US20120205845A1 - Hydraulic Bearing - Google Patents

Hydraulic Bearing Download PDF

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Publication number
US20120205845A1
US20120205845A1 US13/411,155 US201213411155A US2012205845A1 US 20120205845 A1 US20120205845 A1 US 20120205845A1 US 201213411155 A US201213411155 A US 201213411155A US 2012205845 A1 US2012205845 A1 US 2012205845A1
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US
United States
Prior art keywords
connecting piece
hydraulic bearing
annular
partition unit
chamber
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.)
Abandoned
Application number
US13/411,155
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English (en)
Inventor
Volker Gedenk
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ContiTech Luftfedersysteme GmbH
Original Assignee
ContiTech Luftfedersysteme 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 ContiTech Luftfedersysteme GmbH filed Critical ContiTech Luftfedersysteme GmbH
Assigned to CONTITECH LUFTFEDERSYSTEME GMBH reassignment CONTITECH LUFTFEDERSYSTEME GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GEDENK, VOLKER
Publication of US20120205845A1 publication Critical patent/US20120205845A1/en
Priority to US14/452,299 priority Critical patent/US9488245B2/en
Abandoned legal-status Critical Current

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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
    • F16F13/10—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
    • 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
    • F16F13/18—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 characterised by the location or the shape of the equilibration chamber, e.g. the equilibration chamber, surrounding the plastics spring or being annular

