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WO2004088165A1 - Coussinet de palier pourvu d'un element ressort - Google Patents

Coussinet de palier pourvu d'un element ressort Download PDF

Info

Publication number
WO2004088165A1
WO2004088165A1 PCT/EP2004/003369 EP2004003369W WO2004088165A1 WO 2004088165 A1 WO2004088165 A1 WO 2004088165A1 EP 2004003369 W EP2004003369 W EP 2004003369W WO 2004088165 A1 WO2004088165 A1 WO 2004088165A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring element
bearing bush
recess
inner sleeve
support body
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
PCT/EP2004/003369
Other languages
German (de)
English (en)
Inventor
Jérôme Kieffer
Philippe Drumel
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.)
Trelleborg Automotive Germany GmbH
Original Assignee
Trelleborg Automotive Technical Centre 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 Trelleborg Automotive Technical Centre GmbH filed Critical Trelleborg Automotive Technical Centre GmbH
Publication of WO2004088165A1 publication Critical patent/WO2004088165A1/fr
Anticipated expiration legal-status Critical
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
    • F16F13/1481—Units of the bushing type, i.e. loaded predominantly radially characterised by features of plastic springs, e.g. presence of cavities or stiffeners; characterised by features of flexible walls of equilibration chambers, i.e. membranes
    • 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
    • F16F3/00—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic
    • F16F3/08—Spring units consisting of several springs, e.g. for obtaining a desired spring characteristic with springs made of a material having high internal friction, e.g. rubber
    • F16F3/087—Units comprising several springs made of plastics or the like material
    • F16F3/093—Units comprising several springs made of plastics or the like material the springs being of different materials, e.g. having different types of rubber

