DE4117129A1 - Anti-vibration mounting assembly - has four internal chambers which are interconnected and filled with damping fluid - Google Patents

Abstract

The hydraulically damped anti-vibration mounting has an outer metal housing (10) which receives an elastomeric insert (14). The insert has a central through hole in which an elastomeric bush (12) is fitted. This bush (12) is vulcanised to a metal housing (16) which is vulcanised to the bore of the insert (14) which is, in turn, vulcanised to the outer metal housing (10). The elastomeric insert has four internal chambers which are filled with hydraulic damping fluid. The two chambers (24, 26) are diametrically opposite to each other and are interconnected by a circumferential groove (46) in the bush (12). The two chambers (28, 30) are also diametrically opposite and are interconnectedby the circumferential goove (48). The diagonally opposite chambers, (26, 28) and (24, 30) are interconnected by oblique grooves (32, 34). USE/ADVANTAGE - Anti-vibration mounting for road vehicles. The mounting damps out both axial and radial vibrations.

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 neter 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.

The invention has for its object a hydraulic damping bearing in training according to the preamble of Claim 1 to improve so that the bearing sleeve and  Bearing core are able to damped in addition Swinging movements in the axial and radial directions also in the the plane containing the chambers and bearing axis damped tilt movements to each other.

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

The mutual connection of the diagonally assigned Throttle channels connecting storage chambers 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 of the 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 latter case, damping flows are suppressed liquid of the loaded storage chamber diametrically opposite storage chamber of the same chamber group leads.

The embodiment of the invention according to claim 3 enables light also a different damping behavior of the Bearing in the axial and radial directions, in which the to each belonging to a chamber group, diametrically opposite each other lying storage chambers each have at least one throttle channel are directly connected and these Dros sel channels in cross-section smaller or larger than those for the slide gonal connection of throttle channels serving storage chambers can be laid.  

A further development of a bearing designed according to Pa claim 4 also enables different steaming behave in such a way that all have the same cross-section Throttle channels provide greater damping in the bearing axis direction is enough. This results from a particular in Bearing axis direction extending to the radial throttle channels each chamber group connected throttle channel, from which one accordingly longer displacement distance results, so that by additionally displacing liquid masses Inertia is increased accordingly.

In the drawing, embodiments of the invention are shown posed. Show it:

Fig. 1 shows a first embodiment of a hydraulically damped bearing, in longitudinal section,

Fig. 2 and 3 highly schematic representations of further mög Licher, mutual connections of the chambers of the bearing of FIG. 1.

The hydraulically damping bearing shown in Fig. 1 has an outer, cylindrical bearing sleeve 10 , one of these concentrically assigned bearing core 12 , a preferably rubber existing elastomer insert 14 and a bearing core 12 on the intermediate tube 16 .

The outer bearing sleeve 10 preferably 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, preferably rubber outer layer of small thickness can be vulcanized at least in some areas. 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 path of a spiral following incorporated are . They could also be formed by a bead formed in the intermediate tube 16 .

Both throttle channels 32 , 34 are formed, for example, by grooves formed on the same peripheral section 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 the chambers 24 , 26 , 28 and 30 are connected to one another in such a way that when the bearing sleeve 10 and the bearing core 12 move relative to one another, each from the pressurized chambers via the throttle channels 32 and 34 into the chamber diagonally assigned to each of these chambers Damping damping fluid can be displaced.

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 connected to the throttle channels 32 and 34 is molded into the elastomer insert 14 .

Fig. 3 shows a chamber connection, in which the respective egg ner chamber groups 24 , 26 and 28 , 30 are connected to each other via a throttle channel 40 and 42 , respectively. The throttle ducts 40 and 42 are in turn connected to one another by a throttle duct 44 which preferably extends in the bearing axis direction.

This channel arrangement also enables damped Kippbe movements of the bearing sleeve 10 and bearing core 12 to each other.

The radial damping is freely adjustable by appropriate selection of the cross sections of the throttle channels 40 , 42 , while a greater channel length is available in the axial damping through the throttle channel 44 and thus a greater liquid mass is to be displaced, whereby the absorber effect can be significantly increased.

The flow of the damping fluid in the throttle channels 32 , 34 or 40 , 42 and 44 can be influenced in terms of a desired damping behavior by the arrangement of valve, membrane or flap-like throttle elements in a part of the channels or in all channels what is not shown for the sake of simplicity.

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 Kippbe movements compared to the axial damping offers a smaller damping effect.

Claims (5)

1.Hydraulically damping bearing, with a bearing core, an outer bearing sleeve surrounding it with a radial spacing, egg nem arranged therebetween, elastomeric insert with two axially superimposed and separate groups of diametrically opposed damping agent-filled chambers that dial for axial and / or ra Damping are connected via throttle channels, characterized in that all chambers ( 24 , 26 , 28 , 30 ) are connected to one another. 2. Bearing according to claim 1, characterized by at least one with the throttle channels ( 32 , 34 ), in the elastomer insert ( 14 ) molded damping means memory ( 38 ). 3. Bearing according to claim 1 or 2, characterized in that the chambers ( 24 , 26 , 28 , 30 ) of each chamber group are interconnected via at least one throttle channel ( 40 ; 42 or 46 ; 48 ). 4. Bearing according to claim 3, characterized in that the chambers ( 24 , 26 , 28 , 30 ) of each chamber group with interconnecting throttle channels ( 40 ; 42 or 46 ; 48 ) are mutually connected to one another (channel 44 ). 5. Bearing according to claim 1, characterized, that at least part of the throttle channels with a throttle element ment is equipped.