WO1994001695A1 - Element deformable de transmission de force - Google Patents

Element deformable de transmission de force Download PDF

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Publication number
WO1994001695A1
WO1994001695A1 PCT/SE1993/000615 SE9300615W WO9401695A1 WO 1994001695 A1 WO1994001695 A1 WO 1994001695A1 SE 9300615 W SE9300615 W SE 9300615W WO 9401695 A1 WO9401695 A1 WO 9401695A1
Authority
WO
WIPO (PCT)
Prior art keywords
end plates
elastomer body
spring element
annular elements
plates
Prior art date
Application number
PCT/SE1993/000615
Other languages
English (en)
Inventor
Karl Olle Lennart Johansson
Original Assignee
Trelleborg Industri Aktiebolag
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 Trelleborg Industri Aktiebolag filed Critical Trelleborg Industri Aktiebolag
Priority to AU45213/93A priority Critical patent/AU4521393A/en
Publication of WO1994001695A1 publication Critical patent/WO1994001695A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
    • B60G11/02—Resilient suspensions characterised by arrangement, location or kind of springs having leaf springs only
    • B60G11/10—Resilient suspensions characterised by arrangement, location or kind of springs having leaf springs only characterised by means specially adapted for attaching the spring to axle or sprung part of the vehicle
    • B60G11/107—Sliding or rolling mountings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G5/00—Resilient suspensions for a set of tandem wheels or axles having interrelated movements
    • B60G5/04—Resilient suspensions for a set of tandem wheels or axles having interrelated movements with two or more pivoted arms, the movements of which are resiliently interrelated, e.g. the arms being rigid
    • B60G5/053—Resilient suspensions for a set of tandem wheels or axles having interrelated movements with two or more pivoted arms, the movements of which are resiliently interrelated, e.g. the arms being rigid a leafspring being used as equilibration unit between two axle-supporting units
    • 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
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/40—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers consisting of a stack of similar elements separated by non-elastic intermediate layers
    • F16F1/403—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers consisting of a stack of similar elements separated by non-elastic intermediate layers characterised by the shape of the non-elastic interengaging parts between the elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2200/00—Indexing codes relating to suspension types
    • B60G2200/30—Rigid axle suspensions
    • B60G2200/318—Rigid axle suspensions two or more axles being mounted on a longitudinal rocking or walking beam
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/10—Type of spring
    • B60G2202/11—Leaf spring
    • B60G2202/112—Leaf spring longitudinally arranged
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/10—Type of spring
    • B60G2202/14—Plastic spring, e.g. rubber
    • B60G2202/143—Plastic spring, e.g. rubber subjected to compression
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/12—Mounting of springs or dampers
    • B60G2204/121—Mounting of leaf springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B60G2204/12—Mounting of springs or dampers
    • B60G2204/125—Mounting of rubber type springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/423—Rails, tubes, or the like, for guiding the movement of suspension elements
    • B60G2204/4232—Sliding mounts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/45—Stops limiting travel
    • B60G2204/4504—Stops limiting travel using cable or band to prevent extension