Definitions

  • the invention relates to a bearing bush with an inner sleeve and an outer sleeve and a support body arranged between the inner and outer sleeve made of elastomeric material, wherein the support body has at least a first recess and a second recess, which are arranged on opposite sides of the inner sleeve, each in the first recess and the second recess a spring element cooperating with the inner sleeve is inserted and the recesses are filled with a hydraulically damping liquid and are connected to one another via an overflow channel.
  • Bearing bushes of this type are used in particular in vehicle construction and have an elastic supporting body with which vibrations of a component subject to vibration are damped. Hydraulic damping bushes are also known, in which hydraulic damping takes place through chambers filled with hydraulic fluids, which are connected via an overflow channel.
  • EP 1 217 249 A1 describes a hydraulically damping bearing bush which has an inner and an outer sleeve, the inner sleeve being supported by an elastic support body.
  • the elastic support body has cutouts which form chambers filled with hydraulic fluid.
  • a limiting element is used in the chambers, which serves as a stop for the inner bush.
  • DE 197 29 290 C2 shows a hydraulically damping rubber bearing with an inner tube and an outer tube.
  • a rubber part is arranged between the inner tube and the outer tube, in which chambers are formed which are filled with a damping agent.
  • Stop bodies are arranged in the chambers and are connected to one another via a semi-ring-shaped element. The element serves in particular to form an overflow channel connecting the chambers.
  • the radial stiffness can be set differently depending on the radial direction. For example, it may be necessary for the radial stiffness in the Y direction to be lower than in the X direction.
  • the object of the present invention is to propose a bearing bush in which the radial rigidity is adjustable.
  • a bearing bush of the type mentioned at the outset in that the spring element is essentially planar and is supported in its central region on the inner sleeve and on the edge side with its end regions on the outer sleeve and a cylindrical insert vulcanized into the support body is provided, which has supporting stops which cooperate with the end regions of the spring elements.
  • the bearing bush By inserting the spring elements into the respective recesses, the bearing bush is given a different, in particular increased, radial rigidity in the direction of action of the spring elements.
  • the spring element is supported with its central area on the inner sleeve and with its end areas on the inside of the outer sleeve.
  • An insert vulcanized into the support body makes it possible for the end regions of the spring elements to be supported on stops of this insert, thereby ensuring that the spring elements are held securely.
  • This construction makes it possible to absorb a radial load from the spring element, the spring element expanding into the chamber between the outer sleeve and the spring element under radial load.
  • the spring element acts as a stop and limits the deflection movement of the inner sleeve.
  • Different design of the spring element in relation to its shape and the material used different radial stiffness can be achieved for the bearing bushes for different applications.
  • the basic design of the bearing bush does not have to be changed.
  • An elastic rubber layer is advantageously arranged between the inner sleeve and the spring element.
  • an elastic buffer is arranged in a chamber, which supports the spring element in the radial direction.
  • This elastic buffer is produced together with the support body in a vulcanization process.
  • a recess is made in the vulcanizate in the area of the later positions of the spring elements, so that the spring elements can be inserted on both sides of the inner sleeve between the inner sleeve and the elastic buffers.
  • Figure 1 is a schematic cross section through a bearing bush according to the present invention.
  • FIG. 2 shows a longitudinal section through a bearing bush according to the invention
  • 3 shows a section along the line III-III in FIG. 2;
  • FIG. 7 shows a section along the line Vll-Vll in FIG. 6.
  • FIG. 1 shows a cross section of a bearing bush 10 according to the invention in a schematic representation.
  • the bearing bush 10 comprises an inner sleeve 11 which has an opening into which a bearing part (not shown) can be inserted.
  • the inner sleeve 11 is made of metal, for example.
  • This inner sleeve 11 is arranged within an outer sleeve 12.
  • An elastic support body 13 is inserted between the outer sleeve 12 and the inner sleeve 11, which supports the inner sleeve 11.
  • the elastic support body 13 has a recess 14 into which a spring element 16 is inserted, as a result of which a chamber 18 is formed between the outer sleeve 12 and the spring element 16.
  • This spring element 16 interacts with the inner sleeve 11 and the outer sleeve 12, the spring element 16 abutting the inner sleeve 11 in a contact area 23 in its central region and with its end regions 24 being supported on the outer sleeve 12 at the edge. With a radial load, the spring element 16 is deflected into the chamber 18 by bending.
  • a second recess 15 is further arranged in the elastomeric support body 13. In this second recess 15, a further spring element 17 is inserted, which works in the opposite direction in the event of radial loading in the same way as the spring element 16 in the first recess 14.
  • the spring element 17 forms a second chamber 19 with the outer sleeve 12 Recesses formed chambers 18, 19 are not shown here
  • Overflow channel 20 connected and are filled with a hydraulic fluid. With radial loading in one direction, the liquid located in the corresponding recess can flow via the overflow channel 20 into the other recess, as a result of which an improved damping behavior is achieved.
  • FIG. 2 shows a longitudinal section through a bearing bush 10 according to the invention.
  • the bearing bush 10 comprises an inner sleeve 11 and an outer sleeve 12.
  • the inner sleeve 11 has radially protruding beads 11a in its central region.
  • spring elements 16, 17 are arranged, with which a desired radial rigidity can be set.
  • FIG. 3 shows a cross section of the bearing bush 10 along the section line III-III according to FIG. 2.
  • the inner sleeve 11 is surrounded by an elastic support body 13 which has a first recess 14 and a second recess 15.
  • the support body 13 and the inner sleeve 11 are arranged within the outer sleeve 12.
  • the inner sleeve 11 is supported in the area of the recesses 14 and 15 by the spring elements 16, 17.
  • the spring elements 16, 17 each abut the inner sleeve 11 in a contact area 23.
  • a thin rubber layer 21 is arranged between the spring elements 16, 17 and the inner sleeve 11.
  • the spring elements 16, 17 each form a chamber 18, 19 with the outer sleeve 12 on the corresponding side of the bearing bush 10.
  • the recesses 14 and 15 including the chambers 18, 19 are connected to one another via an overflow channel 20 and filled with hydraulic fluid.
  • the corresponding spring element 16 With one-sided radial Load, the corresponding spring element 16 is pressed into the associated chamber 18, whereby the liquid therein is pressed via the overflow channel 20 into the recess 15 and the chamber 19 on the other side of the bearing bush 10. Hydraulic damping is achieved by the liquid column vibrating in the overflow channel 20.
  • a cylindrical insert 25 which is shown in FIG. 4, is received in the outer sleeve 12.
  • the insert 25 has spaced support rings 26a, 26b, which are connected by struts 27 arranged offset in the circumferential direction.
  • the struts 27 serve as a support for the spring elements 16, 17 which rest with their end regions 24 on the struts 27.
  • insert webs 22 running in the circumferential direction are provided on the insert 25.
  • FIG. 5 shows a spring element 16, 17 according to the invention.
  • This spring element 16, 17 lies with the contact area 23 on the inner sleeve 11. With the end regions 24, it is supported on the struts 27 of the insert 25.
  • the support body 13 is vulcanized into the insert 25.
  • the insert webs 22 which are arranged in the region of the overflow channels 20 and are vulcanized into the support body 13 serve as reinforcements.
  • the bearing bush 10 is characterized by a simple structure.
  • FIGS. 6 and 7. A further embodiment is shown in FIGS. 6 and 7.
  • an elastic buffer 28 is in each case in the chambers 18 and 19 on the cylindrical inlet. vulcanized set.
  • the spring element 16, 17 rests in its central region on the inner sleeve 11 and on the opposite side of the spring element on the elastic buffer 28.
  • the end regions of the spring element 16, 17 rest against the edge on the inside of the outer sleeve 12, in particular on the struts 27 of the cylindrical insert 25, which is supported on the outer sleeve 12.
  • the elastic buffers 28 are produced together with the support body 13 in a vulcanization process.
  • a recess is made in the vulcanized body at the later position of the spring elements 16, 17.
  • the thickness of the recess is preferably less than the thickness of the spring elements 16, 17.
  • the elastic buffers 28 are preloaded in the radial direction by the insertion of the spring elements 16, 17 and give the bearing bush additional rigidity in the radial direction. The radial stiffness can thus be adjusted by simply changing the thickness of the spring elements 16, 17 without changing the structure of the bearing bush and in particular of the vulcanized body.
  • the elastic buffers 28 enable the individual movements to be decoupled.
  • the elastic buffers 28 only support a radial movement of the inner sleeve 11. If the inner sleeve 11 is rotated or tilted with respect to the axial axis of the bearing bush, the friction acts due to the twisting of the inner sleeve 11 only on the spring elements 16 and 17 and not on the elastic buffers 28, so that these frictional forces from the spring elements 16, 17 are included.
  • the friction between the inner sleeve 11 and the spring elements 16, 17 is low.
  • this design prevents the generation of noise.
  • noises occur in particular when there is friction between rubber and metal parts. Since, in the embodiment according to the invention, when the inner sleeve rotates, the metallic inner sleeve rubs against the spring elements 16, 17 made of plastic, noise is prevented.
  • End areas of cylindrical insert a, b support rings

