GB2041485A - Fluid-damped elastomeric mountings - Google Patents
Fluid-damped elastomeric mountings Download PDFInfo
- Publication number
- GB2041485A GB2041485A GB7926447A GB7926447A GB2041485A GB 2041485 A GB2041485 A GB 2041485A GB 7926447 A GB7926447 A GB 7926447A GB 7926447 A GB7926447 A GB 7926447A GB 2041485 A GB2041485 A GB 2041485A
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- GB
- United Kingdom
- Prior art keywords
- piston
- restriction
- rubber
- rubber mounting
- plate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
- F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
Abstract
In a rubber mounting comprising three mounting plates interconnected by two annularly shaped rubber spring members 13, 11 to define upper and lower fluid-filled working spaces 1, 14, a plate 3 is disposed between the spaces and is resiliently supported for axial movement between two sealing positions, the plate 3 occupying a mean position when its support is unstressed. Communication between the two fluid-filled working spaces is via a restriction 4 defined at least partially by the plate 3 and by a transfer passage 9 the transfer passage being closed when the plate is in a sealing position. Low frequency high amplitude movements in either direction cause the plate to close the transfer passage 9, flow taking place through the restriction 4. At high frequencies, the plate 3 takes up a position where the passage 9 is open. <IMAGE>
Description
SPECIFICATION
Rubber mounting with hydraulic piston damping
The invention relates to a rubber mounting with hydraulic damping in which a mounting plate, a carrier flange and a base plate are connected together respectively by annularlyshaped spring elements of a rubber-like resilient material, and in which each spring element additionally defines an upper and a lower working space, which are each filled with a fluid, and which are connected together by a restriction.
A rubber mounting of this kind is known from German Patent 945 899. It is characterised in that, at uniform amplitude of the exciting vibration and increasing frequency, the damping, or the loss factor, increases at first, up to a maximum value. During this there exists a relationship between the speed with which the damping fluid flows through the restriction, and the damping obtained. If thereafter the frequency is raised still further, then the quantity of fluid flowing through the restriction diminishes, and also its speed, so that one reaches a decrease in the damping.
This decrease in the damping with further increasing frequency is brought about in that the resistance to flow of the restriction becomes greater than the resistance of the resilient boundary walls of the working spaces, which has the consequence that these deform in themselves, and accommodate a part of the compressed fluid. In consequence less and less fluid flows through the restriction, until finally above a predetermined frequency the entire compressed fluid is accommodated by the yielding bounding walls. As regards the dynamic properties there results from this above the said predetermined limiting frequency the disadvantage of a dynamic pressure increase in the main working space with the consequence of a significant dynamic stiffening of the mounting.For better understanding these occurrences are explained in more detail below with reference to the diagram appearing as Fig. 6 in the accompanying drawings.
The dynamic pressure differences in the main chamber are plotted against the exciting frequency f, and in particular on the one hand the component which is brought about by the damping and on the other hand the component which is brought about by the resilient surrounding walls. It is to be observed that the two components are displaced by 90 in phase. The pressure variation consequent on the damping is proportional to the speed and rises with increasing frequency in the frequency range f < f,. The pressure variation proportional to travel in consequence of the elasticity of the resilient surrounding walls varies only insignificantly in this frequency range, i.e. practically the total fluid flows through the restriction.
At the frequency f = f, the pressure component proportional to speed attains its maximum, while the component proportional to travel has risen slightly. With further increase of the exciting frequency, the pressure component proportional to speed decreases, while the component proportional to travel increases more strongly, i.e. less and less fluid flows through the restriction and the flow speed diminishes in spite of increasing frequency.
From frequencies f < f2, the damping is approximately zero, while the pressure component dependent on travel has attained substantially its terminal value.
Particularly in the mounting of an internal combustion engine in a motor vehicle, the requirement has now been established to provide damping as high as possible in the lower frequency range (between about 5 to 1 2 Hz), in order to maintain the vibrational travel of the engine as small as possible on excitation by irregularities in the road, and in the higher frequency range above about 30 Hz to isolate well the vibrations coming from the engine.
The first reqirement of high damping in the lower frequency range is fulfilled here, while the second requirement for good isolation is only fulfilled partially. In fact good isolation presupposes low spring stiffness and if possible no damping. The damping does indeed tend towards zero, but the spring stiffness increases with increasing frequency.
The object underlying the invention is to develop this mounting so that at higher frequencies of for example greater than 30 Hz no significant dynamic hardening of the mounting occurs, and that the good damping properties in the lower frequency range are maintained or improved.
This object is solved according to the invention in that the restriction 4 is contained in a piston 3 with two sealing surfaces, which is mounted to be movable in the axial direction between two abutments 6, 1 7 of the carrier flange 8, while the mean position is fixed by at least one resilient element 5, in such a way that a transfer passage 9 is constituted between the sealing surfaces 15, 1 6 and the abutments, and that the self-frequency of the piston lies in the range of the desired maximum damping.
The present invention starts from the recognition that, in a rubber mounting of the kind defined above, there exists a direct proportional relationship between the loss factor defining the damping, and the dynamic spring stiffness. According to the invention a rubber mounting with hydraulic piston damping, comprising a mounting plate, a carrier flange and a base plate, the mounting plate and base plate being connected to opposing sides of the carrier flange by annularly-shaped spring elements of a rubber-like resilient material to define upper and lower working spaces, the mounting further including a piston having upper and lower sealing surfaces, the piston being mounted to be movable in its axial direction between upper and lower sealing positions, and being resiliently supported in a mean position between the upper and lower sealing positions by at least one resilient element, the upper and lower working spaces being filled with a fluid medium and being in communication with each other via a restriction defined at least partially by the piston, and by a transfer passage, the transfer passage being closed both when the piston is in the upper and the lower sealing positions, the self-frequency of the piston lying in the range of the desired maximum damping.
It is clear that the restriction hitherto arranged fixed in the carrier flange is now provided in a piston which is connected by a resilient suspension with the carrier flange and which is movable between two abutments.
The mass of the piston and the elastic suspension then constitute a vibratory system, the resonant frequency of which is arranged to lie in the range of the vibrations to be damped.
Along with the restriction itself there is present as a second connection between the two working spaces, a transfer passage with a cross section which is significantly greater than the cross section of the restriction itself.
In the rest condition the piston is held in a mean position by the one or more resilient elements, in such a way that the transfer passage 9 is open. This mean position is not affected by the static forces introduced through the mounting plate 7, because an exactly balanced pressure exists in both working spaces. The position of the piston is thus determined exclusively by the resilient elements.
During dynamic loading with large amplitude of for example more than 0.5 mm and a low frequency, upon flexing of the mounting plate into the upper working space a hydraulic pressure builds up as a consequence of the flow resistance of the restriction and of the transfer passage, which forces the piston against the lower abutment. The fluid can then still only flow through the restriction, by which a large damping is created. Upon unloading of the mounting plate, the piston swings in the opposite direction against the upper abutment, so that the transfer passage is again closed according to the above-mentioned operating conditions with high damping.
