DE4117129C2 - - Google Patents

Description

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

A bearing of this design is known from JP 62-2 24 744 A, FIGS . 4 and 5.

The mutual connection of its diagonally assigned to each other neten chambers via independent throttle channels enables damping of axial and radial vibrations. On the other hand, this bearing construction does not allow La gerhülse and bearing core to each other in the storage chambers and Execute damped tilting movements containing the bearing axis can.

From FIGS. 6 and 7 of the same document, even a bearing having the same mutual assignment of chambers is known, the outer and inner bearing part in the gerkammern the La and the plane containing the bearing axis damped Kippbe movements can perform one another, but this bearing is not capable , to dampen radial vibrations due to the mutual connection of adjacent chambers of both chamber groups.

Finally, a bearing is known from JP 60-1 39 942 (A), which is capable of both axially and radially directed vibration dampen movements as well as tilting movements. To do this However, a total of three throttle channels are required, which corresponds to one.  require elaborate design of the bearing core to the door between the two chamber groups.

The invention has for its object a hydraulic damping fendes camp in training according to the preamble of Pa to technically simplify and ensure tent claim 1 that by the same both damped swinging movements in the axial and radial direction, as well as in the chambers and At the bearing axis containing plane damped tilting movements towards each other that are possible.

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

The mutual connection of the diagonally assigned Bearing chambers with throttle channels connecting each other leads to that when tilting both bearing parts to one another from two struck damping fluid in the two storage chambers whose unloaded storage chambers are displaced, whereby the remaining storage chambers have a supporting function.

Intervention options for changing the damping behavior in the case of tilting movements of both bearing parts offer further training in Invention according to claims 2 and 3. In the former case there is an appropriately flexible displacement space available Available in the damping fluid ver when tilting is pushing.

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

Fig. 1 a hydraulically damped mounting device, in longitudinal section,

Fig. 2 shows the mutual connection of the storage chambers, highly schematic.

The hydraulically damping bearing shown has an outer, cylindrical bearing sleeve 10 , one of these concentrically assigned bearing core 12 , an elastomer insert 14 , preferably made of rubber, and an intermediate tube 16 receiving the bearing core 12 .

The outer bearing sleeve 10 has an outwardly provided ge edge piece to form a flange 18 which accommodates the mounting position of the bearing within a recess of a bearing, for example a subframe. On the outer circumference of the outer bearing sleeve 10 , as indicated at 20 , an elastomeric, for. B. rubber existing outer layer of small thickness. It serves to bridge larger diameter tolerances of the recess receiving the bearing.

The bore 22 , which penetrates the bearing core 12 in a graduated manner, serves to receive a clamping bolt in order to elastically connect the bearing receptacle to a further part.

The bearing core 12 is sealed in the intermediate tube 16 and axially secured, while this and the outer La gerhülse 10 are connected by vulcanization with the elastomeric insert 14 .

For hydraulic bearing damping serve two groups of chambers arranged in the direction of the bearing axis at a distance from one another, which are formed, for example, by recesses formed in the elastomer insert 14 and the bearing core 12 covering them.

Each chamber group comprises two diametrically associated chambers 24 , 26 and 28 , 30 , one chamber 24 and 26 of one chamber group, one chamber 28 and 30 of the other chamber group.

The chambers 24 and 30 as well as 26 and 28 are thus assigned dia gonal each other and a diagonally extending orifice passage 32 and 34 connected to each other, which choke channels 32 and 34 in the outer periphery of the bearing core 12, the Ver running a spiral following, incorporated are. They could also be formed by a bead molded into the intermediate tube 16 .

Both throttle ducts 32 , 34 are formed, for example, by grooves formed on the circumferential portion of the bearing core 12 , which are covered by the intermediate tube 16 in the chamber-free area.

At 36 , both throttle channels 32 and 34 intersect. Thus, all chambers 24 , 26 , 28 and 30 are connected to one another in such a way that when the bearing sleeve 10 and bearing core 12 move relative to one another, each from the pressurized chambers via the throttle channels 32 and 34 into the diagonally associated chamber of each of these chambers damping fluid can be displaced for the purpose of damping.

With a matching cross-section and the same length of the Dros selkanäle 32 , 34 , the bearing damping is the same strength with axial and radial bearing load.

Furthermore, in the radial plane containing the bearing axis and the bearing chambers 24 , 26 , 28 and 30 , in mutually opposite directions, a damped tilting of the bearing sleeve 10 and bearing core 12 to one another is possible, in that case from the respectively loaded, diagonally assigned bearing chambers, for example the Bearing chambers 26 and 28 , damping fluid over sections 32 'and 32 ''of the throttle channel 32 in the bearing chambers 24 and 30 is displaced.

The damping of such tilting movements can be changed in a simple manner in the sense of a softer damping, provided that, according to FIG. 2, at least one correspondingly expandable damping agent reservoir 38 is formed in the elastomer insert 14 connected to the throttle channels 32 and 34 .

The flow of the damping fluid in the throttle channels 32 , 34 can be specifically influenced in terms of a desired Dämpfungsverhal th by the arrangement of valve, membrane or flap-like throttle elements in part of the channels or in all channels, which is not for the sake of simplicity is shown.

Influencing the damping behavior with axial and Ra dial movements of the bearing sleeve 10 and bearing core 12 to each other can be in a bearing design according to FIG. 1 by the additional, mutual connection of each chamber group belonging to chambers 24 and 26 or 28 and 30 over each achieve a connecting channel 46 or 48 , in which case the radial damping and the damping of Kippbewe movements compared to the axial damping offers a smaller damping effect.

Claims (3)

1.Hydraulically damping bearing, with a bearing core, an outer bearing sleeve surrounding it at a radial distance and an elastomeric insert arranged therebetween with two axially superimposed groups of diametrically opposed, damping agent-filled chambers, where the diagonally assigned chambers of both groups are connected to each other by a throttle channel, characterized in that the two throttle channels ( 32 , 34 ) each follow the course of a spiral diagonally between the diagonally assigned chambers ( 24 , 30 ; 26 , 28 ) and thereby cut the. 2. Bearing according to claim 1, characterized by at least one with the throttle channels ( 32 , 34 ) connected, molded into the elastomer insert damping agent store ( 38 ). 3. Bearing according to claim 1 or 2, characterized in that at least part of the throttle channels ( 32 , 34 ) is equipped with a Drosselele element.