perpendicular to the

  between them and in axial direction.

  The housing possibilities given for such support levels make it frequently impossible to obtain a relationship

desired between these flexibilities.

  The reason is that, for space reasons, the space re-

  cevant the rubber bodies between the inner element and the element

  bearing outside cannot be foreseen large enough.

  It is therefore necessary to seek a compromise for the angle of obliquity and the dimensioning of the rubber bodies perpendicular to the faces of the two bearing elements which must be joined to these bodies by vulcanization, compromise which provides to a small extent

  an acceptable harmonization of the flexibilities of the bearing, because of the vo-

  insufficient rubber lume that can be accommodated between the two elements

bearings.

  In addition to insufficient flexibilities of the bearing in the direction of the radial development of the rubber bodies and in the direction

  support bearing resulting from such an intermediate solution

  diaire, it is also necessary to consider drawbacks in terms of uncoupling of structural noise, since the reduced volume of rubber is accompanied by a corresponding reduction in the insulating effect

rubber.

  The object of the present invention is to indicate a support bearing of the type mentioned in the introduction, the configuration of which allows a desired harmonization of the radial and axial flexibilities of the bearing even when the given housing possibilities require a mode

compact construction.

  According to the invention, this object is achieved by the fact that the element

  bearing housing is made in one piece and has a rhombic section, that the outer bearing element has envelope parts parallel to the faces of the rhombus of the inner bearing element, and that the rubber bodies are associated like

  spacers with rhombus faces and vulcanized on the latter.

  According to an advantageous additional characteristic, the parts

  rubber bodies like spacers that extend parallel-

  According to an additional characteristic, the rubber bodies have a recess which extends at least over part of their axial length.

  another additional feature, elastic stops, mutual-

  opposite, are formed on the inner periphery of the element

  outer bearing between the rubber bodies of the spacer type.

  Finally, according to a final advantageous additional characteristic, the oblique parts of the rubber bodies are provided outside.

  a receiving element for the outer bearing element.

  According to the invention, the rubber bodies therefore extend, between the two bearing elements, parallel to the axis of the bearing on a first part and oblique to the axis of the bearing on a consecutive part. rubber body between the inner element and the outer element of the bearing offers possibilities of intervention in order to obtain an advantageous harmonization of the

flexibilities of the bearing.

  The parts of the rubber bodies which extend parallel to the axis of the bearing can receive a considerably larger radial dimension than those which extend exclusively obliquely between the two bearing elements, since the region between the two elements bearing, region which, in the bearing configuration

  known, is delimited by the upper outer edge and the inner edge

  lower laughter of the rubber bodies extending obliquely, can now, with the orientation parallel to the axis, be completely filled

  of rubber, so that you have a net volume of rubber-

much bigger.

  This large volume of rubber makes it possible to give the support bearing greater flexibility in this radial plane and thus to obtain a decoupling of the noise which is consequently improved. In addition, compared to the known bearing configuration with bodies in

  oblique rubber, the parts parallel to the axis of the rubber bodies

  chouc allow, during axial stresses of the bearing, greater relative movements between the two bearing elements for the same thrust stress, and therefore an increase in flexibility

axial of the bearing.

  The parts of the rubber bodies arranged obliquely to the axis of the bearing are subjected to thrust and compression stresses which are superimposed, a corresponding choice of the angle of obliquity making it possible to determine the share of the stress of

  compression and therefore the axial flexibility of the bearing.

  The configuration of the bearing provided by the invention therefore makes it possible to

  vary or even distribute the compression constraint shares

  the rubber bodies in their different

  parts so as to obtain, even with a

  bearing pact, bearing flexibilities which are found in a re-

Mutual relationship desired.

  An exemplary embodiment of the invention is shown in the accompanying drawings, in which: FIG. 1 is a view in longitudinal section of a support bearing along the line I-I in FIG. 2,

  Figure 2 is a cross-sectional view of the support bearing

  your along line II-II of figure 1,

  Figure 3 is a longitudinal sectional view of the support bearing

  along line III-III of figure 2 and

  FIG. 4 is a schematic representation intended to explain

  quer the advantages that allows to obtain the invention.