One can now increase the elastic resilience of the resilient elements 13, 11, for example by selection of a rubber-like resilient material with greater stiffness, and one obtains an increase of the loss factor and thus of the damping in the zone of the previously-mentioned vibrations with low frequency and large amplitude. The dynamic hardening of the mounting increases however also, in this frequency range, which however is not significant in the range of lower frequencies.
With further increasing exciting frequency and decreasing amplitude, the stroke travelled by the piston parallel to the applied vibration as a consequence of its inertia also becomes smaller, and finally it no longer reaches the abutments, but finally it remains in the mean position. As a consequence of the increasing opening of the transfer passage 9 which then occurs, the cross section of which is significantly greater than that of the restriction, there occurs, with the higher frequencies which have now been reached, an exchange of fluid without significant pressure drop between the two working spaces. An increase of the damping only reappears if on the basis of a further increase of the applied frequency, flow velocities of the damping fluid arise in the neighbourhood of the transfer passage which correspond to the critical speed in the restriction at low frequencies.The further progress of the damping behaviour above this frequency then corresponds in principle to that which has been mentioned above with reference to the restriction.
With the viewpoint given above, it has appeared advantageous with regard to the manufacture of a mounting for a piston engine in a motor vehicle, if the free cross section of the transfer passage 9 in the mean position corresponds to at least 30 times the value of the free cross section of the restriction. With the corresponding construction, in the zone of large engine vibrations in the lower frequency zone of about 5 to 20 Hz, good damping results can be achieved, while with higher frequencies with small amplitudes from about 30 Hz a good isolation is provided. Only with significantly higher frequencies, which according to the type of engine can lie above 200 Hz, does there arise the second damping maximum, and the dynamic hardening which is undesired in the thinking of the invention and which is substantially removed in the lower frequency range. The second damping maximum and the start of dynamic hardening can be put off if desired, if the ratio of the cross section between the restriction and the transfer passage is increased or decreased if necessary from the above-mentioned factor.
According to a particular construction, provision is made that the length of the restriction is at least 50 times the value of the associated diameter. By a corresponding variation of the restriction a significant improvement of the damping behaviour at low frequencies can be obtained, without increase of the spring stiffness at higher frequencies. The objective underlying the invention, namely to construct the mounting in such a way, with a good damping behaviour at low frequencies, that it ensures a good isolation of the applied vibrations at high frequencies, is obtained with such a construction in a particularly advantageous manner.
The rubber mounting according to the invention can vary in a number of ways having regard to particular boundary conditions resulting from practical use.
The piston can in an advantageous manner be an annular ring guided on a projection of the carrier flange, while the cross section of the restriction is formed by the free space between the projection and the internal diameter of the ring.
The piston 3 can also be formed of a flat circularly-shaped disc of a rubber-like resilient material, which is connected in the centre with a mounting 210, and which has a circumferential bead 203, with two external sealing surfaces. One or more associated restrictions of the piston can then be made long or short, and they can be arranged in any part of the disc. It has appeared particularly advantageous if the restriction is a part of the mounting, or if it is vulcanised on to the disc as a circumferential tube 204 in the neighbourhood of the external circumference. In the last-mentioned case, there results from the vulcanising on of the tube an additional mechanical stiffening of the disc in the neighbourhood of the external circumference, which is of particular advantage in relation to the sealing obtained between the sealing surfaces which exist there and the abutments 6, 17.
By the mass of the tube, according to the selection of material, the weight of the piston and thus the resonant frequency of the vibrating system can alter.
According to another advantageous construction, provision is made that the piston is a flat disc of a rubber-like resilient material, which is anchored with a circumferential bead 11 2 in a turn-over of the carrier flange 8, and which has within the bead a plurality of openings 11 3 distributed around the periphery, forming parts of the transfer passages, the piston also having sealing surfaces on both its faces in a zone radially inside the openings. With such a construction, to avoid the disc deforming radially inside the sealing surfaces in undesired manner under operating conditions, it has appeared as advantageous to stiffen this zone additionally statically if desired, for example in that in this zone stiffening ribs or strengthening inserts are applied.According to a particular construction, provision is made to install in this zone an independent component of a stiff material with one or more restrictions, for example by adhesion onto the disc, by vulcanising on, or
by bolting. A corresponding restriction can receive any desired length, while however regard should be had that the total weight enters as a significant parameter into the resonance frequency determining the operat
ing properties. The designer has to have regard to this in establishing the choice of material and of the external appearance of the component.
According to another advantageous construction, provision is made that the piston 3 is a disc of metal, which guided in a concentric position parallel to the axis of an opening in the carrier flange, by nibs 10 projecting beyond the external periphery, and that as the resilient element a plurality of pegs of a rubber-like resilient material are provided, which are a part of the annular spring members, and which abut resiliently against the disc, and that the abutments of the carrier flange each consist of a circumferential bead, 6, 8 of a rubber-like resilient material.
A rubber mounting of this kind can be manufactured in a particularly simple manner on a mass-production scale. The disc can for example be a flat plate of steel, of another metal, or of a fibre-reinforced plastics material. In the last-mentioned case there results a particularly high resonance frequency.
The mechanical preparation of the disc requires no special precision, but in general the emplqyment of simple stamping procedures is sufficient.
The mean position of the disc is determined resiliently by the pegs of a rubber-like resilient material engaging its surfaces. It is important that the movability of the disc in the axial direction is not unduly hindered by the abutment of the pegs, and the choice of material of the pegs as well as of the cross section in the critical bending zone is to be determined accordingly. It is not absolutely necessary that the pegs be integral with the spring member, but it is also possible to mount the pegs if required as inserted members in the disc.
Such a construction is however rather more time-consuming in manufacture, and the additional weight of the pegs as well as their satisfactory anchoring require particular consideration. In the construction first mentioned however, the pegs can be made in a single manufacturing operation directly in one with the spring members without special efforts being necessary. By shaping the cross section of the circumferential bead 6, 8 in a form similar to that of a sine curve, there results with such a construction the further advantage, that a thorough sealing is achieved even with employment af discs with a relatively uneven surface and of small press force.
The sealing is then produced regularly lry a very closely defined contact surface betvuk qn the piston and the respective bead, which is advantageous during the time which occurs after the reversal of the direction of pressure up to the respective disengagement of the piston from the bead.
It is in consequence not necessary with such a construction to employ discs which have a high grade surface quality in the zone of the sealing surfaces.
Some constructions of the rubber mounting according to the invention by way of example are shown in the accompanying drawing.
There are shown:
Figure 1 a rubber mounting with a piston in the form of a flat disc.
Figure 2 with a piston in the form of a membrane, in which in the zone of the axis of symmetry a stiffening body with a restriction is vulcanised in.
Figure 3 a rubber mounting with a piston in the form of a membrane, which is fastened in the centre to a support, and the restriction of which consists of a spirally wound tube.
Figure 4 a fragment of a rubber mounting similar to that of Fig. 3, in which however the transfer passage and the restriction are combined into a unit, so made that the restriction consists of one or more grooves extending in the radial direction, which interrupt the sealing surfaces and/or the abutments.
Figure 5a rubber mounting corresponding to Fig. 3, in which the piston is formed of annular shape, and is guided on a cylindrical projection of the carrier flange.
Figure 6 is a diagram showing the variation of dynamic pressure difference against exciting frequency.
