DE4117128C2 - - Google Patents

Description

The invention relates to a hydraulically damping bearing with the Features of the preamble of claim 1.

Such a bearing is known from JP 62-1 71 540 (A). The same thing only has two axially delimited from one another Throttle channel arrangement interconnected and with a Damping agent filled ring spaces. The one of those ring rooms is from the area expanded into the cone Vulcanized elastomer body of both bearing parts limited.

The elastomer body itself is in the conical ring area between two bearing parts solidly designed, what the damping capacity this bearing in a direction deviating from its axial direction Direction severely restricted.

JP 57-25 536 (A) is also a vibration-resistant bearing known that also one between an outer and one vulcanized, solid elastomer body having. Here the outer bearing part also forms a closure plate for a liquid space enclosed by the elastomer body, while the inner bearing part one from the elastomer body recorded, hollow-conical base forms, in which a vulcanized membrane housed on its inner circumference is, and the end wall centrally from a throttle bore is enforced.

This bearing enables an effective damping of axially directed Vibrations, however, remain radial vibrations  largely undamped because the volume of space changes with relative movements hardly any of the two bearing parts in the radial direction changed.

In addition to the bearing construction according to JP 62-1 71 540 (A), from which the invention is based, for technical background reference is also made to the bearing according to JP 62-2 24 744 - FIGS . 4 and 5, which, analogously to the invention, is likewise has two groups of two diametrically opposed, filled with damping agent and interconnected chambers, each chamber of one group axially adjacent to a chamber of the other groups.

This camp has only one cylindrical, the two Chamber group receiving elastomer body.

With regard to the design of this bearing for radial damping and axially directed vibrations are therefore often compromise solutions to look for as that for a desired softness of the bearing Radial dimension of the elastomer body required in the radial direction one required to support axially directed forces Rigidity opposes it.

The invention has for its object a bearing in one training corresponding to the preamble of claim 1 stating the radial and radial damping to be supported and damped and axial forces can be tuned.

This object is achieved by the characterizing Features of claim 1 solved.

The bearing construction according to the invention is accordingly four Chambers equipped, the conically enlarged section of the elastomer body at least partially the chambers of one of the two chamber groups. Both elastomer body sections can get wall thicknesses that relate to the required bearing softness have it tuned precisely.

Due to the at least partially in the conically expanded Ab Leave the cut of the elastomeric body into the molded chambers there are both radial and axial vibrations Effectively dampen both bearing parts to each other by such Movements in both chambers an exchange of damping fluid cause volume changes.

In the case of axial force, this takes place in the cylindrical Section of the elastomeric body located essentially the function of equalization chambers by putting in this from the two in the flared section of the elastomer body located damping fluid chambers is displaced.

The axial softness of the bearing becomes predominant through the flared section of the elastomer body  determined by this under the influence of axial forces on each other superimposed shear and compressive stresses.

A particular advantage of the invention is therefore that To be able to use bearings to support large axial forces, whereby by appropriate choice of the angle of attack of the ko nisch expanded elastomer body section the proportion of Compressive stress in this elastomer body section and thus the axial bearing softness can be determined.  

Advantageous embodiments of the invention are the subject of Subclaims.

In the drawing, an embodiment of the invention is shown posed. Show it:

Fig. 1 is a longitudinal section of the bearing taken along the line II of FIG. 2

Fig. 2 shows a cross section of the bearing taken along the line II-II in FIG. 1.

The camp has an outer bearing part 10 in the form of a circumferentially closed sheet metal jacket and an inner, cylindri's bearing part 12 which is sealed and axially secured in an intermediate sleeve 13 . Between the outer La gerteil 10 and the intermediate sleeve 13 , a preferably made of rubber elastomer body 14 is vulcanized.

As shown in FIG. 1, the outer bearing part 10 has a cylindrical section a, the length of which corresponds approximately to the axial dimension of a bearing receiving eye. The rest of the jacket portion b of the bearing part 10 extends, as shown in FIG. 1, in the region of the upper end of the bearing face obliquely outwards, upwards.

Bearing part 10 and the intermediate sleeve 13 together delimit a cylindrical annular space 16 in section a, while in section b both bearing parts 10 and 12 delimit a conical annular space 18 , the radial spacings of parts 10 and 13 or 10 and 12 between their cylindrical and conical Mantelab cut a and b to achieve radial and axial resilience, for example, correspond to each other.

