WO2003058092A1 - Support a amortissement pneumatique triaxial - Google Patents

Support a amortissement pneumatique triaxial Download PDF

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Publication number
WO2003058092A1
WO2003058092A1 PCT/EP2003/000186 EP0300186W WO03058092A1 WO 2003058092 A1 WO2003058092 A1 WO 2003058092A1 EP 0300186 W EP0300186 W EP 0300186W WO 03058092 A1 WO03058092 A1 WO 03058092A1
Authority
WO
WIPO (PCT)
Prior art keywords
chamber
spring bearing
bearing according
chamber system
housing
Prior art date
Application number
PCT/EP2003/000186
Other languages
German (de)
English (en)
Inventor
Wolf Franz-Josef
Original Assignee
Woco Franz-Josef Wolf & Co. Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Woco Franz-Josef Wolf & Co. Gmbh filed Critical Woco Franz-Josef Wolf & Co. Gmbh
Priority to EP03701502A priority Critical patent/EP1463896A1/fr
Publication of WO2003058092A1 publication Critical patent/WO2003058092A1/fr

Links

Classifications

    • 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
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/1418—Units of the bushing type, i.e. loaded predominantly radially characterised by the location or shape of the equilibration chamber
    • 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
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/16—Units of the bushing type, i.e. loaded predominantly radially specially adapted for receiving axial loads