Fig. 1 shows a rubber mounting according to the present invention, consisting of a mounting plate 7, a carrier flange 8 and a base plate 2, which are each connected together by an annularly shaped resilient element 1 3, 11 of a rubber-like resilient material, and in which each spring element additionally defines an upper working space 1 and a lower working space 14, which are each filled with a fluid, and which are connected together by a plurality of restrictions 4.
The restrictions are contained in a piston 3 formed as a flat disc, which is guided coaxially to the axis of symmetry of the rubber mounting by a plurality of nibs 10 distributed around the circumference. The piston consists of sheet metal or of a fibre-reinforced plastics material, and it is mounted to be movable in the axial direction between an annular circumferential upper abutment 1 7 and a lower abutment 6 of the mounting plate. The piston, in the neighbourhood of each of the abutments, has an associated annular circumferential sealing surface 1 5, 1 6. Because of the formation of the cross section of the abutments, the piston does not require any specially high degree of finish even in the area of the sealing surfaces.It consists of a stampedout component, which can be obtained by simple stamping from usual commercial sheetlike material.
The abutments 6, 1 7 are a portion of the spring elements vulcanised onto the carrier flange. In consequence their manufacture does not require any additional working step.
The mean position assumed by the piston in the vibration-free condition, or with vibrations above a predetermined limiting frequency, is produced by pegs 5 of a softly resilient material abutting resiliently against the surfaces of the piston. Just as with reference to the number of the nibs 10 present around the periphery of the piston, it has appeared to be advantageous if the number of peg pairs distributed around the circumference is restricted to 3. With a higher number of pairs of pegs, which is entirely possible, difficulties can arise with a unitary formation together with the rubber-like spring elements 13, 11 as regards the obtaining of the desired softly resilient properties.
The carrier flange has two bores 18, 19, by which it can be bolted to the vehicle frame of the motor vehicle. The mounting plate includes a projecting threaded stud 20, on which the engine to be supported is mounted and screwed down. Of course it is likewise possible to provide an internal thread if desired in the mounting plate, and to carry out the mounting of the engine correspondingly in the reverse manner.
The carrier flange is divided into two, and includes on the lower side in an annular recess a sheet metal component 21 with an angle-shaped cross section, onto which the lower spring element 11 with the base plate 2 is vulcanised. Good resuls are also obtained if the two parts are bolted or welded together.
Fig. 2 shows a rubber mounting according to the present invention, in which the upper spring element is arranged radially outside a part of the carrier flange 8 projecting in the axial direction. Such a construction makes possible in a particularly uncomplicated manner the introduction of an end abutment, by which the reduction of the axial spacing between the mounting pate 107 and the carrier flange during overloading can be limited to a predetermined dimension.
The mounting plate 107 is provided on its outer periphery with an annular-shape projection 11 5 enlarged conically downwards, onto which the upper spring element is vulcanised.
In the lower part the carrier flange has a circumferential annular groove, in which the piston 3, formed like a membrane, is sealingly embedded with a bead 11 2 running round the outer periphery, and in which the piston is anchored by axial pressing on of the abutment plate 110. Against the lower side of the abutment plate there lies a sheet metal component 11 6 with an angle-shaped cross section, which is mounted with the abutment plate in the same groove, and which is anchored in it by a beading over 22 of the carrier flange.
Onto the inner side of the sheet metal component 11 6 there is-vulcanised the lower spring element 11, and onto this as a separate unit the base plate 2.
The abutments are constituted by an annularly extending ridge 1 7 of the carrier flange, and a similar ridge 6 of the abutment plate.
The surfaces of the two components facing the piston are symmetrically shaped.
The piston has at its circumference at least two uniformly spaced openings 113, which lie between its sealing surface and the bead 11 2 running round its outer periphery. The openings can be circularly or oval shaped, and they constitute a part of the transfer passage.
The other part of the transfer passage is constituted by the spacing of the surface of the piston from the associated abutment at the time. The spacing affects also the elasticity of the piston and thus its vibrating behaviour.
The upper working space 1 and the lower working space 14 of the rubber mounting are connected by a restriction 4. This is contained in a special component 103 of a rigid material, which is vulcanised into the central part of the membrane-like piston 3. The two parts can if desired also be fastened together or secured by adhesive. The length of the restriction is substantially greater than its diameter. Advantageously this value amounts to at least 50 times that of the diameter. Purely on grounds of clarity of illustration, the diameter of the restriction is exaggerated.
Fig. 3 shows a rubber mounting according to the present invention, which in its external construction resembles the construction according to Fig. 1. The mounting plate 7 is also in this construction vulcanised together with the carrier flange 8 by means of an annular spring element arranged to extend outwardly from the mounting plate. Directly vulcanised onto the carrier flange is the lower spring element 11, while the manufacture has been carried out in such a way that no adhesion exists on the annular circumferential surfaces between the corners A and B. The base plate is assembled from a cylindrical component 214 vulcanised onto the lower spring element, and a relatively flat lower plate 21 3. Both components are connected together in a liquid-tight manner, preferably by rivetting or welding together.
In a groove of the carrier flange there is anchored a support 210, which in its central part is connected by rivetting with the piston 3 formed like a membrane. The piston formed like a membrane is stiffened in the area of the outer periphery by a circumferential ring 212 of metal, and it has within the ring a restriction in the form of a helically-wound tube 204 vulcanised into the membrane.
Outside the ring an annular projecting bead is vulcanised onto the piston, the lateral flank surfaces of which are formed as sealing surfaces. Thè-associated abutments are constituted by a circumferential rubber bead 6 of the mounting plate and by a circumferential corner 17 of the support 210. In the mean position produced by the resilient properties of the piston formed like a membrane the transfer passage is constituted by the spacing between the sealing surfaces and the abutments.
In the construction shown a "long restriction" is again employed, i.e. the length of the tube vulcanised into the piston amounts to at least 50 times the internal diameter of it. In a simpler construction it is also possible to use a short tube and for this purpose for example to employ a hollow rivet, by which the piston is connected with the support 210.
An alternative construction for the formation of a "short restriction" in a rubber mounting according to Fig. 3 is shown in Fig. 4. Here the restriction is divided longitudinally, and it consists of one or more grooves 305, 306, which interrupt the abutments, and of a plurality of further grooves 304 associated with these grooves, which interrupt the sealing surfaces of the piston. In the mean position determined by the resilient properties of the piston formed like a membrane, these parts constitute a direct portion of the transfer passage 309. When the piston is in a sealing position, grooves 304, 305 and 306 provide communication between the working spaces.
The remaining construction corresponds to the construction according to Fig. 3.
Fig. 5 shows a rubber mounting similar to
Fig. 3, in which the piston 203 is constructed of annular shape, and is mounted in the carrier flange 8 by at least three radially extending external bars 209 of a resilient material. The separation of the two working spaces 1 and 14 occurs by means of a plate with an upstanding peripheral flange 205 rigidly secured to the mounting 210, and surrounded by the piston 203. An annular gap 204 formed between the flange 205 and the piston 203 fulfils the function of the previously-described restriction 4. The transfer passage 9 is formed by the respectively smallest spacing between the piston and the abutments 6, 1 7. The piston is stiffened by an annular insert 212 of metal.