Definitions

  • the invention relates to a hydraulic bearing with hydraulic damping, which has an annular rubber-elastic spring element, that is, a spring element of an elastomer such as rubber or a plastic with rubber-elastic behavior, as specified for example by DIN 7724.
  • the associated rubber-elastic spring element is connected, on the one hand, to the sprung body and, on the other hand, to the unsprung mass by way of respective upper and lower, likewise annular, connecting pieces, which are generally vulcanized on. If such a hydraulic bearing is used as a chassis spring of a vehicle, one connecting piece is connected to the body as a sprung body, while the other connecting piece is connected to the chassis as an unsprung mass.
  • the hydraulic bearing also comprises a hydraulic chamber unit, which comprises a working chamber and a compensating chamber and is surrounded by the annular spring element and/or the annular connecting pieces in such a way that inward deflection causes the volume of the working chamber filled with a damping medium to change, and further comprises a partition unit provided with at least one connecting channel between the working chamber and the compensating chamber.
  • a hydraulic chamber unit which comprises a working chamber and a compensating chamber and is surrounded by the annular spring element and/or the annular connecting pieces in such a way that inward deflection causes the volume of the working chamber filled with a damping medium to change
  • a partition unit provided with at least one connecting channel between the working chamber and the compensating chamber.
  • U.S. Pat. No. 6,595,504 discloses a hydraulic spring with a damper which has a sufficient damping effect under greatly differing loads and frequencies on account of the relatively long damping channels in the partition unit. Disadvantageously, however, the overall height is relatively great here.
  • a hydraulic bearing that is, a rubber-elastic spring with hydraulic damping, which provides sufficient and adjustable damping in different frequency and loading ranges and nevertheless only has an overall size that is as small as possible.
  • the hydraulic bearing of the invention is interposed between a sprung body and an unsprung mass.
  • the hydraulic bearing includes: a lower annular connecting piece connecting the hydraulic bearing to the unsprung mass; an upper annular connecting piece connecting the hydraulic bearing to the sprung body; an annular rubber-elastic spring defining a vertical structural elevation and being connected to the unsprung mass via the lower annular connecting piece and to the sprung body via the upper annular connecting piece; a hydraulic chamber unit including a working chamber and a compensating chamber; the hydraulic chamber unit being surrounded by the annular rubber-elastic spring and/or the annular connecting pieces so as to cause the volume of the working chamber filled with a damping medium to change in response to a deflection of the hydraulic bearing; a partition unit disposed between the working chamber and the compensating chamber; the partition unit including a disc defining a disc plane and the disc having a connecting channel formed in the plane; the annular connecting pieces having respective vertical structural elevations; the partition unit being arranged within the vertical structural elevation of the annular rubber-elastic
  • the partition unit is formed as at least one disc with a connecting channel extending in the plane of the disc and is arranged within the overall vertical elevation of the spring element and a connecting piece, that is, within the extent of the height of these parts in the axis of the spring, that is, the axis along which the spring force acts.
  • the partition unit is arranged within the connecting piece in such a way that the compensating chamber is formed between the partition unit and the end of the connecting piece that is remote from the latter.
  • the rubber-elastic spring element is formed as an upwardly open hollow cone, which is connected, on the one hand, to the sprung body and, on the other hand, to the unsprung mass by way of an upper connecting piece, vulcanized on its inner cone, and a lower connecting piece, vulcanized on its outer cone, and in which the partition unit is arranged within the upper connecting piece in such a way that the compensating chamber is formed between the partition unit and the end of the upper connecting piece.
  • the conical form not only has the effect of optimizing the spring properties, it also provides a larger cavity as an “inner structural space” within the components—assuming concentric arrangement—with the same load-bearing capacity of the spring, so that the structural design and production are simplified.
  • a further advantageous feature is that the connecting piece having the partition unit has a seat or a recess for receiving the partition unit formed as a disc, that is, for example a milled relief or a turned offset. This produces reliable positioning during production and operationally secure fixing.
  • the partition unit comprises multiple discs arranged one above the other, the channels of which are connected in such a way that they communicate with one another.
  • This allows the damping to be adapted to different loads and frequencies in an extremely simple way already during production, by way of the overall length of the damping channel connecting the working chamber and the compensating chamber, which is in actual fact provided by the number of discs, that is specifically it is adapted just by adding further discs. This presupposes that the dimensions match and that prepared/pre-milled connecting pieces are available.
  • a further advantageous feature is that the length of the overall connecting channel formed by multiple discs can be changed by rotating the discs. This either allows the rubber-elastic spring element also to be adapted to changed damping properties under different loads and frequencies after production, or else allows it to be adapted by uniform “standard discs” to different applications just by rotating them during production.
  • a further advantageous feature is that the connecting channels located in the discs are milled in on one side. This allows the corresponding channels to be produced in a particularly easy and low-cost way. The respective covering of the channels then takes place at least partially by the adjacently lying disc or connecting piece.
  • a further advantageous feature is that the compensating space is delimited by a cover at the end of the connecting piece.
  • the fluid that is used for the damping is particularly well protected against the ingress of foreign bodies or moisture.
  • the compensating space is delimited by a membrane arranged within the connecting piece. With such a membrane, which is additionally especially elastic, however, an upside-down type of construction can also be realized, one in which the compensating space is arranged at the bottom.
  • the rubber-elastic spring element is formed as a multilayered spring, that is, as a rubber-metal element. This increases the load-bearing capacity of the spring, so that the inward deflection, the changing of the volume of the working chamber and the damping can be designed for particularly high loads, which is particularly necessary for example in the case of rail vehicles, which must absorb load differences of approximately 1:5 between the unloaded state and the loaded state.
