EP1409887A1 - Silentbloc a element de renforcement - Google Patents

Silentbloc a element de renforcement

Info

Publication number
EP1409887A1
EP1409887A1 EP01986335A EP01986335A EP1409887A1 EP 1409887 A1 EP1409887 A1 EP 1409887A1 EP 01986335 A EP01986335 A EP 01986335A EP 01986335 A EP01986335 A EP 01986335A EP 1409887 A1 EP1409887 A1 EP 1409887A1
Authority
EP
European Patent Office
Prior art keywords
bearing
edges
elements
rubber bearing
stiffening
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.)
Withdrawn
Application number
EP01986335A
Other languages
German (de)
English (en)
Inventor
Helmut Kammel
Bernd KÜMPER
Jim Robinson
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 EP1409887A1 publication Critical patent/EP1409887A1/fr
Withdrawn legal-status Critical Current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
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
    • F16F1/3842—Method of assembly, production or treatment; Mounting thereof
    • 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
    • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
    • F16F1/387—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type comprising means for modifying the rigidity in particular directions
    • F16F1/3873—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type comprising means for modifying the rigidity in particular directions having holes or openings

Definitions

  • the invention relates to a rubber bearing with one or more stiffening elements vulcanized into the elastomer of the bearing body, the approximately cylindrical stiffening element or elements consisting of one or more inserts.
  • the or possibly the stiffening elements are arranged in the elastomer around the bearing axis and stiffen the bearing in particular with regard to radially acting forces.
  • they consist of a hard plastic or sheet metal.
  • the deformation characteristics of the bearing can be influenced in a targeted manner. If the bearing has several stiffening elements, these are integrated into the elastomeric bearing body at different distances from the bearing axis.
  • the invention relates to bearings in which the stiffening elements have adjacent axially parallel edges due to their shape or, in the case of multi-part stiffening elements, due to the arrangement of the insert parts with respect to one another. In the case of multi-part stiffening elements, such edges are provided in the transition area between the individual inserts.
  • the stiffening element is made in one piece, but has a slot or cut running continuously in the longitudinal direction of the bearing, so that at least two axially parallel edges are also formed here. The slot allows opening or opening the bearing body and thus simplifies its assembly on a rod to be stored therein.
  • Rubber bearings are used in large numbers in the automotive industry.
  • the latter serve here, in which the bearing body has a longitudinal slot, for example the storage of
  • Stabilizers that is, torsion bars, which are used to reduce the curvature of the vehicle body in order to avoid oversteering of the vehicle when driving through a curve.
  • plain bearings or conventional bearings without sliding inner bearing surfaces are used to support the stabilizers or torsion bars.
  • a corresponding bearing suitable for the storage of stabilizers is already known from DE 42 04252 AI.
  • the document describes a plastic bearing, which is designed as a plain bearing.
  • the bearing has a continuous slot in the longitudinal direction through the bearing body in a known manner.
  • the stiffening element is formed by an insert made of plastic, which is integrated into the bearing body and has an increased hardness compared to the rest of the bearing body. Due to the longitudinal slot projecting through both the elastomer and the stiffening insert, the bearing can be opened for mounting on a stabilizer by pressing on its half-shells. After placing on the rod, the bearing body closes due to its
  • the bearing is then mounted on the vehicle chassis using a bracket or the like.
  • the bearing shells are preloaded against each other by the bracket surrounding the bearing.
  • a disadvantage of the bearings described so far is that axially running edges of the stiffening element respectively integrated in the bearing body collide with one another after the mounting of the bearing and the subsequent preloading of its bearing shells under gimbal load due to a relative movement between the half shells. This causes the edges to rub against each other, which in turn causes unwanted noise.
  • the stiffening element or elements consist of several insert parts which are prestressed against one another after assembly.
  • the rubber bearing according to the invention consists in a manner known per se from a
  • Bearing body in which one or more, one- or multi-part stiffening elements are vulcanized into the elastomer, which, due to their shape or their multi-part design, have mutually adjacent, axially parallel edges.
  • the inserts which form the stiffening element or elements are designed such that they are in the assembled state of the bearing neighboring and axially parallel edges of the stiffening element or elements have a non-linear, complementary edge profile.
  • the gaps formed between the edges due to their profiling are filled with the elastomer.
  • the elastomer that settles between the edges reliably prevents the edges from lining up even when the bearing is subjected to greater gimbal loads.
  • the mutually adjacent, that is to say adjacent, edges of the insert parts forming the stiffening element or elements have a plurality of cutouts.
  • these cutouts are each offset with respect to two adjacent edges.
  • the distances between the cutouts are each less than the length of the cutouts in the opposite edge.