CLAI MS
1. A rubber mounting with hydraulic piston damping, comprising a mounting plate, a carrier flange and a base plate, the mounting plate and base plate being connected to opposing sides of the carrier flange by annularlyshaped spring elements of a rubber-like resilient material to define upper and lower working spaces, the mounting further including a piston having upper and lower sealing surfaces, the piston being mounted to be movable in its axial direction between upper and lower sealing positions, and being resiliently supported in a mean position between the upper and lower sealing positions by at least one resilient element, the upper and lower working spaces being filled with a fluid medium and being in communication with each other via a restriction defined at least
**WARNING** end of DESC field may overlap start of CLMS **.
Claims (14)
1. A rubber mounting with hydraulic piston damping, comprising a mounting plate, a carrier flange and a base plate, the mounting plate and base plate being connected to opposing sides of the carrier flange by annularlyshaped spring elements of a rubber-like resilient material to define upper and lower working spaces, the mounting further including a piston having upper and lower sealing surfaces, the piston being mounted to be movable in its axial direction between upper and lower sealing positions, and being resiliently supported in a mean position between the upper and lower sealing positions by at least one resilient element, the upper and lower working spaces being filled with a fluid medium and being in communication with each other via a restriction defined at least
partially by the piston, and by a transfer passage, the transfer passage being closed both when the piston is in the upper and the lower sealing positions, the self-frequency of the piston lying in the range of the desired maximum damping.
2. A rubber mounting according to claim 1, in which the resilient element or elements is or are part of the piston.
3. A rubber mounting according to claim 1, in which the resilient element or elements is or are attached directly to the carrier flange.
4. A rubber mounting according to claim 1, in which the resilient element or elements is or are parts of the annularly-shaped spring elememts.
5. A rubber mounting according to any preceding claim, in which the free cross section of the transfer passage when the piston is in the mean position is at least 30 times the area of the free cross section of the restriction 4.
6. A rubber mounting according to any preceding claim in which the length of the restriction corresponds to at least 50 times the value of the associated diameter.
7. A rubber mounting according to any preceding claims 1 to 3, in which the piston is constituted by an annular ring, guided on a projection of the carrier flange, and that the restriction is constituted by the free clearance between the projection and the internal diameter of the ring.
8. A rubber mounting according to any of claims 1 to 6, in which the piston is a flat annular ring of a rubber-like resilient material, which is connected in the centre with a carrier, and which has a bead running around the outer circumference, with two external sealing surfaces.
9. A rubber mounting according to claim 8, in which the restriction is arranged in the carrier.
10. A rubber mounting according to claim 8, in which the restriction is a circumferential tube vulcanised into the ring in the neightbourhood of its outer periphery.
11. A rubber mounting according to claims 1 to 3, in which the piston is a flat disc of a rubber-like resilient material, which is anchored in a beaded-over part of the carrier flange by a circumferential bead, and which has a plurality of openings distributed around the circumference and forming part of the transfer passages, the disc also having sealing surfaces on both its faces in a lying radially inwardly of the openings.
12. A rubber mounting according to claims 8 to 11, characterised in that the restriction is contained in a component of a rigid material connected with the piston.
13. A rubber mounting according to claims 1 to 6, in which the piston is a disc of metal, which is guided in a concentric position parallel to the axis of an opening of the carrier flange, by nibs 10 projecting beyond the outer periphery of the piston and that as resilient element there are provided a plurality of pins of a rubber-like resilient material, which are integral with the spring members, and which abut resiliently against the disc, and that the abutments of the carrier flange each consist of a circumferential bead of a rubber-like resilient material.
14. Rubber mounting according to claim 13, characterised in that the disc is a flat plate of metal or of a fibre-reinforced plastics material.
1 5. A rubber mounting substantially as herein described with reference to Fig. 1, Fig.
2, Figs. 3 and 4 or Fig. 5 of the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2905090A DE2905090C2 (en) | 1979-02-10 | 1979-02-10 | Rubber mount with hydraulic damping |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB2041485A true GB2041485A (en) | 1980-09-10 |
| GB2041485B GB2041485B (en) | 1983-09-01 |
Family
ID=6062627
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB7926447A Expired GB2041485B (en) | 1979-02-10 | 1979-07-30 | Fluid-damped elastomeric mountings |
Country Status (6)
| Country | Link |
|---|---|
| JP (1) | JPS55107145A (en) |
| DE (1) | DE2905090C2 (en) |
| FR (1) | FR2448673B1 (en) |
| GB (1) | GB2041485B (en) |
| IT (1) | IT1118200B (en) |
| SE (1) | SE441120B (en) |
Cited By (63)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0027751A1 (en) * | 1979-10-22 | 1981-04-29 | Automobiles Peugeot | Elastic mounting, particularly for the suspension of a vehicle engine |
| EP0038062A2 (en) * | 1980-04-14 | 1981-10-21 | Nissan Motor Co., Ltd. | Damper in particular for suspension of an engine |
