EP1117944A1 - Palier metallo-caoutchoute a amortissement axial - Google Patents

Palier metallo-caoutchoute a amortissement axial

Info

Publication number
EP1117944A1
EP1117944A1 EP00956114A EP00956114A EP1117944A1 EP 1117944 A1 EP1117944 A1 EP 1117944A1 EP 00956114 A EP00956114 A EP 00956114A EP 00956114 A EP00956114 A EP 00956114A EP 1117944 A1 EP1117944 A1 EP 1117944A1
Authority
EP
European Patent Office
Prior art keywords
bearing
channel
chambers
elastomer
axial
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.)
Ceased
Application number
EP00956114A
Other languages
German (de)
English (en)
Inventor
Andreas Vossel
Frank Meyerink
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.)
ZF Lemfoerder GmbH
Original Assignee
ZF Lemfoerder 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 ZF Lemfoerder GmbH filed Critical ZF Lemfoerder GmbH
Publication of EP1117944A1 publication Critical patent/EP1117944A1/fr
Ceased legal-status Critical Current

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
    • 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 rubber bearing with axial damping, which consists essentially of an inner part, a section surrounding the inner part and connected to it by vulcanization, chambers for a damping agent, a channel support with a damping agent channel and a bearing sleeve receiving the aforementioned parts
  • Rubber bearings are manufactured in a wide variety of designs and are often used in particular in automotive engineering.These are used, for example, to mount the wheel suspension or as an auxiliary frame bearing. Depending on the application, different requirements are placed on the damping behavior of the rubber bearings. The damping behavior can be determined by the choice of materials, particularly the elastomer , as well as the structural design of the warehouse
  • a channel carrier is arranged between the bearing inner part and the outer sleeve, in which the steaming agent channel connecting the radially distributed chambers is formed by the amount and the type of steaming agent and of course the size of the steaming agent chambers can influence the steaming behavior of the bearing.
  • the bearing disclosed in the document is primarily designed to influence the steaming behavior with radially entered forces
  • the axial damping behavior of the bearing plays an important role.
  • the object of the invention is to provide a rubber bearing which can be made variable with a simple structure with regard to its axial vapor behavior
  • the rubber bearing consists in a known manner of a bearing inner part, an elastomer surrounding the bearing inner part in sections and connected to it by vulcanization, and has chambers for receiving a steaming agent as well as a steaming agent channel that enables the steaming agent to circulate between the chambers Bearing sleeve included
  • the inner bearing part like other bearings known from the prior art, is formed in several pieces.
  • the inner bearing part has a section at the axial bearing ends with a larger diameter than the central region of the inner bearing part According to the invention, a channel carrier with chambers for the damping means is arranged between the sections of the bearing inner part which are enlarged in diameter.
  • This channel carrier consists of an inner sleeve, an elastomer connected to the inner sleeve by vulcanization and a channel ring surrounding the inner sleeve and the elastomer and also connected to them by vulcanization.
  • a channel ring surrounding the inner sleeve and the elastomer and also connected to them by vulcanization.
  • at least one groove is worked in, which forms at least one channel between the channel ring and the outer sleeve of the bearing, via which the chambers formed in the channel carrier and during assembly between the channel carrier and the sections of the bearing inner part with enlarged diameter are formed Chambers are interconnected.
  • the multi-piece inner bearing part consists of two supporting bodies, one of which forms the entire central region of the inner bearing part and an adjoining section of the one axial bearing end that is enlarged in diameter compared to this region.
  • the other support body is designed as a ring which forms the other, enlarged in diameter, axial bearing end of the bearing inner part. According to the invention, the latter support body is pushed onto the first support body forming the central region of the inner bearing part.
  • Both supporting bodies are surrounded in the area of the axial bearing ends by an elastomer which is connected to them and an outer ring by vulcanization.
  • a shoulder for axially fixing the position of the channel carrier is provided on the part forming the central region of the inner bearing part in the vicinity of the section with an enlarged diameter.
  • the part of the support body which forms the central region of the bearing inner part is also provided with a flattened portion on its circumferential surface.
  • the channel for the damping agent runs obliquely or helically on the outer contour of the channel ring in the sense of the invention.
  • the steam channel means connects those chambers with one another which form during assembly between the channel carrier and the diameter-enlarged sections of the inner bearing part.
  • the modular structure of the bearing makes it possible to adapt the steam behavior of the bearing to the respective application in a particularly advantageous manner.
  • the channel carrier provided according to the invention, it is also possible in a simple manner to interpret the identification behavior differently.
  • This allows the outer contour of the inner sleeve of the channel carrier as well as the the elastomer surrounding the inner sleeve and thus the outer contour of the channel support have a cross-section deviating from the circular shape, while its inner contour has an approximately circular cross-section.