Definitions

  • This invention relates to a yieldable power-trans ⁇ mitting element of the type defined in the preamble to appended claim 1.
  • SE-B-436,480 (US-A-4,615,513) discloses a flexible, force-transmitting resilient element having two end plates, a substantially cylindrical intermediate body therebetween, a number of spaced-apart annular elements inserted in and connected to the elastomer body, and a mechanical connecting element which is disposed between the end plates and extends through the elastomer body and the annular elements inserted therein and which is adapted to limit the extent to which the end plates can be pulled away from one another when the resilient element is sub ⁇ jected to tensile load.
  • the resilient element described in SE-B-436,480 is intended to transmit compression and tensile forces between two components which are movable in relation to one another, e.g.
  • the mechanical connecting element extends through the rubber body and interconnects the end plates in such a manner that they are limitedly movable in relation to one another.
  • the mechanical connecting element is in the form of a link element which is arranged in the rubber body and which, at its opposite ends, is movably mounted on holders fixedly connected to the adjoining end plates.
  • the metal rings vulcanised into the rubber body at regular intervals between the end plates serve to affect the spring charac- teristics of the resilient element and to counteract bulg ⁇ ing of the rubber body when subjected to tensile load.
  • the metal rings and the end plates of this resilient element are substantially flat.
  • a resilient element of the type disclosed in SE-B- 436,480 shows good properties when used primarily for transmitting compression and tensile forces between two units which are connected to the end plates of the resilient element.
  • the link element between the end plates ensures that excessive tensile load does not cause the rubber body to come loose from the end plates.
  • this known resilient element does not show equally good properties when used primarily for transmitting shearing and bending movements between an axle and a vehicle frame or a bogie frame.
  • GB-862,173 discloses a spring assembly comprising a number of rubber discs between which dome-shaped metal plates are bonded by vulcanisation.
  • the spring assembly consists of two mirror-inverted units so arranged that th domed metal plates of one unit either have their crowns facing the crowns of the metal plates of the other unit o have their concave sides facing the concave sides of the metal plates of the other unit.
  • the two units are inter ⁇ connected by being vulcanised to an intermediate plate which in the former variant is biconcave and in the lat ⁇ ter variant is biconvex.
  • the purpose of so designing the spring assembly is to avoid the need of mechanical interconnection of the metal plates vulcanised into the rubber body.
  • the intermediate plate is designed as a biconvex disc, and the domed metal plates provided on bot sides of the intermediate plate have their crowns facing outwards, towards the end plates.
  • the spring elements are inserted between the conven tional leaf-spring assembly of the motor vehicle and the pivotally suspended axle.
  • the spring element essentially takes up only forces directed in its axial direction, i.e. compressive and tensile forces, since shearing and bending forces are extremely limited owing t the spring element being inserted between the outer end o the axle and the outer end of the leaf-spring assembly, and to the mounting place of the axle and the mounting en of the leaf-spring assembly being fixedly interconnected.
  • US-A-4,995,598 teaches a resilient element primarily intended to withstand heavy compressive loads and being o tubular and laminated structure.
  • This element has two end plates and a vulcanised annular metal plate vulcanised into and serving to stiffen the tubular rubber body place between and vulcanised to the end plates.
  • the resilient element is inserted between two components and is screwed to one of these by means of a bolt extending through the resilient element and rigidly connecting one end plate to this component.
  • the bolt serves as a buffer member normally extending freely through the through hole of the resilient element at a distance from the wall thereof, but being, in case of heavy shearing loads, brought into engagement with this wall in order to prevent relative motion of the end plates in the plane thereof.
  • EP-A-0,263,388 discloses a wheel suspension, in which a rubber spring element is inserted between the outer end of a leaf-spring assembly and an axle supported thereby, in order to take up relative motion between the• leaf springs and the axle.
  • This spring element is tubular and has essentially the same structure as the element according to SE-B-436,480 (US-A-4,615,513) , except that the metal plates are dome-shaped and the connecting ele ⁇ ment is a chain extending freely through the tubular spring element in order to limit the extent to which the end plates can be pulled away from one another when the spring element is subjected to axial tensile forces.
  • the chain links do not really have any other effect on the spring characteristics of the element.
  • US-A-4,105,266 teaches a tubular spring element, in which annular metal plates are vulcanised to the tubular rubber body.
  • the spring element has a circular-cylindri ⁇ cal portion into which are vulcanised flat annular metal plates, and a conical portion into which are vulcanised annular domed plates. Between these two portions, there is provided an intermediate ring having a flat side and a domed side in order to form a transition between the two portions.