To form the conical annular space 18 is on the corre sponding front end of the inner, from a diameter abge set bore 20 for receiving a clamping screw enforced th bearing part 12 preferably a corresponding, also penetrated by a bore 22 shaped plate 24 . However, a one-piece design of the inner bearing part 12 is also possible. Both annular spaces 16 and 18 are completely filled by the elastomer body 14 .

As shown in Fig. 1, the elastomer body 14 contains two axially spaced or separated by an intermediate wall 10 groups diametrically opposed, damping agent-filled, kidney-shaped chambers 26 , 26 ', 28 , 28 ', the axial and / or radial damping are connected to each other. They are formed by depressions molded into the elastomer body 14 and the inner bearing part 12 covering them. For this purpose, the intermediate sleeve 13 has corresponding windows 15 in the region of the depressions on the circumference.

The belonging to a chamber group chambers 28 and 28 'are provided approximately in the central region of the cylindrical Mantelabschnit tes a, while the other chamber groups belong to the chambers 26 and 26 ' at the angle α of the conical annular space 18 in the part of the elastomer present in this body 14 are molded and partially extend into the existing in the cylindrical sheath section a part of the Elastomerkör pers 14 .

Due to the arrangement of the two chamber groups, two mutually diametrical radial webs 30 and 32 are formed on the elastomer body 14 , which give the bearing in the plane containing this and the bearing axis 33 ent a higher rigidity than in the perpendicular thereto, the chambers 26 , 26 '; 28 , 28 'together with bearing axis 33 containing plane.

For hydraulic bearing damping, the diagonally opposite chambers 26 , 28 'and 26 ', 28 can be connected to each other via a dash-dotted line, for example. Via a portion of the outer circumference of the inner bearing part 12 along a Wen del extending throttle channel 34 and 36 . Both throttle ducts 34 and 36 are formed, for example, by grooves formed on one of the opposite circumferential sections of the inner bearing part 12 , which are covered in the chamber-free area by the intermediate sleeve 13 . This Kanalan arrangement allows only damping of axially and radially directed oscillating movements of the two bearing parts 10 and 12 to each other in the plane of the drawing.

With a matching cross-section and the same length of the Dros selkanäle 34 and 36 , the bearing damping with axial and radial bearing load is equally strong.

In the event that both throttle channels 34 and 36 are provided on the same peripheral portion of the inner bearing part 12 and intersect, there is the essential advantage that both bearing parts 10 and 12 are able to perform damped tilting movements to each other in the plane of the drawing.

This is possible by tilting both bearing parts 10 and 12 to each other from two pressurized, diagonally assigned chambers 26 , 28 'and 26 ', 28 damping fluid in the other two unloaded chambers 26 'and 28 and 26 , 28th 'Is displaced.

The damping of tilting movements can be changed in a simple manner in the sense of a softer damping, provided that in the elastomer body 14 at least one connected to the throttle channels 34 and 36 , correspondingly expandable damping means memory 38 is molded.

Another possible chamber connection provides, each belonging to each chamber group chambers 26 , 26 '; 28 , 28 'to connect with each other via a throttle channel 40 and 42 and in addition to connect the adjacent chambers 26 , 28 and 26 ', 28 'of both chamber groups via a throttle channel 44 and 46 penetrating the intermediate wall 19 to each other.

This chamber connection offers the main advantage of appropriate choice of cross sections of the throttle channels the In Select the intensity of the axial and radial damping differently to be able to. Tilting movements are also dampened.

Another variant of the chamber connection can consist in connecting the two throttle ducts 40 , 42 to one another via a connection line 48, which preferably extends in the axial direction and is indicated by dash-dotted lines. In this case, the arrangement of the throttle channels 44 and 46 running parallel to the axis is not required.

The radial damping is freely adjustable by appropriate selection of the cross sections of the throttle channels 40 and 42 , while in the axial damping through the throttle channel 48, a larger channel length is available and thus a larger liquid mass must be displaced. In this way, the absorber effect can be significantly increased.

The flow of the damping fluid in the throttle channels 34 and 36 or 40 and 42 and 48 can be influenced in terms of a desired damping behavior by the arrangement of valve membrane or flap-like throttle elements in at least some of the channels, which is a matter of convenience is not shown.