  • This makes it possible to vary the characteristic behavior of the bearing without changing the shape of the inner part of the bearing, especially without the cylindrical inner part of the bearing can go away, for example, it is possible without increased manufacturing effort, by a square or rectangular shape of the channel support cross-section, a different identifier in the circumferential direction to achieve behavior of the bearing
  • the multi-piece inner part of the bearing consisting of the supporting bodies can also consist of relatively thin hollow profile elements
  • the invention creates a bearing structure that is characterized by a high degree of flexibility with regard to adapting the essential bearing parameters to the respective application. This is primarily due to the modular
  • Bearing structure but especially achieved by the channel support, which by the shape
  • its outer contour enables a high degree of variability with regard to the radial steam behavior of the bearing and, on the other hand, allows fine tuning of the axial steam behavior by means of a length of the steam medium channel which can be varied within wide limits.
  • the advantages illustrated are also achieved with a comparatively simple bearing structure
  • FIG. 1 the bearing according to the invention in an axially sectioned illustration
  • Figure 2 The bearing of Figure 1 in an axonomet ⁇ schen, partially cut
  • FIG. 3 shows the channel carrier of the bearing according to FIGS. 1 and 2 in an axial sectional view
  • FIG. 4 shows the channel carrier according to FIG. 3 in an axonometric view
  • FIG. 5 shows the duct support according to FIGS. 3 and 4 in a radially sectioned view
  • FIG. 6 shows a support body of the bearing inner part in an axially sectioned view
  • FIG. 7 shows the support body according to FIG. 6 in an axonometric view
  • FIG. 8 shows another together with the support body according to FIG. 6 the supporting body forming the bearing inner part
  • Figure 1 illustrates the structure of the bearing according to the invention with the aid of a sectional view in which the section is axially guided through the bearing.
  • the bearing is essentially formed from a bearing inner part 1, a channel support 1 1 surrounding the bearing inner part 1 and a bearing sleeve 10 receiving these parts
  • Inner bearing part 1 is formed in several pieces and, in the example shown, consists of two supporting bodies 16, 17, one of which forms the entire central region 4 of the inner bearing part 1 and a section 2 which is enlarged in diameter compared to this central region 4 at the axial end of the bearing, while the other supporting body 17 consists of an annular element, which at first
  • the channel support 11, which surrounds the inner bearing part 1, consists of an inner sleeve 13 and a channel ring 15, 15 chambers 5, 5 'being formed between the inner sleeve 13 and this channel ring for receiving a steaming agent.
  • the special shape of the supporting bodies 16, 17 and the channel carrier 11 form between the enlarged sections 2, 3 of the inner bearing part 1 and the channel support 11 further chambers 6, 7 from.
  • the chambers 6, 7 are connected to one another by a channel 12 running on the outer contour of the channel ring 15.
  • the channel 12 is particularly good in axonometric 4 can be seen.
  • the inner bearing part 1, like the channel support 11, is partially surrounded by an elastomer 9, 9 'and connected to it by vulcanization
  • FIGS. 3 to 5 The special design of the channel carrier 11 is once again illustrated by FIGS. 3 to 5.
  • the inner sleeve 13 of the channel carrier 11 can be seen, which is connected by vulcanization with an elastomer 14 and with the annular channel ring 15 between the channel ring 15 and the Inner sleeve 13 are steam chamber 5, 5 'formed.
  • These chambers 5, 5' are connected to at least one of the chambers 6 and 7 which form between the supporting body 16 and the channel support 11 during bearing assembly at the axial ends of the bearing 4
  • the inner sleeve 13 of the channel carrier 11 has an outer contour with an approximately square cross-section.This outer contour determines the characteristic behavior of the bearing.
  • the special design of the bearing enables the characteristic behavior without changing the Inner geometry of the
  • Varying inner bearing part 1 This is a significant advantage of this modular Embodiment of the rubber bearing.
  • the storage properties such as steam behavior and identification behavior, are mainly determined by the design of the channel carrier 11, in particular the outer contour of its inner sleeve 13 and the channel 12.
  • FIG. 6 again shows the formation of the upper one according to FIG.
  • the support body 16 forms the entire central region 4 of the inner bearing part 1 and the axial termination of the one bearing end. This axial closure is enlarged in diameter compared to the central area 4.
  • the supporting body 16 is surrounded by vulcanization with an elastomer 18 and an outer ring 19 forming a sealing lip.
  • a shoulder 20 is provided on the area 4 with a reduced diameter in the vicinity of the axial termination.
  • the channel support 11 of the bearing is fixed in the axial direction on this shoulder.
  • the second support body 17, which together with the support body 16 forms the bearing inner part 1, is shown again as a detail in FIG. This is a ring which can be pushed onto the central region 4 formed by the supporting body 16 and which is likewise surrounded by vulcanization with an elastomer 18 and an outer ring 19.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Support Of The Bearing (AREA)