Definitions

  • the invention relates to a three-axis damped spring bearing for filtering vibrations, which has at least one chamber system in a housing, the chamber system having at least one essentially flexible, dynamically acting working chamber, at least one compensating chamber and at least one throttle device in operative connection with at least one compensating chamber and at least one working chamber comprises, this chamber system is provided at least in regions by an elastomer body, and when vibrations are fed in via an exciter, a volume flow of a fluid arranged within this chamber system is induced.
  • vibration generating devices such as Washing machines or automobiles where insulation, i.e. Decoupling that seeks sources of vibration from the surrounding housing.
  • insulation i.e. Decoupling that seeks sources of vibration from the surrounding housing.
  • elastomeric bearings are used, via which e.g. in the case of the automotive industry, the engines are attached to supporting parts of the body.
  • some of these bearings are additionally combined with fluid damping. The principle of action is as follows:
  • Two chambers filled with fluid are connected to one another via a throttle feed line, vibrations being supplied to at least one of the chambers via an elastomer body in the form of pressure fluctuations. This leads to a pressure gradient between the two chambers, which results in a volume flow of the fluid via the throttle feed line, which is responsible for damping the vibrations.
  • Hydraulic fluids are predominantly used as fluid in these chamber systems, whereby some of the suitable liquids have the disadvantage, among other things, that they have to be treated as special waste when they are disposed of and correspondingly high safety requirements are imposed on them Manufacture of hydraulically damped elastomer bearings exist. In addition, the damping effect diminishes considerably when air gets into the hydraulic fluid during filling. For the reasons mentioned above, manufacturers are increasingly moving to replacing liquids with gases.
  • DE 44 02 543 AI discloses a fluid-damped elastomer spring for engine mounting, which has two chambers in one housing, a working and an equalizing chamber, which are connected to one another by a slack that is movably arranged in the housing.
  • the slack provides a throttle feed line in the form of a passage channel or a passage opening, wherein a flow control valve can also be arranged in the throttle feed line.
  • the damping effect of the elastomer spring can alternatively be varied in that the slack is elastically suspended in the working chamber.
  • an air-damped elastomer body in the form of a rubber bearing for attachment to a vibration generator is known.
  • the elastomer body arranged between rings has an air chamber in its interior, which is divided into an upper and a lower air chamber by a piston-shaped rubber body.
  • an opening for connecting the upper and the lower air chamber can be provided in the rubber body, which causes damping due to a throttling effect.
  • the damping properties can also be influenced via one or more pressure membranes which are connected to at least one of the air chambers.
  • DE 41 16 706 AI discloses a fluid-damped elastomeric bearing for reducing vibrations in motor vehicle engines, in which an elastic support member is arranged between two sleeves, an inner and an outer sleeve, the outer sleeve forming a housing, in such a way that two Fluid chambers in the form of a main chamber and a supplementary chamber, which are connected to one another, are formed.
  • the connection is provided via a nozzle device, which causes damping under load due to the fluid conveyance.
  • DE 695 16 459 T2 also shows a vibration damping device, for example for installation in a vehicle between the engine and vehicle chassis, which achieves a damping effect essentially through the use of fluids separated by diaphragms.
  • An elastomer body encompassed in some areas by a housing encloses, in addition to a main fluid chamber, two auxiliary fluid chambers which are connected to one another via throttle passages of different dimensions.
  • the main and auxiliary fluid chambers can couple via the diaphragms to air chambers which are open to the atmosphere, closed or can be opened or closed via a control in order to implement an air spring. This and the different dimensions of the throttle passages filter out defined frequency intervals of the vibrations.
  • a disadvantage of the prior art described above is that a targeted adjustment of the spring constants of the spring bearings is made more difficult and complicated by the fact that two chambers of a chamber system are designed to be elastic, so that when pressure builds up in one of the two chambers, this deforms additionally, which in turn changes affects the pressure.
  • the known spring bearings cannot be individually adapted for all three spatial directions of the respective load after installation.
  • the object of the present invention is therefore to further develop the generic three-axis damped spring bearing in such a way that the disadvantages of the prior art are overcome.
  • a three-axle damped spring bearing is to be supplied, which allows the spring forces to be adjusted at any time without problems to adapt to occurring loads.
  • Vibrations can be fed into the at least one working chamber, and the at least one
  • Compensation chamber is an essentially rigid, statically acting chamber.
  • a spring bearing according to the invention is characterized by a multiplicity of chamber systems, preferably at least two chamber systems communicating with one another in such a way that the fluid can flow from one chamber system into another chamber system via a connection. It is also proposed according to the invention that at least two chamber systems work essentially parallel to one another, preferably a first chamber system essentially parallel to a second chamber system, a third chamber system essentially parallel to a fourth chamber system and the first and second chamber systems essentially perpendicular to the third and fourth chamber system work.
  • a spring bearing according to the invention is also characterized in that at least three chamber systems are provided, with at least one chamber system providing filtering of vibrations in each of the three axes of the spring bearing.