  The reference 10 designates the floor assembly of a passenger car and the reference 12 an auxiliary frame connected elastically to this floor assembly. The connection is made using support bearings 14 which, in a known manner, are each fitted into a

  receiver eyelet 16 of the auxiliary frame 12.

  The support bearings 14 have an external element of pa-

  link 18 in the form of a peripherally closed sheet metal envelope, and an inner bearing element 20 or central bearing element An elastic insertion element 22 of rubber is vulcanized between the two bearing elements 18 and 20 This element of insertion constitutes two rubber bodies of the kind spacers 24 and 26, mutually opposite The latter may, in order to obtain a desired flexibility of the bearing in the radial plane aa in which they are located, present

  each a recess 28 which, as shown in FIG. 1, extends through

  tially in the rubber bodies 24 and 26 in the axial direction of the support bearing 14; but these recesses could very well divide the rubber bodies 24 and 26 over the whole of their

axial extent.

  These recesses 28 are for example delimited laterally by plane faces 30 and 32, parallel to each other, partial rubber bodies 34, 36 and 38, 40 thus formed. These faces could also, as shown in phantom, be arranged forming between they have an acute angle open radially outwards, according to the bearing flexibility and the characteristic curve appearance which are required in the

radial plane a-a.

  The partial rubber bodies 34, 36, 38, 40 have pre-

  ference a rectangular section and are vulcanized on mutually opposite planar peripheral face parts 40,42, 44,46 and 48,50; 52.54, respectively of the outer bearing member 18 and the member

bearing interior 20.

  As shown in FIG. 1, the partial rubber bodies 34 to 40 extend parallel to the axis 56 of the bearing over a part b of their length, which preferably corresponds approximately to the axial dimension of the receiving eyelet 16 Their remaining part c extends, in the region of a front end of the bearing, between the partial faces designated respectively 58.62 and 60.64 of the element

  outside of bearing 18 and of the central bearing element 20, faces

  which are preferably arranged obliquely outwards, the oblique parts c of the partial rubber bodies 34 to 40 being provided on the front side of the bearing which is turned towards the assembly

floor 10.

  References 66 and 68 designate approximate recesses-

  kidney-shaped, passing through the support bearing 14 in the axial direction and associated with periphery parts of the central bearing element

  which are mutually opposite in a radial plane d-d perpendi-

  cular in the radial plane a-a, recesses whose delimiting wall op-

  posed to the central bearing element 20 constitutes for the latter a

radial stop 70.

  The sheet metal envelope constituting the outer bearing element 18

  is covered on the outside with a layer of rubber 72 which,

  lon Figure 1, forms at the lower front end of the bearing a support bead 74 which vertically covers the edge of the receiving eyelet 16 In the opposite axial direction, the wall portions disposed obliquely outward 58,62 of the sheet metal envelope 18 form, as shown in Figure 3, fixing stops in position. The central bearing element 20 can, with the aid of a fixing screw 76, be for example screwed to a plate-shaped connecting element 78 of the floor assembly 10, an element which for this purpose has a cylindrical centering collar 80, projecting towards the

  low and with an internal thread, which engages by complementa-

  form rity in a recess 82 provided on the front side of the central bearing element 20 In the screwed state, the central bearing element

  20 bears by one of its front faces against the coupling element

cord 78.

  The configuration of the bearing provided by the invention makes it possible to obtain a relationship between the rigidities of the bearing which cannot

  be obtained, for a given limited installation space, with

  Known support links of the type mentioned in the introduction.

  In this context, in order to explain the benefits that can be

  obtained by the invention, reference is made to FIG. 4.

  In this figure, the reference 84 designates an external element and the reference 86 an internal element of a known support bearing of the type mentioned in the introduction The reference 88 designates one of its

  two rubber bodies, which extend at an acute angle relative to

  bearing at axis 90 of the bearing With respect to a desired radial rigidity,

  relatively high, from the bearing in direction X, the rubber bodies

  chouc 48 are subjected to thrust and compression stresses which overlap, the compression stresses being clearly preponderant. The desired radial rigidity in this radial direction therefore requires a thickness e of the rubber bodies 88 which, on the one hand, cannot offer satisfactory noise decoupling between the auxiliary frame and the bodywork and which, on the other hand, does not allow to obtain the desired axial flexibility of the bearing only in a limited manner in the

  axial or support direction indicated by arrow 92.