  • the individual rubber layers have concentric zones located outside one another of gradually decreasing moduli of elasticity, as seen from the radially outermost to the radially innermost zone of each rubber layer, or vice versa.
  • This spring element does not include any connectin element or the like restricting the extent to which the end plates can be pulled apart upon tensile load, or otherwise affecting the spring characteristics of the element.
  • US-A-3,677,535 teaches a spring element having a plu- rality of separate annular elements inserted between a supporting and a supported member and precompressed by being clamped together by means of a throughgoing stud bolt, nuts and intermediate washers, there being provided a rubber disc between each intermediate washer and the abutment surface of each component.
  • the annular elements have been provided with vulcanised metal rings on the end surfaces, intermediate washers being inserted for stacking and guiding purposes.
  • the interme ⁇ diate washers serve to mechanically prevent adjoining metal plates from sliding in the radial direction in rela tion to one another.
  • the inner peripheral edge of the intermediate washers is in the form of an annular cutting edge engaging the circumferential surface of the through going stud bolt.
  • GB-A-2,117,085 discloses a spring element, in which a plurality of rigid plates are embedded in elastomeric material, and a stabilising means extends towards and through the plates. This construction resembles those disclosed in US-A-4,995,598 and US-A-3,677,535.
  • the prior-art spring elements have various drawbacks that either limit their service life or unfavourably affect the spring characteristics.
  • One object of the present invention is, therefore, t provide a spring element showing a much better combinatio of properties than the prior-art elements and having a good capacity for transmitting shearing and bending move ⁇ ments without breakdown as well as a good capacity for transmitting compressive and tensile forces. According to the invention, this object is achieved by a spring element as defined in appended claim 1. Espe- cially preferred embodiments of the invention are recited in the appended subclaims.
  • the power-transmitting spring element com ⁇ prises end plates and a substantially cylindrical elasto- mer body inserted between the end-plate surfaces facing one another.
  • a number of spaced-apart annular elements are inserted in and connected to the elastomer body.
  • An inter ⁇ mediate ring whose two opposite end surfaces are concave, is inserted centrally in the elastomer body.
  • the end-plate surfaces facing one another are convex, and the annular elements between the convex surfaces of the end plates and the intermediate ring are correspondingly domed.
  • the end plates, the elastomer body, the intermediate ring and the annular elements have a through hole through which extends a rod-shaped connecting element and which is of larger width than this element.
  • the end plates On the outside, the end plates have cup-shaped seats for engaging circumferential abut ⁇ ment surfaces projecting from the connecting element.
  • the present invention is based on the spring ele- ment of SE-B-436,480 (US-A-4,615,513) and is founded on the insight that the deficiencies of this element as to the transmission of shearing and bending movements are largely due to the fact that the different layers of the elastomer body between the annular elements and the end plates are subjected to considerable compressive and tensile stresses, not only when such stresses are trans ⁇ mitted between the end plates but also when shearing and bending forces are transmitted.
  • the end plates and the discs or rings inserted in the elastomer body in such a manner that a parallel displacement or inclination of the end plates in relation to one another will largely result in the elasto meric material being subjected to shear deformation only, the elastomer layers may be thinner, thus being able to take up more load per surface unit. It has been found tha this can be achieved if the different layers of the elas ⁇ tomer body and the metal rings inserted therein are domed and so positioned that their convex sides face a biconcav intermediate ring arrranged centrally in the elastomer body, i.e.
  • a ring whose opposite end surfaces are concave
  • the end-plate sides facing the elastomer body are also convex.
  • the elastomer body and the adjoining metal rings are adhesively attached to each other, preferably vulca ⁇ nised to each other, with the aid of an adhesive system.
  • the domed shape of the metal rings and the elastomer layers results in that static and dynamic forces are transmitted from one end plate to the other largely by shearing forces.
  • This is due to the fact that a deformation of the elastomeric material, e.g. when the end plates are inclined in relation to one another, i transmitted from or towards the external periphery of the substantially circular-cylindrical spring assembly away from and towards, respectively, the centre, the deforma ⁇ tion forces being diverted by the domed surfaces of the annular element and thus being to an even greater extent forcedly guided and directed as shearing forces along the domed surfaces.
  • This guiding effect is obtained upon com- pressive and tensile load in the axial direction of the spring assembly as well as upon shearing and bending move ments between the two end plates.