  • a fifth chamber system filters vibrations substantially perpendicular to the first, second, third and / or fourth chamber system.
  • a sixth compensation chamber is arranged essentially peripherally around a sixth working chamber and / or in at least one seventh chamber system a seventh working chamber is arranged essentially peripherally around a seventh compensation chamber.
  • the fluid be gaseous, preferably include air and / or nitrogen.
  • a spring bearing according to the invention is characterized in that at least one chamber system, preferably each chamber system, can be pressurized via a separate and / or common pressure supply line.
  • the pressure supply line is connected to a control and / or regulating unit for pressurization.
  • control and / or regulating unit is connected to a sensor, in particular for detecting the engine rotational frequency and / or the vehicle speed. It is further proposed that the housing can be closed at least on one side by means of a cover, in particular in the form of a cover plate, by means of screws, clamps, clips and / or the like and / or by means of caulking.
  • the elastomer body have a hub for receiving an axle which can be coupled to a motor, in particular in the form of a hollow axle, four webs which extend at an essentially equidistant distance concentrically around the hub, in particular in the form of trapezoidal spring bars, and two walls , in particular in the form of wall spring elements, for connecting the webs in the region of the opening of the hub, and four chamber segments are arranged between the webs and the housing.
  • the hollow axis delimits a compensation chamber after closure with a lid and coupling to the motor, a working chamber between the lid, the walls and the cover of the housing delimits and at least one throttle device runs through the lid.
  • the invention is further characterized in that the side surfaces of the webs expand from the hub to the housing, and each wall has four trapezoidal segments.
  • a spring bearing according to the invention is characterized in that the webs each engage the two chamber segments, preferably in the form of a groove, at their end facing away from the hub, preferably in the form of a dovetail guide.
  • the elastomer body has at least one reinforcing element, preferably in the form of a tubular sleeve inside the hub and / or a rigid dovetail guide at the free end of each web.
  • each reinforcing element is attached at least in regions in and / or on the elastomer body, preferably by vulcanization.
  • a sealing element preferably in the form of a sealing web, is attached to the dovetail guide, in particular by vulcanization, at least in some areas.
  • a seal is arranged in the periphery of at least one wall spring element at least in regions, preferably all around.
  • the housing and / or the cover has or have a groove for receiving the seal.
  • a spring bearing according to the invention is also characterized in that the axle, the cover, the chamber segments, the housing, the reinforcing elements and / or the cover are each made of a metal and / or a rigid plastic.
  • a spring bearing according to the invention can be used as an engine mount, gearbox mount and / or pendulum support in the engine compartment of a motor vehicle, as an axle mount and / or as a washing machine mount.
  • the invention is therefore based on the knowledge that a rigid design of the compensation chamber leads to a more precise setting of the spring constants, since there is no volume work of the air on the walls of the compensation chamber to be taken into account.
  • the best possible structure-borne noise insulation is achieved by the spring bearing, since it is active in all three spatial directions and does not work with the internal friction of the elastomer, as is the case with pure elastomer bearings.
  • the damping behavior of the bearing can be optimally matched to the load or the vibrations to be filtered at any time by integrating a externally accessible drain feed device by means of individual pressurization of individual or all chamber systems.
  • Another advantage is the simple plug-in system with which the individual components of the spring bearing can be assembled without connecting the elastomer to its metallic support in a force-locking manner by means of a vulcanization process. This ensures problem-free recycling that serves to conserve raw materials.
  • Figure 1 is an exploded perspective view of a spring bearing according to the invention, obliquely from above;
  • FIG. 2 shows a cross-sectional view through the spring bearing of FIG. 1 in operative connection with a motor, along the section line A - A of FIG. 1;
  • FIG. 3 shows a partial cross-sectional view through the spring bearing of FIGS. 1 and 2 along the section line BB of FIG. 1.
  • a fluid-damped elastomeric spring bearing 1 comprises a substantially dimensionally stable housing 2, for example made of a metal, with a front opening 3, a rear opening 5 running through a rear wall 4 and a flange 6 on its lower one End for fastening in particular to a carrier of a body (not shown) of a motor vehicle.
  • the wall 7 of the housing 2 is provided, for example, with six threaded bores 8 equidistant from one another in order to fasten a cover plate 9 for covering the front opening 3 by means of screws 10, the cover plate 9 also being fastened to the housing 2 by means of caulking can.
  • the wall 7 encloses an essentially cuboid cavity 11, which serves to receive an elastomer body 12, together with chamber segments 13 arranged laterally on it, a hollow axis 14 and a cover 15.
  • the hollow axle 14 is in particular part of an engine mount 16 which is individually adapted to a vehicle type and which is screwed to an engine block 17 (see also FIG. 2).
  • the elastomer body 12 has a centrally arranged hub 20, on the periphery of which four spring webs 21 extending radially outwards are formed at a distance of 90 degrees each.
  • the side faces 22 the spring bars 21 are trapezoidal in shape, the side faces 22 widening toward the longitudinal sides 23 of the spring bars 21.
  • the spring bars 21 are each connected to one another via two wall spring elements 24 and each have a dovetail guide 25 at their peripheral ends, for example made of metal or glass fiber reinforced plastic, on which a sealing bar 26 is also vulcanized from an elastomeric material (see also FIG. 3).