| EP0042910A2 (en) * | 1980-06-27 | 1982-01-06 | Boge GmbH | Mounting with a single hydraulic damping chamber |
| EP0058408A2 (en) * | 1981-02-17 | 1982-08-25 | Nissan Motor Co., Ltd. | Fluid-filled engine mount device |
| EP0065298A2 (en) * | 1981-05-18 | 1982-11-24 | Nissan Motor Co., Ltd. | Engine mount device |
| EP0068395A2 (en) * | 1981-07-01 | 1983-01-05 | Nissan Motor Co., Ltd. | Vibration damper |
| FR2536143A1 (en) * | 1982-11-13 | 1984-05-18 | Tokai Rubber Ind Ltd | VIBRATION DAMPING STRUCTURE |
| GB2129910A (en) * | 1982-09-09 | 1984-05-23 | Continental Gummi Werke Ag | Hydraulically damped elastomeric mounting |
| GB2132311A (en) * | 1982-12-14 | 1984-07-04 | Boge Gmbh | Hydraulically damped rubber mounting |
| EP0115174A2 (en) * | 1983-01-27 | 1984-08-08 | General Motors Corporation | Hydraulic-elastomeric mount |
| FR2547378A1 (en) * | 1983-06-10 | 1984-12-14 | Toyoda Gosei Kk | |
| EP0132404A2 (en) * | 1983-07-22 | 1985-01-30 | Honda Giken Kogyo Kabushiki Kaisha | Fluid-sealed engine mounting |
| EP0133588A2 (en) * | 1983-08-15 | 1985-02-27 | Bridgestone Corporation | Vibration isolating device and system |
| EP0147242A2 (en) * | 1983-12-28 | 1985-07-03 | Bridgestone Corporation | Vibration isolating devices |
| GB2152182A (en) * | 1983-11-23 | 1985-07-31 | Porsche Ag | Hydraulically damped two-chamber bearing structure |
| US4535976A (en) * | 1980-06-23 | 1985-08-20 | Bridgestone Tire Co., Ltd. | Rubber vibration isolators |
| FR2559864A1 (en) * | 1984-02-21 | 1985-08-23 | Honda Motor Co Ltd | VIBRATION ISOLATOR |
| EP0154828A1 (en) * | 1984-03-01 | 1985-09-18 | Continental Aktiengesellschaft | Hydraulically damped elastic mounting, in particular for the driving engine in motor vehicles |
| EP0156697A1 (en) * | 1984-02-27 | 1985-10-02 | Hutchinson | Modifications to hydraulic antivibration mounts |
| FR2563881A1 (en) * | 1984-05-04 | 1985-11-08 | Boge Gmbh | HYDRAULIC DAMPING RUBBER SUPPORT FOR MOTOR VEHICLES |
| US4568069A (en) * | 1981-08-07 | 1986-02-04 | Automobiles Peugeot | Elastically yieldable mount, in particular for the suspension of a vehicle engine |
| EP0173273A2 (en) * | 1984-08-27 | 1986-03-05 | Bridgestone Corporation | Vibration isolating apparatus |
| EP0174184A2 (en) * | 1984-09-07 | 1986-03-12 | Bridgestone Corporation | Vibration isolating apparatus |
| US4588173A (en) * | 1983-11-23 | 1986-05-13 | General Motors Corporation | Hydraulic-elastomeric mount |
| FR2575253A1 (en) * | 1984-12-24 | 1986-06-27 | Hutchinson | HYDRAULIC ANTIVIBRATORY SUPPORT |
| EP0191703A1 (en) * | 1985-02-15 | 1986-08-20 | Hutchinson | Hydraulic antivibration mounts |
| US4610421A (en) * | 1983-02-04 | 1986-09-09 | Toyota Jidosha Kabushiki Kaisha | Mounting construction for engine-transmission assembly |
| EP0194035A2 (en) * | 1985-02-28 | 1986-09-10 | General Motors Corporation | Hydraulic-elastomeric vehicle engine mount |
| US4611795A (en) * | 1983-01-27 | 1986-09-16 | General Motors Corporation | Hydraulic-elastomeric mount |
| US4630803A (en) * | 1981-09-04 | 1986-12-23 | Daimler-Benz Aktiengesellschaft | Suspension-strut mounting for installation between a shock-absorber strut or spring strut and a vehicle body spring-supported with respect to the axles, in particular of a motor vehicle |
| US4635910A (en) * | 1984-05-03 | 1987-01-13 | Toyoda Gosei Co., Ltd. | Fluid-filled damper device |
| US4641817A (en) * | 1983-04-05 | 1987-02-10 | Dunlop Limited | Vibration absorbing mountings |
| US4664363A (en) * | 1985-10-07 | 1987-05-12 | General Motors Corporation | Hydraulic-elastomeric mount displacement decoupler |
| US4673156A (en) * | 1984-10-16 | 1987-06-16 | Nissan Motor Co., Ltd. | Liquid-filled type vibration damping structure |
| US4676489A (en) * | 1984-01-26 | 1987-06-30 | Metzeler Kautschuk Gmbh | Two chamber engine mount with hydraulic damping |
| US4679777A (en) * | 1985-10-07 | 1987-07-14 | General Motors Corporation | Hydraulic-elastomeric mount displacement decoupler |
| US4682753A (en) * | 1983-11-12 | 1987-07-28 | Dunlop Limited | Vibration absorbing mountings |
| US4697794A (en) * | 1982-12-16 | 1987-10-06 | Boge Gmbh | Rubber mounting with hydraulic damping |
| US4721291A (en) * | 1985-07-05 | 1988-01-26 | Toyota Jidosha Kabushiki Kaisha | Vibration-preventing rubber device |
| US4721288A (en) * | 1984-06-06 | 1988-01-26 | Metzeler Kautschuk Gmbh | Two-chamber engine mount with hydraulic damping |
| US4739979A (en) * | 1985-09-26 | 1988-04-26 | Tokai Rubber Industries, Ltd. | Fluid-filled resilient support structure |
| US4753421A (en) * | 1985-07-05 | 1988-06-28 | Toyota Jidosha Kabushiki Kaisha | Vibration-preventing rubber device |
| US4753422A (en) * | 1986-01-30 | 1988-06-28 | Thorn Richard P | Quiet acting low friction decouplers for fluid filled vibration isolators |
| EP0276673A1 (en) * | 1987-01-21 | 1988-08-03 | ITT Industrie Riunite SpA | Elastic antivibration support with hydraulic damping, especially for a piston engine |
| US4767106A (en) * | 1986-02-25 | 1988-08-30 | Automobiles Peugeot | Hydroelastic support, in particular for a vehicle engine |
| US4767107A (en) * | 1986-01-30 | 1988-08-30 | Automobiles Peugeot | Central suspension hydroelastic mount, in particular for the suspension of a motor-vehicle motor-drive unit |
| US4768760A (en) * | 1986-01-22 | 1988-09-06 | Automobiles Peugeot | Hydro-elastic articulation |
| US4781361A (en) * | 1985-07-05 | 1988-11-01 | Toyota Jidosha Kabushiki Kaisha | Vibration-preventing rubber device |
| US4783063A (en) * | 1987-01-30 | 1988-11-08 | General Motors Corporation | Hydraulic-elastomeric mount displacement decoupler |
| US4793600A (en) * | 1986-03-14 | 1988-12-27 | Bridgestone Corporation | Vibration isolating apparatus |
| GB2209378A (en) * | 1987-09-04 | 1989-05-10 | Standard Products Co | Elastomeric engine mount with hydraulic damping |
| US4856750A (en) * | 1987-04-13 | 1989-08-15 | Automobiles Peugeot | Hydroelastic support, in particular for the suspension of a vehicle engine |