  • the connecting element being designed as a rigid rod extending through an axial through hole in the spring element, to this hole having a larger diameter th the rod, and to the rod having enlarged ends engaging cu shaped seats on the outside of the end plates, the sprin assembly can be deformed with a minimum of influence from the engagement of the rod with the end plates and with but an insignificant engagement between the rod and the wall of the through hole of the element and, should such insig- nificant engagement occur, only with at a gradually in ⁇ creasing engagement, as seen in the longitudinal direction of the rod.
  • Fig. 1 is a side view, partly in longitudinal section, showing a first embodiment of the spring element when loaded.
  • Fig. 2 is a longitudinal section of a second embodiment of the spring element when loaded.
  • the spring element shown in Fig. 1 has two cup-shaped end plates 10 made of metal material. A suitable number of mounting holes 12 are distributed round the flange portion 11 of the end plates. The plates 10 are arranged with their convex sides facing one another. Between the plates, there is provided a spring assembly 13, which has a cen- trally arranged intermediate ring 14 which is biconcave, i.e. which has two concave opposite surfaces.
  • the inter ⁇ mediate ring 14 is connected to each of the end plates 10 by vulcanised elastomeric material, preferably a rubber mixture having a hardness of 60-80° Shore, especially 65-75° Shore, e.g. 70° Shore.
  • a suitable rubber mixture contains natural rubber (NR) to which has been admixed styrene-butadiene rubber (SBR) in order to increase the toughness of the mixture.
  • Domed annular elements 15 of metal material are inserted and vulcanised into the vulcanised elastomeric material between the intermediate ring 14 and each of the end plates 10 in order to divide the elastomeric material into part layers 16, thereby to achieve the desired guid ⁇ ance of stresses in the elastomeric material arising upon loading of the spring element.
  • the end plates 10, the annular elements 15 and the intermediate ring 14 have essentially the same curvature at their dome-shaped sur- faces, which preferably are designed substantially as the circumferential surface of a spherical zone.
  • the differen part layers 16 and the adjoining components 10, 15 and 14 are joined into one piece by vulcanisation using an adhe- sive system.
  • a rod 17 with enlarged ends 18 extends through a cen tral hole 19 in the spring element and serves to keep the element together, as well as to take up any point loads that might damage the elastomeric material and its adhe- sion to the different metal layers.
  • the enlarged ends 18, needed for keeping the element together are designed wit a dome-shaped surface 20 (see Fig. 2) facing the adjoinin end plate 10 and adapted to cooperate with a correspond ⁇ ingly domed surface 21 (see Fig. 2) on the end plate 10.
  • the centres of curvature of the two substantially spheri ⁇ cally domed surfaces 20 and 21 are located at the points to enable deformation of the spring assembly 13 with a minimum of forces due to the engagement of the rod 17 wit the end plates 10.
  • the enlarged parts 18 are formed or mounted on the rod 17 in any suitable way.
  • one enlarged part may b a forged head, while the other is a ring passed on and welded to the rod or is a nut screwed thereon.
  • the end surfaces 22 of the rod 17, preferably convex ly domed as well, are situated at a certain distance from the plane defined by the free external surfaces of the flanges 11. This makes it possible for the rod 17 to serv as a force-absorbing element in the event that the spring element is subjected to excessively high impact loads in the compacting direction.
  • the spring element according to the invention is distinguished by the end plates 10 and the intermediate plates or annular elements 15 being domed and having thei convex sides facing a concave surface of the centre piece or intermediate ring 14.
  • the elastomeric material in the part layers 16 will largely be subjected to only shearing deformation when th end plates 10 are displaced in parallel or set at an angl in relation to one another.
  • the elastomer layer 16 may be thinner than completely flat elastomer layers. Because the elastomer layers can be thinner, they are als able to take up a greater load per surface unit, while at the same time the spring element maintains its pliancy in bending deformation.
  • the centre hole 19 for the rod 17 should be so large that the spring assembly 13 can be deformed into an S shape, as indicated by a dash-dot line in Fig. 2, and that the rod, if it were to engage the inner wall of the through hole of the spring element when this is con ⁇ siderably deformed by inclination and parallel displace- ment of the end plates 10 in relation to one another, wil do so by the length of engagement increasing gradually.
  • the spring assem ⁇ bly is vulcanised directly to the end plates 10, which is preferred.
  • the spring assembly may also be clampe between the end plates and thus be joined thereto in posi tive, i.e. form-fitting, and non-positive manner, as show in Fig. 2.
  • the spring assembly has domed annular elements 23 vulcanised to the adjoining elastomer layer 16 and pressed against the convex surface of the en plate 10.
  • the elastomeric mate rial is on both sides of the intermediate ring 14 divided into four part layers 16 by means of three annular ele- ments 15.
  • more or fewer part layers and annular elements may be used, if so desired.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Springs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Abstract