  • the dovetail guide 25 is in turn connected to the elastomer body 12 by a vulcanization process.
  • the sealing webs 26 provide sealing contact surfaces for the four chamber segments 13. These chamber segments 13 are made of a dimensionally stable material, such as die-cast aluminum, and are trough-shaped, and they have narrow support webs 28 in their trough-shaped depressions, which in the embodiment shown are flush with the side edges 29 of the chamber segments 13 and are small in height Have recess 30 in the middle.
  • the motor mount 16 and the cover 15 are also made of a dimensionally stable material like the chamber segments 13.
  • Throttling devices 31 in the form of e.g. Throttle valves or narrowed bushings, arranged, which allow a compressible fluid to pass through.
  • a throttle device 31 equivalent to the throttle devices 31 present in the chamber segments 13 is arranged in the cover 15.
  • the elastomer body 12 can be inserted into the dimensionally stable housing 2 through the front opening 3 after the chamber segments 13 have been placed on the elastomer body 12, and can be kept there by attaching and screwing the cover plate 9 in the housing 2.
  • the hollow shaft 14 of the motor mount 16 can then be inserted into the hub 20 of the elastomer body 12 with the cover 15 pressed into its front end.
  • the hollow axle 14 has a stop 32 and a motor mounting flange 33, via which a vibration exciter, not shown in FIG. 1, such as an engine block 17 (see FIG. 2), can be brought into engagement.
  • a vibration exciter not shown in FIG. 1, such as an engine block 17 (see FIG. 2)
  • the motor mount 16 is coupled to the motor block 17 via threaded bolts 34 via the motor mount flange 33.
  • four so-called dynamic chambers 35 are formed, in which at least one wall area is formed by an essentially flexible, elastic wall element, such as e.g. the side surfaces 22 or the hub 20 of the elastomer body 12 is formed (see Figure 3).
  • These four dynamic chambers 35 are each arranged radially offset by 90 degrees around the hub 20.
  • a fifth dynamic chamber 36 forms when the elastomer body 12 is installed in the dimensionally stable housing 2, when the hollow axis 14 closed by the cover 15 lies flush against the hub 20, the stop 32 defining the insertion depth.
  • This fifth dynamic chamber 36 is enclosed by the side surfaces 22 of the elastomer body 12, the cover 15 and the cover plate 9, the cover plate 9 being undercut centrally.
  • Fitting the chamber segments 13 into the dimensionally stable housing 2 also leads to the formation of four static chambers 37, in that the wall 7 of the housing 2 closes the trough-shaped depressions 27 of the chamber segments 13 towards the housing side (see FIG. 3).
  • These static chambers 37 have an inflexible nature due to the selected materials, so they are also essentially dimensionally stable.
  • the chamber segments 13 are thereby sealed off from one another by means of the sealing webs 26 arranged on the dovetail guide 25 and by means of a seal 39 formed all round on the wall spring elements 24 of the elastomer body 12.
  • the cover plate 9 and the rear wall 4 of the housing 2 have a sealing groove 40 for receiving the seal 39.
  • a fifth static chamber 38 is provided by the hollow shaft 14 which is brought into contact with the hub 20 and closed by the cover 15.
  • Each dynamic chamber 35, 36 is connected to a static chamber 37, 38 via a throttle device 31.
  • the diagonally running spring bars 21 separate the four dynamic chambers 35 from one another, which are connected to the first four static chambers 37 via the throttle devices 31 in the chamber segments 13.
  • the elastomer body 12 is on the to Spring bars 21 arranged dovetail guides 25 anchored to the chamber segments 13.
  • two chamber segments 13 each form, after installation in the housing 2, a negatively designed groove which accommodates the dovetail guide 25.
  • the static chambers 37, 38 remain volume-preserving, in contrast to the dynamic chambers 35, 36.
  • the cover plate 9 serves as an impact stop for vibration limitation on the end face, that is to say in the axial direction of the hub 20, the stop via a bulge which is pronounced at the front end of the hub 20 41 takes place.
  • the inside of the hub 20 is provided with a reinforcing element in the form of a tubular sleeve 42 in order to prevent excessive breathing, ie deformation of the elastomer walls in the area of the hub 20, when vibrations are fed in.
  • the tubular sleeve 42 is vulcanized into the hub 20 and then calibrated to the nominal size.
  • the spring bearing 1 according to the invention exhibits double-acting damping in the radial direction with respect to the hub 20 by two chamber systems connected at the same time, each consisting of a dynamic chamber 35 and a static chamber 37.
  • the rear opening 5 present in the rear wall 4 of the housing 2 is dimensioned such that the stop segments 43 located on the hub 20 prevent contact between the hollow axis 14 of the motor mount 16 and the housing 2 in the event of a strong vibration-related radial deflection of the hollow axis 14.
  • the elastomeric spring bearing 1 according to the invention can be supported with compressed air in order to be able to absorb a larger static load.
  • the pressure can be applied via one or more devices (not shown) which are arranged on or in the wall 7 of the housing 2 or the cover plate 9.
  • these devices enable specific influencing and individual adjustment of the damping characteristics for different frequencies, namely by modifying the individual spring constants of the spring bearing 1.
  • the spring constants can be adjusted at any time, even after a vehicle has been delivered from the factory , e.g. for regular maintenance work in motor vehicle companies or the like.
  • a pressure application of approximately 50 kPa (0.5 bar) to a maximum of 250 kPa (2.5 bar) is preferably provided, the spring bearing 1 according to the invention being able to absorb a load of 750 N from 150 kPa (1.5 bar).
  • individual chamber systems can be short-circuited with one another, so that the fluid present in the chamber systems between the short-circuited chamber systems can flow back and forth, whereby communication between the chamber systems is achieved.
  • Screws 42 tube sleeve