  • the properties of the hydraulic bearing according to the invention with regard to the damping and the overall size can accordingly be used particularly well in the case of a chassis for a rail vehicle.
  • the use of a hydraulic bearing incorporating a rubber-elastic spring element as a machine mounting also offers advantages, since here too the overall size and the damping are the essential properties.
  • FIG. 1 shows a hydraulic bearing according to the invention
  • FIG. 2 shows another embodiment of a hydraulic bearing according to the invention wherein a partition unit comprises three discs;
  • FIG. 3 shows a further embodiment of a hydraulic bearing according to the invention wherein the partition unit comprises three discs;
  • FIG. 4 is a perspective view of the disc of the partition unit of the hydraulic bearing of FIG. 1 ;
  • FIG. 5 is an exploded perspective view of the partition unit of FIGS. 2 and 3 and shows the flow of hydraulic oil passing from the compensating chamber to the working chamber of the hydraulic bearing;
  • FIG. 6 shows the partition unit of FIGS. 2 and 3 with the discs thereof rotated to shorten the path of the hydraulic oil from the compensating chamber to the working chamber;
  • FIG. 7 is a perspective view of a disc wherein the channel formed therein is milled from one side leaving a channel base within the disc.
  • FIG. 1 shows a hydraulic bearing 1 with hydraulic damping for a chassis of a rail vehicle.
  • the hydraulic bearing comprises an annular rubber-elastic spring element 2 , which is connected, on the one hand, to the sprung body and, on the other hand, to the unsprung mass by way of respective upper and lower, likewise annular, connecting pieces 3 and 4 .
  • the sprung body and the unsprung mass that is, the body and the chassis of the rail vehicle, are not represented in any more detail here.
  • the hydraulic bearing 1 also has a hydraulic chamber unit, which comprises a working chamber 5 and a compensating chamber 6 and is surrounded by the annular spring element 2 and the annular connecting pieces 3 and 4 in such a way that inward deflection causes the volume of the working chamber 5 filled with hydraulic oil as damping medium to change.
  • a partition unit 8 which is provided with at least one connecting channel 7 between the working chamber 5 and the compensating chamber 6 and is formed as at least one disc 9 with a connecting channel 7 extending in the plane of the disc 9 as shown, for example, in FIG. 4 .
  • the upper connecting piece 3 has, in this case, a corresponding bore 10 through which the hydraulic oil can enter the connecting channel 7 .
  • the disc 9 is shown seated on thin disc 25 having an aperture 26 communicating with connecting bore 10 formed in the connecting piece 3 .
  • the connecting channel 7 is a through slot with a thin disc 25 defining the base of the channel.
  • the upper connecting piece 3 is therefore formed as a compact pot-shaped body and can consequently be produced correspondingly easily and accurately.
  • the partition unit 8 is arranged within the overall vertical elevation of the spring element 2 and the connecting piece 3 in such a way that the compensating chamber 6 is formed between the partition unit 8 and the end 11 of the connecting piece 3 that is remote from the partition unit 8 .
  • the rubber-elastic spring element 2 is constructed as a multilayered spring, that is, as a rubber-metal element, and is formed as an upwardly open hollow cone. Accordingly, the rubber parts 12 , which are reinforced with metal rings 13 , can be seen in FIGS. 1 to 3 .
  • the rubber-elastic spring element 2 is connected, on the one hand, to the sprung body and, on the other hand, to the unsprung mass (not shown) by way of the upper connecting piece 3 , vulcanized on its inner cone, and by way of the lower connecting piece 4 , vulcanized on its outer cone.
  • the connecting piece 3 which includes the partition unit 8 , is provided with a seat(s) or a recess(es) for receiving one or more discs 9 , 14 and 15 , which singly or together form the partition unit.
  • FIG. 1 shows a hydraulic bearing 1 , which is provided with one disc 9
  • FIG. 2 shows a hydraulic bearing 21 , which is provided with three discs 9 , 14 and 15 .
  • the partition unit 16 consisting of three discs 9 , 14 and 15 , is constructed in such a way that the channels of the discs 9 , 14 and 15 are connected so that they communicate with one another, and consequently provide a long connecting channel 17 .
  • the connecting channel 17 is made up of channel segments in the respective discs ( 9 , 14 , 15 ) identified in FIG. 5 by reference numerals 9 a , 14 a and 15 a .
  • the thick discs 9 , 14 and 15 rest upon respective thin discs 27 , 28 and 29 .
  • the thin discs 27 , 28 and 29 have respective apertures 27 a , 28 a and 29 a through which the hydraulic oil flows from one channel segment to the next as the hydraulic oil flows from the compensating chamber 6 to the working chamber 5 as indicated by the arrows in FIG. 5 .
  • the long connecting channel 17 allows the damping to be adapted to different loads and frequencies in a very simple manner in the case of both versions shown in FIG. 1 and FIG. 2 , by way of the overall length of the connecting channel, without changing the connecting piece 3 . This serves the “same parts principle” in the production of different spring elements.
  • the three discs 9 , 14 and 15 can be rotated about longitudinal axis 32 with respect to one another, so that the length of the composite connecting channel 17 formed by the three channel segments 9 a , 14 a and 15 a can be changed.
  • the thin discs 27 , 28 and 29 are also rotated as shown by comparing their respective positions in FIGS. 5 and 6 .
  • the connecting channel segments 9 a , 14 a and 15 a located here in the thick discs 9 , 14 and 15 are not milled in on one side but are through slots with the apertured thin discs 27 , 28 and 29 sandwiched together with the thick discs.
  • the discs are fixed in the connecting piece 3 by way of a central threaded fastener 18 .
  • the single disc 9 in FIG. 1 is likewise a disc having a channel 7 defined by a through slot and is fixed in the connecting piece 3 by an outer thin disc 19 having an aperture to permit the connecting channel 7 to communicate with the compensating chamber 6 .
  • the compensating chamber is upwardly open, while the working chamber 5 is closed by a cover 20 at the end of the connecting piece 4 .
  • FIG. 3 shows a further embodiment of a hydraulic bearing 22 with a partition unit 16 consisting of three discs in which the compensating chamber 6 is delimited by a membrane 23 arranged within the connecting piece 3 and is closed by a further cover 24 .
  • the hydraulic bearing 22 is therefore well protected against the ingress of foreign bodies or moisture and cannot be damaged during transport or installation.
  • the thick disc 34 is provided with a channel 36 formed by milling the disc from one side and leaving a channel base 38 within the disc.
  • the milled channel 36 ends in an aperture 40 .