Finally, with a connection of all chambers 26 , 26 'and 28 , 28 ' via intersecting throttle channels 34 and 36 in axial and radial movements of outer and inner bearing parts 10 and 12 to one another by an additional, mutual connection of each to a chamber group belonging Kam mers 26 , 26 '; 28 , 28 'via a throttle channel 40 or 42, the damping behavior can be influenced accordingly, where in this case the radial damping and the damping of tilting movements compared to the axial damping offers a smaller damping effect.

With an axial bearing loading damping fluid is displaced from both chambers 26 and 26 ', for example. About the throttle channels 44 and 46 in the chambers 28 and 28 ', which in the annular space 18 between African bearing parts 10 and 12 before existing, elastomeric material both on Thrust, as well as pressure. Although due to the relatively large wall thickness (radial dimension c) of the hollow cylindrical section a of the elastomer body 14 , the bearing in the plane of the drawing is distinguished by a correspondingly large radial softness and since adequate supporting forces could not counteract it by correspondingly large, axially directed forces, thrust is superimposed - And compressive stresses in the elasto meren material of the annular space 18 supporting forces achieved, which also provide sufficient resistance to such large axial forces.

As shown in FIG. 1, 14 has the elastomeric body at its the conical annular space 18 opposite end 50 on the outside, each chamber 'adjacent 28 and 28, a kidney-shaped chamber the course of the following, groove-like indentation 52 and 54, respectively. Their arrangement is made, for example, such that their radial distance from the bearing axis 33 corresponds approximately to that between the outer chamber wall 62 or 64 and the bearing axis 33 .

Through such indentations 52 and 54 , the resilience speed of the chamber end walls 58 and 60 can be specifically adjusted to a desired softness of the bearing in the axial direction in an advantageous manner. The indentations 52 and 54 could also be provided inside the chamber.

Claims (9)

1.Hydraulically damping bearing, with an inner bearing part and an outer bearing part surrounding it, which then merge into a cylindrical section in a conically widening region in the same axial direction and which accommodate an elastomer body in the respectively enclosed ring regions which axially delimited one another , includes damping agent-filled spaces, which are located on the one hand in the cylindrical ring area and on the other hand are assigned to the conical ring area and are connected to one another via a throttle channel arrangement, characterized in that the spaces in the cylindrical and the in the conical ring area are each separated by a group of two diametrically opposite one another Chambers ( 26 , 26 '; 28 , 28 ') are formed such that each chamber ( 26 , 26 '; 28 , 28 ') of one group is axially adjacent to one chamber of the other group and that the chambers ( 26 , 26 ' ) extend between sections of the conically widening regions of the outer and inner bearing part ( 10, 12 ). 2. Bearing according to claim 1, characterized in that the chambers ( 26, 26 ' ) present in the conical ring region extend partially into the cylindrical ring region. 3. Bearing according to claim 1 or 2, characterized in that the distances between the inner and outer bearing parts ( 10, 12 ) are the same in their cylindrical portion and in the conical region. 4. Bearing according to one of the preceding claims, characterized in that the chambers arranged in the cylindrical section ( 28, 28 ' ) closing towards the outside end wall parts ( 58 or 60 ) of the elastomer body ( 14 ) per chamber ( 28 or 28' ) have a resilient deformation zone in the axial direction. 5. Bearing according to claim 4, characterized in that the deformation zones are formed by concentrically extending to the bearing axis ( 33 ), groove-like indentations ( 52, 54 ) and are provided on the outside of the end wall and have a radial distance from the bearing axis ( 33 ) which is approximately that between the outer peripheral wall of the chamber ( 62, 64 ) and bearing axis ( 33 ) corresponds. 6. Bearing according to one of the preceding claims, characterized by at least one with the throttle channels ( 34, 36; 40, 42 ) connected in the elastomer body ( 14 ) molded damping agent memory ( 38 ). 7. Bearing according to one of the preceding claims, characterized in that the chambers ( 26, 26 '; 28, 28 ') of each chamber group and the axially adjacent chambers ( 26, 28 or 26 ', 28' ) of both chamber groups each with each other are connected. 8. Bearing according to one of the preceding claims, characterized in that the chambers ( 26, 26 '; 28, 28 ') of each chamber group interconnecting throttle channels ( 40, 42 ) are mutually connected. 9. Bearing according to one of the preceding claims 1 to 6, characterized in that the mutually diagonally assigned chambers ( 26, 28 ';26', 28 ) of both chamber groups are each connected to one another via a throttle channel ( 34 or 36 ).