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Abstract

L'invention concerne un support à amortissement triaxial (1) destiné à la filtration de vibrations. Ce support comprend un boîtier (2) comportant au moins un système de chambres (31, 35, 36, 37, 38), ce système comprenant au moins une chambre de travail (35, 36) sensiblement flexible à action dynamique, une chambre d'équilibrage (37, 38) et au moins un dispositif d'étranglement (31) relié fonctionnellement à au moins une chambre d'équilibrage (37, 38) et à au moins une chambre de travail (35, 36). Ledit système de chambres (31, 35, 36, 37, 38) est alimenté, au moins localement, par un corps en élastomère (12). Par ailleurs, un débit volumétrique d'un fluide situé à l'intérieur de ce système de chambres est induit lors de l'arrivée de vibrations par l'intermédiaire d'un élément d'excitation (14). Selon l'invention, des vibrations peuvent être acheminées dans les chambres de travail et les chambres d'équilibrage (37, 38) se présentent sous la forme de chambres sensiblement rigides à action statique.
PCT/EP2003/000186 2002-01-10 2003-01-10 Support a amortissement pneumatique triaxial WO2003058092A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP03701502A EP1463896A1 (fr) 2002-01-10 2003-01-10 Support a amortissement pneumatique triaxial

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10200764A DE10200764A1 (de) 2002-01-10 2002-01-10 Dreiachsgedämpftes Luftfederlager
DE10200764.0 2002-01-10

Publications (1)

Publication Number Publication Date
WO2003058092A1 true WO2003058092A1 (fr) 2003-07-17

Family

ID=7711869

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2003/000186 WO2003058092A1 (fr) 2002-01-10 2003-01-10 Support a amortissement pneumatique triaxial

Country Status (3)

Country Link
EP (1) EP1463896A1 (fr)
DE (1) DE10200764A1 (fr)
WO (1) WO2003058092A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007122192A1 (fr) * 2006-04-21 2007-11-01 Trelleborg Automotive Technical Centre Gmbh Coussinet à amortissement pneumatique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007015239B4 (de) 2007-03-29 2012-03-29 Trelleborg Automotive Germany Gmbh Elastische Lagerbuchse

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3888449A (en) * 1973-01-16 1975-06-10 Elliott Brothers London Ltd Anti-vibration mountings
DE3139915A1 (de) * 1980-10-09 1982-07-01 The Toyo Rubber Industry Co., Ltd., Osaka Luftgedaempftes gummilager
US4458888A (en) * 1981-02-10 1984-07-10 Woco Franz-Josef Wolf & Co. Dampening device
DE3618767A1 (de) * 1986-06-04 1987-12-10 Audi Ag Motorlager mit hydraulischer daempfung
EP0442764A1 (fr) * 1990-02-15 1991-08-21 Automobiles Peugeot Articulation hydroélastique à double effet à armatures concentriques
US5172893A (en) * 1990-03-16 1992-12-22 Hutchison Hydraulic antivibratory sleeves
EP0651176A1 (fr) * 1993-11-02 1995-05-03 Metzeler Gimetall Ag Support amortit hydrauliquement
JPH1194011A (ja) * 1997-09-18 1999-04-09 Sumitomo Metal Ind Ltd 液体封入マウント及びそれを用いた鉄道車両用軸箱支持装置
EP1113187A2 (fr) * 1999-12-28 2001-07-04 Yamashita Rubber Kabushiki Kaisha Dispositif anti-vibratoire renfermant du liquide
EP1160483A2 (fr) * 2000-05-30 2001-12-05 Firma Carl Freudenberg Support hydraulique
JP2001336567A (ja) * 2000-05-29 2001-12-07 Bridgestone Corp 防振装置