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Springs (AREA)
  • Vibration Prevention Devices (AREA)
US13/411,155 2009-09-03 2012-03-02 Hydraulic Bearing Abandoned US20120205845A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US14/452,299 US9488245B2 (en) 2009-09-03 2014-08-05 Hydraulic bearing

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009043939.0 2009-09-03
DE102009043939A DE102009043939A1 (de) 2009-09-03 2009-09-03 Hydrolager
PCT/EP2010/062541 WO2011026786A1 (de) 2009-09-03 2010-08-27 Hydrolager

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/062541 Continuation-In-Part WO2011026786A1 (de) 2009-09-03 2010-08-27 Hydrolager

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US14/452,299 Continuation US9488245B2 (en) 2009-09-03 2014-08-05 Hydraulic bearing

Publications (1)

Publication Number Publication Date
US20120205845A1 true US20120205845A1 (en) 2012-08-16

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Family Applications (2)

Application Number Title Priority Date Filing Date
US13/411,155 Abandoned US20120205845A1 (en) 2009-09-03 2012-03-02 Hydraulic Bearing
US14/452,299 Expired - Fee Related US9488245B2 (en) 2009-09-03 2014-08-05 Hydraulic bearing

Family Applications After (1)

Application Number Title Priority Date Filing Date
US14/452,299 Expired - Fee Related US9488245B2 (en) 2009-09-03 2014-08-05 Hydraulic bearing

Country Status (6)

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US (2) US20120205845A1 (de)
EP (1) EP2473757B1 (de)
CN (1) CN102483122B (de)
AU (2) AU2010291365A1 (de)
DE (1) DE102009043939A1 (de)
WO (1) WO2011026786A1 (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113631826A (zh) * 2019-03-22 2021-11-09 Gmt古米金属技术有限公司 弹簧元件和阻燃的覆盖层
US20220065326A1 (en) * 2019-09-06 2022-03-03 Zhuzhou Times New Material Technology Co., Ltd Liquid composite spring and method for adjusting stiffness and damping property thereof
US20220082151A1 (en) * 2019-09-06 2022-03-17 Zhuzhou Times New Material Technology Co., Ltd Liquid composite spring
US20220128118A1 (en) * 2019-09-06 2022-04-28 Zhuzhou Times New Material Technology Co., Ltd Chamber device for liquid composite spring
EP4102098A1 (de) * 2021-06-10 2022-12-14 ContiTech Vibration Control GmbH Hydrolager
CN116517997A (zh) * 2023-05-30 2023-08-01 中国地震局工程力学研究所 一种橡胶碟簧装置

Families Citing this family (6)

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Publication number Priority date Publication date Assignee Title
CN103692876B (zh) * 2013-12-31 2017-08-29 南京工程学院 汽车悬架
DE102016125909A1 (de) 2016-12-30 2018-07-05 Osram Opto Semiconductors Gmbh Bauteil und Anschlussträger
CN109236928B (zh) * 2018-09-26 2020-08-21 株洲时代新材料科技股份有限公司 一种用于轨道列车的减振装置
CN109455191A (zh) * 2018-11-13 2019-03-12 中车长春轨道客车股份有限公司 变刚度转臂节点及具有该转臂节点的一系定位装置
CN113417963B (zh) * 2021-06-30 2022-03-25 东风汽车集团股份有限公司 一种液压悬置结构及汽车
CN114087309B (zh) * 2021-11-26 2022-07-08 湖南福能液压科技有限公司 一种有轨重载货车自适应阻尼橡胶弹簧