| US4861006A (en) * | 1986-09-16 | 1989-08-29 | Bridgestone Corporation | Anti-vibration apparatus |
| EP0346227A1 (en) * | 1988-06-09 | 1989-12-13 | Hutchinson | Modifications of hydraulic antivibration devices |
| US4895353A (en) * | 1988-06-28 | 1990-01-23 | The Pullman Company | Fluid filled elastomeric damping device |
| EP0400365A2 (en) * | 1989-05-30 | 1990-12-05 | Metzeler Gimetall Ag | Hydraulically damping two-chamber engine mount |
| GB2237355A (en) * | 1989-10-27 | 1991-05-01 | Draftex Ind Ltd | A hydroelastic support |
| US5040774A (en) * | 1990-04-09 | 1991-08-20 | The Pullman Company | Hydraulic damping bushing |
| US5501433A (en) * | 1993-07-06 | 1996-03-26 | Yamashita Rubber Kabushiki Kaisha | Liquid sealing and vibration isolator |
| US5772189A (en) * | 1995-06-15 | 1998-06-30 | Yamashita Rubber Kabuskiki Kaisha | Antivibration rubber device |
| EP0969231A2 (en) * | 1998-06-30 | 2000-01-05 | Draftex Industries Limited | sealing membrane arrangements |
| US7588235B2 (en) * | 2005-10-05 | 2009-09-15 | Tokai Rubber Industries, Ltd. | Fluid filled type vibration-damping device |
| DE102010048259A1 (en) * | 2010-10-12 | 2012-05-10 | Volkswagen Ag | Hydraulically damped bearing i.e. aggregate bearing, for motor car, has intermediate plate for clearing and decoupling high-frequency, small-amplitude vibrations fastened at housing and connected to housing in liquid-tight manner |
Families Citing this family (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5925900B2 (en) * | 1979-11-06 | 1984-06-22 | 東海ゴム工業株式会社 | Anti-vibration support |
| JPS56157625A (en) * | 1980-05-02 | 1981-12-04 | Nissan Motor Co Ltd | Mounting device for engine |
| DE3019337C2 (en) * | 1980-05-21 | 1986-07-31 | Fa. Carl Freudenberg, 6940 Weinheim | Elastic rubber mount |
| DE3027742A1 (en) * | 1980-07-22 | 1982-02-04 | Metzeler Kautschuk GmbH, 8000 München | TWO-CHAMBER ENGINE MOUNT WITH HYDRAULIC DAMPING |
| JPS57118921A (en) * | 1981-01-12 | 1982-07-24 | Nissan Motor Co Ltd | Mounting device of power unit |
| US4489921A (en) * | 1982-10-29 | 1984-12-25 | The Standard Products Company | Resilient engine mount |
| DE3323178C2 (en) * | 1983-06-28 | 1986-11-06 | Metzeler Kautschuk GmbH, 8000 München | Decoupling membrane for a two-chamber engine mount |
| DE3330462C2 (en) * | 1983-08-24 | 1986-11-06 | Fa. Carl Freudenberg, 6940 Weinheim | Hydraulically damped engine mount |
| DE3339054C1 (en) * | 1983-10-28 | 1984-10-18 | Daimler-Benz Ag, 7000 Stuttgart | Elastic bearing with hydraulic damping |
| DE3436534A1 (en) * | 1984-03-01 | 1986-04-10 | Continental Gummi-Werke Ag, 3000 Hannover | Hydraulically damped elastic bearing, especially for the propulsion engine in motor vehicles |
| DE3522482A1 (en) | 1985-06-22 | 1987-01-15 | Freudenberg Carl Fa | HYDRAULIC DAMPING ENGINE MOUNT |
| JPS62288741A (en) * | 1986-06-06 | 1987-12-15 | Tokai Rubber Ind Ltd | Mounting device for power unit |
| DE3621466A1 (en) * | 1986-06-26 | 1988-01-07 | Fraunhofer Ges Forschung | Shock absorber |
| DE3641006A1 (en) * | 1986-12-01 | 1988-06-16 | Continental Gummi Werke Ag | Undamped flexible mount with end stops |
| FR2609766B1 (en) | 1987-01-20 | 1989-05-19 | Peugeot | ELASTIC SUPPORT, IN PARTICULAR FOR THE SUSPENSION OF A VEHICLE ENGINE |
| FR2617930B1 (en) | 1987-07-07 | 1992-07-31 | Peugeot | HYDROELASTIC SUPPORT, IN PARTICULAR FOR PROVIDING THE SUSPENSION OF AN ENGINE IN A VEHICLE |
| JPH06100243B2 (en) * | 1987-08-21 | 1994-12-12 | 東海ゴム工業株式会社 | Fluid-filled mounting device |
| DE3805761A1 (en) * | 1988-02-24 | 1989-09-07 | Daimler Benz Ag | HYDRAULIC DAMPING RUBBER BEARING |
| FR2628496B1 (en) | 1988-03-08 | 1990-12-21 | Peugeot | ELASTIC CONNECTION WITH HYDRAULIC RIGIDIFICATION |
| KR20090129170A (en) * | 2008-06-12 | 2009-12-16 | 평화산업주식회사 | Air damping engine mount |
| FR3087157B1 (en) * | 2018-10-12 | 2022-01-14 | Psa Automobiles Sa | MOTOR VEHICLE SUSPENSION END-OF-STROKE HYDRAULIC STOP |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2387066A (en) * | 1944-03-22 | 1945-10-16 | Edmund J Lada | Mount support |
| DE945899C (en) * | 1952-01-19 | 1956-07-19 | Friedrich Stuebbe | Hollow fluid spring with self-damping, especially for vehicles |
| US3202388A (en) * | 1959-05-05 | 1965-08-24 | Yarrow & Co Ltd | Vibration isolators |
| GB1190943A (en) * | 1966-09-02 | 1970-05-06 | Peddinghaus Carl Ullrich Dr | Improvements relating to Hydraulic Shock Absorbers |
| FR2389801A2 (en) * | 1977-05-05 | 1978-12-01 | Peugeot | Anti-vibration mounting for automobile engine - has internal hydraulic damping to increase stiffness at large amplitudes |
| FR2356847A1 (en) * | 1976-06-30 | 1978-01-27 | Peugeot | Anti-vibration mounting for automobile engine - has internal hydraulic damping to increase stiffness at large amplitudes |
| FR2375501A2 (en) * | 1976-12-21 | 1978-07-21 | Peugeot | Anti-vibration mounting for automobile engine - has internal hydraulic damping to increase stiffness at large amplitudes |
| DE2727244C2 (en) * | 1976-06-30 | 1990-06-21 | Automobiles Peugeot, 75116 Paris | Rubber spring with liquid filling |
| FR2372351A2 (en) * | 1976-11-26 | 1978-06-23 | Peugeot | Anti-vibration mounting for automobile engine - has internal hydraulic damping to increase stiffness at large amplitudes |
| JPS53117704A (en) * | 1977-03-23 | 1978-10-14 | Boge Gmbh | Motor bearing device resilient like rubber |
| DE7712833U1 (en) * | 1977-03-23 | 1977-09-15 | Boge Gmbh, 5208 Eitorf | Liquid-filled, rubber-elastic engine mounts, in particular for motor vehicles |
| DE7819605U1 (en) * | 1978-06-30 | 1978-10-26 | Boge Gmbh, 5208 Eitorf | Two-chamber engine mount |
| IT1110771B (en) * | 1979-02-09 | 1986-01-06 | Gomma Antivibranti Applic | CUSHIONING SUPPORT FOR THE SUSPENSION OF A SWINGING BODY TO A SUPPORT STRUCTURE, IN PARTICULAR FOR THE SUSPENSION OF THE ENGINE TO THE FRAME OF A VEHICLE |
-
1979
- 1979-02-10 DE DE2905090A patent/DE2905090C2/en not_active Expired
- 1979-04-24 JP JP5074779A patent/JPS55107145A/en active Pending