Un élément élastique de transmission de force comporte des plaques terminales (10) et un corps élastomère sensiblement cylindrique (13) inséré entre les surfaces opposées de ces plaques terminales. Un certain nombre d'éléments annulaires espacés (15) sont insérés dans le corps élastomère (13) et reliés à ce dernier. Une bague intermédiaire (14), dont les deux surfaces opposées sont concaves, est insérée centralement dans le corps élastomère (13). Les surfaces des plaques terminales (10), situées en regard l'une de l'autre, sont convexes, et les éléments annulaires (15) disposés entre les surfaces convexes des plaques terminales et la bague intermédiaire (14) sont bombés en conséquence. Les plaques terminales (13), le corps élastomère (13), la bague intermédiaire (14) et les éléments annulaires (15) comportent un trou débouchant à travers lequel passe un élément de raccordement en forme de tige (17) et dont le diamètre est supérieur à celui de l'élément de raccordement. A l'extérieur, les plaques terminales (10) présentent des embases cupuliformes (21) venant en contact avec des surfaces de butée circonférentielles (20) faisant saillie sur l'élément de raccordement (17).
PCT/SE1993/000615 1992-07-06 1993-07-06 Element deformable de transmission de force WO1994001695A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU45213/93A AU4521393A (en) 1992-07-06 1993-07-06 Yieldable power-transmitting element