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US4681306A (en) * 1984-03-23 1987-07-21 Metzeler Kautschuk Gmbh Two chamber engine mount with hydraulic damping
US4834349A (en) * 1986-06-12 1989-05-30 Honda Giken Kogyo Kabushiki Kaisha Vibration preventing apparatus using fluid
US4869478A (en) * 1987-01-26 1989-09-26 Hutchinson Improvements to hydraulic antivibratory supports
US5009403A (en) * 1988-07-02 1991-04-23 Tokai Rubber Industries, Ltd. Fluid-filled elastic mount
US5277409A (en) * 1991-12-06 1994-01-11 Tokai Rubber Industries, Ltd. Elastic mount having fluid chamber partially defined by elastically supported oscillating plate
US5779231A (en) * 1993-04-28 1998-07-14 Honda Giken Kogyo Kabushiki Kaisha Vibration-isolating mount device
US6254069B1 (en) * 1997-12-05 2001-07-03 Tokai Rubber Industries, Ltd. Active vibration damping system having controller for generating pulse signal for oscillation of oscillating plate partially defining fluid chambers

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US4969632A (en) * 1989-08-10 1990-11-13 Lord Corporation Mount with adjustable length inertia track
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JP2510919B2 (ja) * 1991-12-24 1996-06-26 東海ゴム工業株式会社 流体封入式マウント装置
FR2701525B1 (fr) * 1993-02-12 1995-04-21 Hutchinson Perfectionnements aux dispositifs antivibratoires hydrauliques.
JPH08159209A (ja) * 1994-12-12 1996-06-21 Toyo Tire & Rubber Co Ltd 液封入式防振装置
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JP3551673B2 (ja) 1996-12-25 2004-08-11 東海ゴム工業株式会社 流体封入式防振装置
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US4681306A (en) * 1984-03-23 1987-07-21 Metzeler Kautschuk Gmbh Two chamber engine mount with hydraulic damping
US4834349A (en) * 1986-06-12 1989-05-30 Honda Giken Kogyo Kabushiki Kaisha Vibration preventing apparatus using fluid
US4869478A (en) * 1987-01-26 1989-09-26 Hutchinson Improvements to hydraulic antivibratory supports
US5009403A (en) * 1988-07-02 1991-04-23 Tokai Rubber Industries, Ltd. Fluid-filled elastic mount
US5277409A (en) * 1991-12-06 1994-01-11 Tokai Rubber Industries, Ltd. Elastic mount having fluid chamber partially defined by elastically supported oscillating plate
US5779231A (en) * 1993-04-28 1998-07-14 Honda Giken Kogyo Kabushiki Kaisha Vibration-isolating mount device
US6254069B1 (en) * 1997-12-05 2001-07-03 Tokai Rubber Industries, Ltd. Active vibration damping system having controller for generating pulse signal for oscillation of oscillating plate partially defining fluid chambers

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113631826A (zh) * 2019-03-22 2021-11-09 Gmt古米金属技术有限公司 弹簧元件和阻燃的覆盖层
US20220065326A1 (en) * 2019-09-06 2022-03-03 Zhuzhou Times New Material Technology Co., Ltd Liquid composite spring and method for adjusting stiffness and damping property thereof
US20220082151A1 (en) * 2019-09-06 2022-03-17 Zhuzhou Times New Material Technology Co., Ltd Liquid composite spring
US20220128118A1 (en) * 2019-09-06 2022-04-28 Zhuzhou Times New Material Technology Co., Ltd Chamber device for liquid composite spring
US11732773B2 (en) * 2019-09-06 2023-08-22 Zhuzhou Times New Material Technology Co., Ltd Liquid composite spring
EP4102098A1 (de) * 2021-06-10 2022-12-14 ContiTech Vibration Control GmbH Hydrolager
CN116517997A (zh) * 2023-05-30 2023-08-01 中国地震局工程力学研究所 一种橡胶碟簧装置

Also Published As

Publication number Publication date
EP2473757B1 (de) 2018-02-28
AU2016216679B2 (en) 2018-10-04
AU2016216679A1 (en) 2016-09-08
CN102483122A (zh) 2012-05-30
DE102009043939A1 (de) 2011-03-10
AU2010291365A1 (en) 2012-04-26
US9488245B2 (en) 2016-11-08
WO2011026786A1 (de) 2011-03-10
CN102483122B (zh) 2015-05-27
US20140346720A1 (en) 2014-11-27
EP2473757A1 (de) 2012-07-11

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