- 1979-04-26 SE SE7903691A patent/SE441120B/en not_active IP Right Cessation
- 1979-07-18 IT IT49798/79A patent/IT1118200B/en active
- 1979-07-30 GB GB7926447A patent/GB2041485B/en not_active Expired
-
1980
- 1980-02-08 FR FR8002814A patent/FR2448673B1/en not_active Expired
Cited By (93)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4720086A (en) * | 1979-10-22 | 1988-01-19 | Automobiles Peugeot | Elastically yieldable unit in particular for the suspension of an engine of a vehicle |
| EP0027751A1 (en) * | 1979-10-22 | 1981-04-29 | Automobiles Peugeot | Elastic mounting, particularly for the suspension of a vehicle engine |
| EP0038062A2 (en) * | 1980-04-14 | 1981-10-21 | Nissan Motor Co., Ltd. | Damper in particular for suspension of an engine |
| EP0038062A3 (en) * | 1980-04-14 | 1982-03-31 | Nissan Motor Company, Limited | Damper in particular for suspension of an engine |
| US4535976A (en) * | 1980-06-23 | 1985-08-20 | Bridgestone Tire Co., Ltd. | Rubber vibration isolators |
| EP0042910A2 (en) * | 1980-06-27 | 1982-01-06 | Boge GmbH | Mounting with a single hydraulic damping chamber |
| EP0042910A3 (en) * | 1980-06-27 | 1982-04-21 | Boge Gmbh | Mounting with a single hydraulic damping chamber |
| EP0058408A3 (en) * | 1981-02-17 | 1983-09-28 | Nissan Motor Company, Limited | Fluid-filled engine mount device |
| EP0058408A2 (en) * | 1981-02-17 | 1982-08-25 | Nissan Motor Co., Ltd. | Fluid-filled engine mount device |
| EP0065298A3 (en) * | 1981-05-18 | 1983-09-28 | Nissan Motor Co., Ltd. | Engine mount device |
| US4657219A (en) * | 1981-05-18 | 1987-04-14 | Nissan Motor Co., Ltd. | Fluid-filled engine mount device |
| EP0065298A2 (en) * | 1981-05-18 | 1982-11-24 | Nissan Motor Co., Ltd. | Engine mount device |
| US4483521A (en) * | 1981-07-01 | 1984-11-20 | Nissan Motor Company, Limited | Rubber and fluid type vibration damper |
| EP0068395A3 (en) * | 1981-07-01 | 1983-11-09 | Nissan Motor Company, Limited | Vibration damper |
| EP0068395A2 (en) * | 1981-07-01 | 1983-01-05 | Nissan Motor Co., Ltd. | Vibration damper |
| US4568069A (en) * | 1981-08-07 | 1986-02-04 | Automobiles Peugeot | Elastically yieldable mount, in particular for the suspension of a vehicle engine |
| US4630803A (en) * | 1981-09-04 | 1986-12-23 | Daimler-Benz Aktiengesellschaft | Suspension-strut mounting for installation between a shock-absorber strut or spring strut and a vehicle body spring-supported with respect to the axles, in particular of a motor vehicle |
| GB2129910A (en) * | 1982-09-09 | 1984-05-23 | Continental Gummi Werke Ag | Hydraulically damped elastomeric mounting |
| FR2536143A1 (en) * | 1982-11-13 | 1984-05-18 | Tokai Rubber Ind Ltd | VIBRATION DAMPING STRUCTURE |
| US4660813A (en) * | 1982-12-14 | 1987-04-28 | Boge Gmbh | Rubber mounting with hydraulic damping, particularly for mounting vehicle engines |
| GB2132311A (en) * | 1982-12-14 | 1984-07-04 | Boge Gmbh | Hydraulically damped rubber mounting |
| US4697794A (en) * | 1982-12-16 | 1987-10-06 | Boge Gmbh | Rubber mounting with hydraulic damping |
| EP0115174A2 (en) * | 1983-01-27 | 1984-08-08 | General Motors Corporation | Hydraulic-elastomeric mount |
| US4611795A (en) * | 1983-01-27 | 1986-09-16 | General Motors Corporation | Hydraulic-elastomeric mount |
| EP0115174A3 (en) * | 1983-01-27 | 1987-02-04 | General Motors Corporation | Hydraulic-elastomeric mount |
| US4610421A (en) * | 1983-02-04 | 1986-09-09 | Toyota Jidosha Kabushiki Kaisha | Mounting construction for engine-transmission assembly |
| US4641817A (en) * | 1983-04-05 | 1987-02-10 | Dunlop Limited | Vibration absorbing mountings |
| FR2547378A1 (en) * | 1983-06-10 | 1984-12-14 | Toyoda Gosei Kk | |
| EP0132404A3 (en) * | 1983-07-22 | 1985-07-31 | Honda Giken Kogyo Kabushiki Kaisha | Fluid-sealed engine mounting |
| EP0132404A2 (en) * | 1983-07-22 | 1985-01-30 | Honda Giken Kogyo Kabushiki Kaisha | Fluid-sealed engine mounting |
| EP0133588A2 (en) * | 1983-08-15 | 1985-02-27 | Bridgestone Corporation | Vibration isolating device and system |
| EP0133588A3 (en) * | 1983-08-15 | 1986-04-09 | Bridgestone Corporation | Vibration isolating device and system |
| US4682753A (en) * | 1983-11-12 | 1987-07-28 | Dunlop Limited | Vibration absorbing mountings |
| GB2152182A (en) * | 1983-11-23 | 1985-07-31 | Porsche Ag | Hydraulically damped two-chamber bearing structure |
| US4588173A (en) * | 1983-11-23 | 1986-05-13 | General Motors Corporation | Hydraulic-elastomeric mount |
| EP0147242A3 (en) * | 1983-12-28 | 1986-05-07 | Bridgestone Corporation | Vibration isolating devices |
| US4630808A (en) * | 1983-12-28 | 1986-12-23 | Bridgestone Corporation | Vibration isolating devices |
| EP0147242A2 (en) * | 1983-12-28 | 1985-07-03 | Bridgestone Corporation | Vibration isolating devices |
| US4676489A (en) * | 1984-01-26 | 1987-06-30 | Metzeler Kautschuk Gmbh | Two chamber engine mount with hydraulic damping |
| FR2559864A1 (en) * | 1984-02-21 | 1985-08-23 | Honda Motor Co Ltd | VIBRATION ISOLATOR |
| EP0156697A1 (en) * | 1984-02-27 | 1985-10-02 | Hutchinson | Modifications to hydraulic antivibration mounts |
| US4621795A (en) * | 1984-03-01 | 1986-11-11 | Continental Gummi-Werke Aktiengesellschaft | Hydraulically damped resilient mounting |
| EP0154828A1 (en) * | 1984-03-01 | 1985-09-18 | Continental Aktiengesellschaft | Hydraulically damped elastic mounting, in particular for the driving engine in motor vehicles |
| US4635910A (en) * | 1984-05-03 | 1987-01-13 | Toyoda Gosei Co., Ltd. | Fluid-filled damper device |
| US4645189A (en) * | 1984-05-04 | 1987-02-24 | Boge Gmbh | Hydraulic damping rubber engine mount |
| FR2563881A1 (en) * | 1984-05-04 | 1985-11-08 | Boge Gmbh | HYDRAULIC DAMPING RUBBER SUPPORT FOR MOTOR VEHICLES |
| US4721288A (en) * | 1984-06-06 | 1988-01-26 | Metzeler Kautschuk Gmbh | Two-chamber engine mount with hydraulic damping |
| EP0173273A3 (en) * | 1984-08-27 | 1988-03-30 | Bridgestone Corporation | Vibration isolating apparatus |