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2512727C2 (de) * 1975-03-22 1982-05-06 Continental Gummi-Werke Ag, 3000 Hannover Elastisches Motorlager mit Luftkissen
DE2652501A1 (de) * 1976-11-18 1978-05-24 Phoenix Gummiwerke Ag Elastisches lager
GB8616572D0 (en) * 1986-07-08 1986-08-13 Btr Plc Vibration absorbing mountings
DE3805763A1 (de) * 1988-02-24 1989-09-07 Daimler Benz Ag Hydraulisch daempfendes gummilager
JPH039137A (ja) * 1989-06-06 1991-01-17 Tokai Rubber Ind Ltd 流体封入式筒型マウント装置
JP2583145B2 (ja) * 1990-05-22 1997-02-19 丸五ゴム工業株式会社 流体封入型防振装置
DE4117128A1 (de) * 1991-05-25 1992-11-26 Daimler Benz Ag Hydraulisch daempfendes lager
DE4402543A1 (de) * 1994-01-28 1995-08-03 Wolf Woco & Co Franz J Fluidgedämpfte Elastomerfeder
DE69516459T2 (de) * 1994-07-01 2000-09-21 Bridgestone Corp Vorrichtung zur Schwingungsisolierung
GB9913761D0 (en) * 1999-06-14 1999-08-11 Avon Vibration Man Syst Ltd Hydraulically damped mounting device

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3888449A (en) * 1973-01-16 1975-06-10 Elliott Brothers London Ltd Anti-vibration mountings
DE3139915A1 (de) * 1980-10-09 1982-07-01 The Toyo Rubber Industry Co., Ltd., Osaka Luftgedaempftes gummilager
US4458888A (en) * 1981-02-10 1984-07-10 Woco Franz-Josef Wolf & Co. Dampening device
DE3618767A1 (de) * 1986-06-04 1987-12-10 Audi Ag Motorlager mit hydraulischer daempfung
EP0442764A1 (fr) * 1990-02-15 1991-08-21 Automobiles Peugeot Articulation hydroélastique à double effet à armatures concentriques
US5172893A (en) * 1990-03-16 1992-12-22 Hutchison Hydraulic antivibratory sleeves
EP0651176A1 (fr) * 1993-11-02 1995-05-03 Metzeler Gimetall Ag Support amortit hydrauliquement
JPH1194011A (ja) * 1997-09-18 1999-04-09 Sumitomo Metal Ind Ltd 液体封入マウント及びそれを用いた鉄道車両用軸箱支持装置
EP1113187A2 (fr) * 1999-12-28 2001-07-04 Yamashita Rubber Kabushiki Kaisha Dispositif anti-vibratoire renfermant du liquide
JP2001336567A (ja) * 2000-05-29 2001-12-07 Bridgestone Corp 防振装置
EP1160483A2 (fr) * 2000-05-30 2001-12-05 Firma Carl Freudenberg Support hydraulique

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1999, no. 09 30 July 1999 (1999-07-30) *
PATENT ABSTRACTS OF JAPAN vol. 2002, no. 04 4 August 2002 (2002-08-04) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007122192A1 (fr) * 2006-04-21 2007-11-01 Trelleborg Automotive Technical Centre Gmbh Coussinet à amortissement pneumatique

Also Published As

Publication number Publication date
EP1463896A1 (fr) 2004-10-06
DE10200764A1 (de) 2003-08-07

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