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9202074A SE500084C2 (sv) 1992-07-06 1992-07-06 Eftergivligt, kraftöverförande fjäderelement
SE9202074-2 1992-07-06

Publications (1)

Publication Number Publication Date
WO1994001695A1 true WO1994001695A1 (fr) 1994-01-20

Family

ID=20386706

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1993/000615 WO1994001695A1 (fr) 1992-07-06 1993-07-06 Element deformable de transmission de force

Country Status (3)

Country Link
AU (1) AU4521393A (fr)
SE (1) SE500084C2 (fr)
WO (1) WO1994001695A1 (fr)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19608860A1 (de) * 1996-03-07 1997-09-18 Joern Gmbh Druckfeder
US5676356A (en) * 1996-05-30 1997-10-14 The Boler Company Flexible bolster
US7201367B2 (en) 2002-12-12 2007-04-10 Caterpillar Inc Load-bearing resilient mount
DE102008052756A1 (de) * 2008-10-22 2010-04-29 Magna Steyr Fahrzeugtechnik Ag & Co. Kg Radaufhängung
GB2443380B (en) * 2005-10-04 2010-07-21 La Z Boy Inc Rocker spring assembly
EP2878851A1 (fr) * 2013-11-29 2015-06-03 Jörn GmbH Ressort de pression ayant une protection contre les surcharges, en particulier entre une extrémité de ressort à lame et un corps d'essieu d'un poids lourd
EP2891816A4 (fr) * 2012-08-28 2016-06-22 Avic Beijing Inst Of Aeranutical Materials Ressort en caoutchouc amortisseur pour suspension d'automobile
EP2891817A4 (fr) * 2012-08-28 2016-06-22 Avic Beijing Inst Of Aeronautical Materials Ressort auxiliaire en caoutchouc pour cadre de suspension automobile
WO2017097558A1 (fr) * 2015-12-09 2017-06-15 Contitech Luftfedersysteme Gmbh Élément ressort en métal-caoutchouc
CN107606052A (zh) * 2017-09-20 2018-01-19 株洲时代新材料科技股份有限公司 减振支撑装置
CN108930741A (zh) * 2018-08-15 2018-12-04 株洲时代新材料科技股份有限公司 一种可调节刚度的橡胶垫及刚度调节方法
CN108930742A (zh) * 2018-08-15 2018-12-04 株洲时代新材料科技股份有限公司 一种可调节轴向刚度的橡胶垫及刚度调节方法
CN108999905A (zh) * 2018-08-15 2018-12-14 株洲时代新材料科技股份有限公司 一种可调节偏转刚度的橡胶垫及刚度调节方法
EP3462053A1 (fr) * 2017-09-20 2019-04-03 Zhuzhou Times New Material Technology Co., Ltd Dispositif de support amortissant les vibrations
CN111542445A (zh) * 2018-03-08 2020-08-14 沃尔沃卡车集团 用于车辆转向架悬挂装置的弹簧组件
CN112211937A (zh) * 2020-09-25 2021-01-12 中国直升机设计研究所 一种非平面剪切弹性叠层隔振器
WO2021086575A1 (fr) * 2019-11-01 2021-05-06 Caterpillar Inc. Liaison centrale pour supports de suspension de camion articulés
TWI734527B (zh) * 2019-06-18 2021-07-21 日商普利司通股份有限公司 防震裝置（二）
US11084672B2 (en) 2018-10-24 2021-08-10 Produits Hevea Inc. Dock bumpers and/or vehicles bumpers

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CN107630973B (zh) * 2017-09-20 2024-04-09 株洲时代新材料科技股份有限公司 减振支撑装置

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DE718344C (de) * 1937-12-30 1942-03-10 Carl F W Borgward Abfederung fuer Kraftfahrzeuge mit unabhaengig gelagerten, durch schwingende Halbachsen oder Querlenker gefuehrten Raedern
GB862173A (en) * 1957-04-12 1961-03-01 Metalastik Ltd Improvements in or relating to spring assemblies
US3677535A (en) * 1970-08-24 1972-07-18 Lord Corp Axial suspension system that accommodate relative lateral movement
US4105266A (en) * 1975-11-17 1978-08-08 Lord Corporation Laminated bearing with plural modulus layer
GB2117085A (en) * 1982-03-19 1983-10-05 Wright Barry Corp Elastomeric stack with stabilising means
US4615513A (en) * 1983-05-05 1986-10-07 Volvo Bm Ab Flexible, force-transmitting element
EP0263388A2 (fr) * 1986-10-09 1988-04-13 MAN Nutzfahrzeuge Aktiengesellschaft Utilisation et construction d'un support en caoutchouc
US4995598A (en) * 1988-03-31 1991-02-26 Dunlop Limited Resilient mounting

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Publication number Priority date Publication date Assignee Title
DE718344C (de) * 1937-12-30 1942-03-10 Carl F W Borgward Abfederung fuer Kraftfahrzeuge mit unabhaengig gelagerten, durch schwingende Halbachsen oder Querlenker gefuehrten Raedern
GB862173A (en) * 1957-04-12 1961-03-01 Metalastik Ltd Improvements in or relating to spring assemblies
US3677535A (en) * 1970-08-24 1972-07-18 Lord Corp Axial suspension system that accommodate relative lateral movement
US4105266A (en) * 1975-11-17 1978-08-08 Lord Corporation Laminated bearing with plural modulus layer
GB2117085A (en) * 1982-03-19 1983-10-05 Wright Barry Corp Elastomeric stack with stabilising means
US4615513A (en) * 1983-05-05 1986-10-07 Volvo Bm Ab Flexible, force-transmitting element
EP0263388A2 (fr) * 1986-10-09 1988-04-13 MAN Nutzfahrzeuge Aktiengesellschaft Utilisation et construction d'un support en caoutchouc
US4995598A (en) * 1988-03-31 1991-02-26 Dunlop Limited Resilient mounting