| US4660812A (en) * | 1984-08-27 | 1987-04-28 | Bridgestone Corporation | Vibration isolating apparatus |
| EP0173273A2 (en) * | 1984-08-27 | 1986-03-05 | Bridgestone Corporation | Vibration isolating apparatus |
| EP0174184A3 (en) * | 1984-09-07 | 1986-05-14 | Bridgestone Corporation | Vibration isolating apparatus |
| EP0174184A2 (en) * | 1984-09-07 | 1986-03-12 | Bridgestone Corporation | Vibration isolating apparatus |
| US4802658A (en) * | 1984-09-07 | 1989-02-07 | Bridgestone Corporation | Vibration isolating apparatus |
| US4673156A (en) * | 1984-10-16 | 1987-06-16 | Nissan Motor Co., Ltd. | Liquid-filled type vibration damping structure |
| US4739978A (en) * | 1984-12-24 | 1988-04-26 | Hutchinson | Hydraulic antivibration support |
| FR2575253A1 (en) * | 1984-12-24 | 1986-06-27 | Hutchinson | HYDRAULIC ANTIVIBRATORY SUPPORT |
| WO1986003813A1 (en) * | 1984-12-24 | 1986-07-03 | Hutchinson | Hydraulic anti-vibration support |
| FR2577641A1 (en) * | 1985-02-15 | 1986-08-22 | Hutchinson | IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS |
| EP0191703A1 (en) * | 1985-02-15 | 1986-08-20 | Hutchinson | Hydraulic antivibration mounts |
| EP0194035A2 (en) * | 1985-02-28 | 1986-09-10 | General Motors Corporation | Hydraulic-elastomeric vehicle engine mount |
| EP0194035A3 (en) * | 1985-02-28 | 1989-02-08 | General Motors Corporation | Hydraulic-elastomeric vehicle engine mount |
| US4721291A (en) * | 1985-07-05 | 1988-01-26 | Toyota Jidosha Kabushiki Kaisha | Vibration-preventing rubber device |
| US4753421A (en) * | 1985-07-05 | 1988-06-28 | Toyota Jidosha Kabushiki Kaisha | Vibration-preventing rubber device |
| US4781361A (en) * | 1985-07-05 | 1988-11-01 | Toyota Jidosha Kabushiki Kaisha | Vibration-preventing rubber device |
| US4739979A (en) * | 1985-09-26 | 1988-04-26 | Tokai Rubber Industries, Ltd. | Fluid-filled resilient support structure |
| US4679777A (en) * | 1985-10-07 | 1987-07-14 | General Motors Corporation | Hydraulic-elastomeric mount displacement decoupler |
| US4664363A (en) * | 1985-10-07 | 1987-05-12 | General Motors Corporation | Hydraulic-elastomeric mount displacement decoupler |
| US4768760A (en) * | 1986-01-22 | 1988-09-06 | Automobiles Peugeot | Hydro-elastic articulation |
| US4753422A (en) * | 1986-01-30 | 1988-06-28 | Thorn Richard P | Quiet acting low friction decouplers for fluid filled vibration isolators |
| US4767107A (en) * | 1986-01-30 | 1988-08-30 | Automobiles Peugeot | Central suspension hydroelastic mount, in particular for the suspension of a motor-vehicle motor-drive unit |
| US4767106A (en) * | 1986-02-25 | 1988-08-30 | Automobiles Peugeot | Hydroelastic support, in particular for a vehicle engine |
| US4793600A (en) * | 1986-03-14 | 1988-12-27 | Bridgestone Corporation | Vibration isolating apparatus |
| US4973031A (en) * | 1986-09-16 | 1990-11-27 | Bridgestone Corporation | Anti-vibration apparatus |
| US4861006A (en) * | 1986-09-16 | 1989-08-29 | Bridgestone Corporation | Anti-vibration apparatus |
| EP0276673A1 (en) * | 1987-01-21 | 1988-08-03 | ITT Industrie Riunite SpA | Elastic antivibration support with hydraulic damping, especially for a piston engine |
| US4783063A (en) * | 1987-01-30 | 1988-11-08 | General Motors Corporation | Hydraulic-elastomeric mount displacement decoupler |
| US4856750A (en) * | 1987-04-13 | 1989-08-15 | Automobiles Peugeot | Hydroelastic support, in particular for the suspension of a vehicle engine |
| US4915365A (en) * | 1987-09-04 | 1990-04-10 | The Standard Products Company | Elastomeric engine mount with hydraulic damping |
| GB2209378B (en) * | 1987-09-04 | 1992-02-12 | Standard Products Co | Elastomeric engine mount with hydraulic damping |
| GB2209378A (en) * | 1987-09-04 | 1989-05-10 | Standard Products Co | Elastomeric engine mount with hydraulic damping |
| FR2632696A1 (en) * | 1988-06-09 | 1989-12-15 | Hutchinson | IMPROVEMENTS IN HYDRAULIC ANTI-VIBRATION DEVICES |
| EP0346227A1 (en) * | 1988-06-09 | 1989-12-13 | Hutchinson | Modifications of hydraulic antivibration devices |
| US4895353A (en) * | 1988-06-28 | 1990-01-23 | The Pullman Company | Fluid filled elastomeric damping device |
| EP0400365A3 (en) * | 1989-05-30 | 1991-01-23 | Metzeler Gimetall Ag | Hydraulically damping two-chamber engine mount |
| EP0400365A2 (en) * | 1989-05-30 | 1990-12-05 | Metzeler Gimetall Ag | Hydraulically damping two-chamber engine mount |
| GB2237355A (en) * | 1989-10-27 | 1991-05-01 | Draftex Ind Ltd | A hydroelastic support |
| US5040774A (en) * | 1990-04-09 | 1991-08-20 | The Pullman Company | Hydraulic damping bushing |
| US5501433A (en) * | 1993-07-06 | 1996-03-26 | Yamashita Rubber Kabushiki Kaisha | Liquid sealing and vibration isolator |
| US5967500A (en) * | 1994-03-01 | 1999-10-19 | Yamashita Rubber Kabushiki Kaisha | Antivibration rubber device |
| US5772189A (en) * | 1995-06-15 | 1998-06-30 | Yamashita Rubber Kabuskiki Kaisha | Antivibration rubber device |
| EP0969231A2 (en) * | 1998-06-30 | 2000-01-05 | Draftex Industries Limited | sealing membrane arrangements |
| US7588235B2 (en) * | 2005-10-05 | 2009-09-15 | Tokai Rubber Industries, Ltd. | Fluid filled type vibration-damping device |
| DE102010048259A1 (en) * | 2010-10-12 | 2012-05-10 | Volkswagen Ag | Hydraulically damped bearing i.e. aggregate bearing, for motor car, has intermediate plate for clearing and decoupling high-frequency, small-amplitude vibrations fastened at housing and connected to housing in liquid-tight manner |
Also Published As
| Publication number | Publication date |
|---|---|
| IT7949798A0 (en) | 1979-07-18 |
| SE441120B (en) | 1985-09-09 |
| SE7903691L (en) | 1980-08-11 |
| DE2905090A1 (en) | 1980-08-14 |
| FR2448673A1 (en) | 1980-09-05 |
| IT1118200B (en) | 1986-02-24 |
| JPS55107145A (en) | 1980-08-16 |
| DE2905090C2 (en) | 1987-11-12 |
| GB2041485B (en) | 1983-09-01 |
| FR2448673B1 (en) | 1985-11-22 |
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| PG | Patent granted |