Abstract

L'invention concerne un palier métallo-caoutchouté à amortissement axial, qui comprend une partie intérieure (1) en plusieurs morceaux, un élastomère (9,9') entourant par sections la partie intérieure (1) et lié à elle par vulcanisation, des chambres (5,5',6,7) pour recevoir un agent d'amortissement, un support de canal (11) avec au moins un canal d'agent d'amortissement (12) permettant à l'agent d'amortissement entre les chambres (5,6,7), ainsi qu'un manchon de palier (10) sensiblement cylindrique qui reçoit les parties de palier précitées. La partie intérieure (1) présente au niveau des extrémités axiales du palier une section (2,3) dont le diamètre est augmenté par rapport à une zone médiane (4) de ladite partie intérieure (1). L'invention se caractérise en ce qu'il est prévu entre les sections (2,3) de la partie intérieure (1), au diamètre augmenté, un support de canal (11) avec des chambres (5,5') pour l'agent d'amortissement. Ce support de canal est entouré d'un manchon intérieur (13), d'un élastomère (14) lié au manchon intérieur par vulcanisation et d'un anneau (15) entourant le manchon intérieure (13) et l'élastomère et lié à eux également par vulcanisation. Dans le contour extérieur de cet anneau, il est pratiqué au moins une rainure qui forme, entre l'anneau (15) et le manchon de palier (10), au moins un canal (12).
EP00956114A 1999-08-04 2000-08-02 Palier metallo-caoutchoute a amortissement axial Ceased EP1117944A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19936014 1999-08-04
DE19936014A DE19936014C2 (de) 1999-08-04 1999-08-04 Gummilager mit axialer Dämpfung
PCT/DE2000/002556 WO2001011256A1 (fr) 1999-08-04 2000-08-02 Palier metallo-caoutchoute a amortissement axial

Publications (1)

Publication Number Publication Date
EP1117944A1 true EP1117944A1 (fr) 2001-07-25

Family

ID=7916698

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00956114A Ceased EP1117944A1 (fr) 1999-08-04 2000-08-02 Palier metallo-caoutchoute a amortissement axial