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 coussinet de palier (10) comprenant un manchon interne (11) et un manchon externe (12) ainsi qu'un corps de support (13) constitué d'un matériau élastomère et disposé entre le manchon interne (11) et le manchon externe (12). Ce corps de support (13) comporte au moins un premier évidement (14) ainsi qu'un deuxième évidement (15) qui se trouvent au niveau de côtés opposés du manchon interne (11). Un élément ressort (16, 17) qui coopère avec le manchon interne (11) est respectivement disposé dans le premier évidement (14) ainsi que dans le deuxième évidement (15). Lesdits évidements (14, 15) sont remplis d'un liquide d'amortissement hydraulique et sont reliés l'un à l'autre par l'intermédiaire d'un conduit de trop-plein (20). L'élément ressort (16, 17) est configuré de manière sensiblement plane et est en appui en zone centrale contre le manchon interne (11) et en périphérie, aux niveau de ses zones terminales (24), contre le manchon externe (12). Un insert cylindrique (25) vulcanisé dans le corps de support (13) comporte des butées de support (26, 27) qui coopèrent avec les zones terminales des éléments ressort (16, 17), ce qui permet d'ajuster la rigidité radiale du coussinet de palier.
PCT/EP2004/003369 2003-04-03 2004-03-30 Coussinet de palier pourvu d'un element ressort Ceased WO2004088165A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10315247.4 2003-04-03
DE2003115247 DE10315247B4 (de) 2003-04-03 2003-04-03 Lagerbuchse mit Federelement