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DE19608860A1 (de) * 1996-03-07 1997-09-18 Joern Gmbh Druckfeder
DE19608860C2 (de) * 1996-03-07 2000-06-29 Joern Gmbh Druckfeder
US5676356A (en) * 1996-05-30 1997-10-14 The Boler Company Flexible bolster
US7201367B2 (en) 2002-12-12 2007-04-10 Caterpillar Inc Load-bearing resilient mount
GB2443380B (en) * 2005-10-04 2010-07-21 La Z Boy Inc Rocker spring assembly
DE102008052756A1 (de) * 2008-10-22 2010-04-29 Magna Steyr Fahrzeugtechnik Ag & Co. Kg Radaufhängung
EP2891816A4 (fr) * 2012-08-28 2016-06-22 Avic Beijing Inst Of Aeranutical Materials Ressort en caoutchouc amortisseur pour suspension d'automobile
EP2891817A4 (fr) * 2012-08-28 2016-06-22 Avic Beijing Inst Of Aeronautical Materials Ressort auxiliaire en caoutchouc pour cadre de suspension automobile
EP2878851A1 (fr) * 2013-11-29 2015-06-03 Jörn GmbH Ressort de pression ayant une protection contre les surcharges, en particulier entre une extrémité de ressort à lame et un corps d'essieu d'un poids lourd
WO2017097558A1 (fr) * 2015-12-09 2017-06-15 Contitech Luftfedersysteme Gmbh Élément ressort en métal-caoutchouc
EP3770460A1 (fr) 2017-09-20 2021-01-27 Zhuzhou Times New Material Technology Co., Ltd Dispositif de support amortissant les vibrations
EP3462053A1 (fr) * 2017-09-20 2019-04-03 Zhuzhou Times New Material Technology Co., Ltd Dispositif de support amortissant les vibrations
US10677311B2 (en) 2017-09-20 2020-06-09 Zhuzhou Times New Material Technology Co. Ltd. Vibration-damping support device
CN107606052B (zh) * 2017-09-20 2024-04-09 株洲时代新材料科技股份有限公司 减振支撑装置
CN107606052A (zh) * 2017-09-20 2018-01-19 株洲时代新材料科技股份有限公司 减振支撑装置
CN111542445A (zh) * 2018-03-08 2020-08-14 沃尔沃卡车集团 用于车辆转向架悬挂装置的弹簧组件
US11458791B2 (en) * 2018-03-08 2022-10-04 Volvo Truck Corporation Spring assembly for a vehicle bogie suspension arrangement
CN108930742A (zh) * 2018-08-15 2018-12-04 株洲时代新材料科技股份有限公司 一种可调节轴向刚度的橡胶垫及刚度调节方法
CN108999905A (zh) * 2018-08-15 2018-12-14 株洲时代新材料科技股份有限公司 一种可调节偏转刚度的橡胶垫及刚度调节方法
CN108930741A (zh) * 2018-08-15 2018-12-04 株洲时代新材料科技股份有限公司 一种可调节刚度的橡胶垫及刚度调节方法
US11084672B2 (en) 2018-10-24 2021-08-10 Produits Hevea Inc. Dock bumpers and/or vehicles bumpers
TWI734527B (zh) * 2019-06-18 2021-07-21 日商普利司通股份有限公司 防震裝置（二）
US11299002B2 (en) 2019-11-01 2022-04-12 Caterpillar Inc. Center link for articulated truck suspension mounts
WO2021086575A1 (fr) * 2019-11-01 2021-05-06 Caterpillar Inc. Liaison centrale pour supports de suspension de camion articulés
CN112211937A (zh) * 2020-09-25 2021-01-12 中国直升机设计研究所 一种非平面剪切弹性叠层隔振器

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AU4521393A (en) 1994-01-31
SE500084C2 (sv) 1994-04-11
SE9202074L (sv) 1994-01-07
SE9202074D0 (sv) 1992-07-06

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