  Unlike this situation, the rubber bodies 24.26

  in the configuration according to the invention may, due to the appearance

  parallel to the axis 90 of the bearing of their part b and of the oblique shape of

  their part c at an angle to be determined, receive a dimension

  significantly larger dial between the two bearing elements 84.86 compared to the known bearing configuration, which allows a

  improved insulation as a result of structural noise.

  It results from this increased radial dimension, for the same thrust stress of the parts b and c of the rubber bodies, increased strokes as a result of the inner bearing element 86, and

  therefore greater axial flexibility of the bearing.

  The part of compressive stress which appears in the event of axial bearing of the bearing is exclusively active in the oblique part c of the rubber bodies 24 and 26, where it is superimposed on the

  thrust stress of part c.

  In the radial direction d-d, the partial rubber bodies 34 to 40 are urged; as shown in figure 2, thanks to the adjustment of the obliquity of the partial rubber bodies 34 to 40, it is possible to obtain in these partial bodies, in the peripheral direction of the bearing, an adequate part of compressive stress in view

  to obtain a determined radial flexibility of the bearing.

  By the shape given to the intermediate space 28 in the rubber bodies 24 and 26 in order to increase their free surface, one can

  thus finely adapt the radial flexibility of the bearing in the horizontal plane

  dial a-a, or define it so that the elastic characteristic of

  rubber body 24 and 26, then stressed in compression, changes

  very gradually following a predetermined radial displacement of the central bearing element 20, by the fact that the faces

  mutually adjacent side 30 and 32 of the partial rubber bodies

  choux 34 to 40, faces which then curve outwards, apply

one against the other.

  The main design parameters determining for the harmonization of the elasticities of the support bearing according to the invention are: the quality of the rubber, the size of the rubber bodies 24 and

  26 in radial direction (layer thickness), their height and their width

  geur, the value of the angle of obliquity of the parts c of the rubber bodies

  chouc, possibly the arrangement of intermediate spaces 28 as well as the curvature of the rubber body in one piece 24 and 26 in the peripheral direction of the bearing, or else a corresponding oblique arrangement of the partial rubber bodies 34 to 40, under a

  obtuse angle to each other.

  An alternative to the described bearing configuration may consist

  ter to provide the rubber bodies in the form of correspondingly curved flat plates, which are vulcanized between planar and parallel partial faces of the two bearing elements, the planar partial faces of the external element being able to be provided on the respective branches of an external U-shaped bearing element.

Claims (4)

  1 Support bearing for the elastic assembly of two parts   of a vehicle, in particular for connecting an auxiliary frame to a body   vehicle series, with an outer bearing element which can be fixed to one of the vehicle parts and an inner bearing element which can be fixed to the other part of the vehicle, the bearing elements each having, from the same front end of the bearing, a peripheral face part extending with the same obliquity towards   the interior, to which a peripheral face part is connected   parallel to the axis, and with rubber bodies introduced between the two bearing elements and vulcanized on the two bearing elements at least in the region of the peripheral face parts parallel to the axis, characterized in that that the inner bearing element (20) is made in one piece and has a rhombic section, in that the outer bearing element (18) has envelope parts (41,44; 48,52) parallel to the rhombe faces (42,46; 50,54) of the inner bearing element (20), and in that the rubber bodies (24, 26) are associated in the manner of spacers with the rhombe faces (41.42;   44.46; 48.50; 52,54) and vulcanized on the latter.   2 support bearing according to claim 1, characterized in that the parts (b) of the rubber bodies of the spacer type (24, 26) which extend parallel to the axis (56) of the bearing are the longest. 3 support bearing according to claim 1 or 2, characterized in that the rubber bodies (24, 26) have a recess (28)   which extends at least over part of their axial length.   4 Support bearing according to any one of the claims   previous, characterized in that elastic stops (70), mutual-   opposite, are formed on the inner periphery of the element   outside of bearing (18) between rubber bodies of the kind tretoises (24, 26).   Support bearing according to any one of the claims   previous, characterized in that the oblique parts (c) of the rubber bodies are provided outside of a receiving element (16)   for the outer bearing element (18).