Publications (1)

Publication Number Publication Date
WO2004088165A1 true WO2004088165A1 (fr) 2004-10-14

Family

ID=33016145

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/003369 Ceased WO2004088165A1 (fr) 2003-04-03 2004-03-30 Coussinet de palier pourvu d'un element ressort

Country Status (2)

Country Link
DE (1) DE10315247B4 (fr)
WO (1) WO2004088165A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116951029A (zh) * 2023-07-13 2023-10-27 株洲时代瑞唯减振装备有限公司 一种用于对橡胶堆实施定向刚度调节和减振的方法

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006052917B4 (de) * 2006-11-08 2012-07-19 Vorwerk Autotec Gmbh & Co. Kg Hydrolager mit Wegbegrenzung
DE102006052918B4 (de) * 2006-11-08 2012-12-06 Vorwerk Autotec Gmbh & Co. Kg Axial vorgespanntes Hydrolager
DE102007038493B4 (de) * 2007-08-14 2012-10-04 Zf Friedrichshafen Ag Elastomeres Buchsenlager mit hydraulischer Dämpfung
DE102007044667A1 (de) * 2007-09-18 2009-04-09 Zf Friedrichshafen Ag Hydrobuchse mit separaten Blähkammern
DE102016215678A1 (de) 2016-08-22 2018-02-22 Schaeffler Technologies AG & Co. KG Lager

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2555688A1 (fr) * 1983-11-25 1985-05-31 Ouest Cie Support elastique a faible raideur, notamment pour vehicule automobile
DE19729290A1 (de) * 1996-09-26 1998-04-16 Mannesmann Boge Gmbh Hydraulisch dämpfendes Gummilager
EP1217249A1 (fr) 2000-12-22 2002-06-26 Hutchinson Manchon antivibratoire et véhicule automobile comportant un tel manchon
EP1348885A1 (fr) * 2002-03-25 2003-10-01 Paulstra CRC Manchon à amortissement hydraulique

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2703038C3 (de) * 1977-01-26 1981-09-17 Metzeler Kautschuk GmbH, 8000 München Vorspannbares Lagerelement
DE7737712U1 (de) * 1977-12-10 1981-02-12 Metzeler Kautschuk Gmbh, 8000 Muenchen Vorspannbares Lagerelement
JPS60208652A (ja) * 1984-03-30 1985-10-21 Tokai Rubber Ind Ltd 車両サスペンシヨン用ゴムブツシユ
DE4131922A1 (de) * 1990-10-03 1992-04-09 Phoenix Ag Hydrobuchse

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2555688A1 (fr) * 1983-11-25 1985-05-31 Ouest Cie Support elastique a faible raideur, notamment pour vehicule automobile
DE19729290A1 (de) * 1996-09-26 1998-04-16 Mannesmann Boge Gmbh Hydraulisch dämpfendes Gummilager
DE19729290C2 (de) 1996-09-26 2002-03-14 Mannesmann Boge Gmbh Hydraulisch dämpfendes Gummilager
EP1217249A1 (fr) 2000-12-22 2002-06-26 Hutchinson Manchon antivibratoire et véhicule automobile comportant un tel manchon
EP1348885A1 (fr) * 2002-03-25 2003-10-01 Paulstra CRC Manchon à amortissement hydraulique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116951029A (zh) * 2023-07-13 2023-10-27 株洲时代瑞唯减振装备有限公司 一种用于对橡胶堆实施定向刚度调节和减振的方法

Also Published As

Publication number Publication date
DE10315247B4 (de) 2005-05-25
DE10315247A1 (de) 2004-10-21

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