Country Status (4)

Country Link
US (1) US6651965B1 (fr)
EP (1) EP1117944A1 (fr)
DE (1) DE19936014C2 (fr)
WO (1) WO2001011256A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10118229B4 (de) 2001-04-11 2007-03-29 ZF Lemförder Metallwaren AG Hydraulisch dämpfendes Buchsenlager
DE10157144A1 (de) * 2001-11-22 2003-06-05 Freudenberg Carl Kg Hydraulisch dämpfende Gummibuchse
FR2841621B1 (fr) 2002-07-01 2004-09-24 Cf Gomma Spa "dispositif d'articulation hydroelastique a effet axial"
DE10359340A1 (de) 2003-12-16 2005-07-28 Zf Friedrichshafen Ag Hydraulisch dämpfendes Buchsenlager
CA2533817C (fr) * 2005-01-26 2012-12-18 The Pullman Company Support de corps avec amortissement hydraulique et element de construction boulonne
US8110651B2 (en) 2008-01-11 2012-02-07 Serina Therapeutics, Inc. Multifunctional forms of polyoxazoline copolymers and drug compositions comprising the same
WO2009091973A2 (fr) * 2008-01-16 2009-07-23 Z F Group North American Operations, Inc. Douille hydraulique
US9038997B2 (en) 2008-02-05 2015-05-26 Cooper-Standard Automotive Inc. Axially damped hydraulic mount assembly
US9765845B2 (en) 2008-02-05 2017-09-19 Cooper-Standard Automotive Inc. Axially damped hydraulic mount assembly
US8091871B2 (en) * 2008-02-05 2012-01-10 Cooper-Standard Automotive Inc. Axially damped hydraulic mount assembly
KR102083206B1 (ko) * 2013-10-25 2020-03-02 현대모비스 주식회사 부시 조립장치
JP2017096354A (ja) * 2015-11-20 2017-06-01 東洋ゴム工業株式会社 防振装置
US10086645B2 (en) * 2016-12-02 2018-10-02 Zhuzhou Times New Material Technology Co., Ltd. Hydraulic bushing and rail vehicle

Family Cites Families (10)

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Publication number Priority date Publication date Assignee Title
JPH0225947Y2 (fr) * 1985-09-26 1990-07-16
FR2659177B1 (fr) 1990-03-01 1992-09-04 Merlin Gerin Capteur de courant pour un declencheur electronique d'un disjoncteur electrique.
FR2659711B1 (fr) * 1990-03-13 1994-08-26 Peugeot Support hydroelastique.
JP2883742B2 (ja) * 1990-12-28 1999-04-19 東海ゴム工業 株式会社 流体封入式筒型マウント
US5413319A (en) 1994-08-10 1995-05-09 Gencorp Inc. Fluid damped bushing
JPH08177945A (ja) * 1994-12-21 1996-07-12 Tokai Rubber Ind Ltd 流体封入式筒型防振装置
JP3477920B2 (ja) * 1995-06-23 2003-12-10 東海ゴム工業株式会社 流体封入式防振支持体
DE19729290C2 (de) * 1996-09-26 2002-03-14 Mannesmann Boge Gmbh Hydraulisch dämpfendes Gummilager
DE19713003A1 (de) * 1997-03-27 1998-10-01 Lemfoerder Metallwaren Ag Hülsengummifeder mit hydraulischer Dämpfung
JPH1163085A (ja) 1997-08-25 1999-03-05 Kinugawa Rubber Ind Co Ltd 液体封入式防振マウント及びその製造方法

Non-Patent Citations (1)

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Title
See references of WO0111256A1 *

Also Published As

Publication number Publication date
WO2001011256A1 (fr) 2001-02-15
DE19936014A1 (de) 2001-03-15
US6651965B1 (en) 2003-11-25
DE19936014C2 (de) 2003-04-03

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