  • the contours of both edges mesh with each other like a comb or interlocking, of course with mechanical decoupling due to the elastomer arranged between them.
  • Different profiles are conceivable for forming such toothed edges.
  • the edges can be profiled by approximately rectangular recesses or also sawtooth-shaped, trapezoidal or similar.
  • the interlocking interlocking of the inserts also prevents the cardanic load from axially shifting against each other.
  • the insert parts are also advantageously designed in such a way that the two edges of each part are also profiled complementarily to one another.
  • these can be joined together regardless of which of their axial ends is rotated in the direction of which axial bearing end when they are inserted into the shape used for vulcanization.
  • the elastomer of such a bearing preferably has in the area of one of the transitions between the inserts forming the stiffening element or elements an axial longitudinal slot in order to facilitate the assembly of the bearing.
  • the elastomer enclosing the inserts it is also possible to support the assembly without an axial slot through the elastomer. For example, in a warehouse with one
  • the elastomer has a thin web instead of a continuous slot in the area of the transitions between the two inserts.
  • a stiffening element is quasi as one
  • Cylinder jacket formed, which, however, has an axially extending slot for use as a stabilizer bearing, which enables the bearing to be pressed on or opened.
  • assemblies are arranged according to a further development of the invention in relation to the continuous slot opposite slots or recesses which also extend in some regions in the longitudinal direction. This simplifies the deformation of the entire bearing during assembly.
  • the surfaces of the inserts forming them additionally have radially circumferential stiffening ribs in accordance with an advantageous embodiment of the bearing. Due to their number and dimensioning, there is a further possibility of specifically influencing the deformation characteristics of the bearing, that is to say its identification. To form axial stops, radial flanges can also be formed at the axial ends of the insert parts. It turns out for manufacturing reasons an embodiment of the bearing in which the insert parts have several openings (bores or punched-outs) distributed over their surfaces is advantageous. This is advantageous insofar as it allows the elastomer to pass through these openings during vulcanization. This avoids that an increased pressure is exerted on the stiffening elements during vulcanization and these are deformed in an undesired manner.
  • the usually approximately cylindrical stiffening elements can have flattened areas on their circumference due to a corresponding design of the inserts forming them.
  • bearings are created for special purposes with different identifications in relation to their scope.
  • the bearing body of the bearing according to the invention which essentially consists of the elastomer, can also be vulcanized onto a metallic inner part or have one or more sliding areas on the inner sides to form a sliding bearing.
  • a stiffening element arranged in the radially outer region of the bearing body and profiled in the manner shown can also form a housing or an outer sleeve for the bearing.
  • Figure 1 A two-part stiffening element for the bearing according to the invention
  • Figure 2 A rubber bearing with a stiffening element according to Figure 1 in the slightly open state
  • Figure 3 The rubber bearing according to Figure 2 in the closed (assembled) state
  • Figure 4 A one-piece stiffening element for the rubber bearing according to the invention.
  • FIG. 1 shows a two-part stiffening element 3 for the bearing according to the invention in a spatial representation.
  • These are, for example, two sheet metal parts 4, 4 'joined together in accordance with the illustration, which in FIG shown together and vulcanized into a vulcanizing mold in the otherwise essentially rubber bearing body 1.
  • the profile of the edges 7, 7 ', 8, 8' of the two inserts 4, 4 'forming the stiffening element 3, which are adjacent to one another in the illustration, that is to say, differing from the prior art, can be clearly seen.
  • these edges 7, 7 ', 8, 8' are profiled in that they have cutouts 11 or cutouts in sections.
  • the profiling in accordance with the basic principle according to the invention, is designed such that the cutouts 11 of the mutually adjacent edges 7, 8 or 7 ', 8' are arranged to be complementary to one another.
  • the distances a between the punched-outs are smaller than the radial extension b of the cutouts 11.
  • the insert parts 4, 4 ′ engage in a comb-like or quasi-interlocking manner.
  • other profiling shapes than those indicated in the illustration for the edges 7, 7 ', 8, 8' are also conceivable for this purpose.
  • the profiled edges 7, 7 ', 8, 8' of the insert parts 4, 4 ' lie against one another. As far as here in this context always from neighboring ones
  • Edges 7, 7 ', 8, 8' and 9, 10 respectively, this takes into account the fact that it is an essential element of the invention that precisely these edges 7, 7 ', 8, 8' and 9 , 10 after the vulcanization of the stiffening element 3 into the elastomer 2 which essentially forms the bearing body 1, no longer touch one another. Rather, it sits between those based on the complementary structuring of the
  • Edges 7, 7 ', 8, 8' or 9, 10 resulting gaps during vulcanization, the later hardening rubber mass and prevents the edges 7, 7 ', 8, 8' or when using the bearing and the resulting gimbal stress 9, 10 and thus the occurrence of friction noises.
  • the two edges 7, 7 'and 8, 8' of each individual part 4 and 4 ' are also profiled in a more complementary manner to one another. This makes it possible to produce an axially symmetrical stiffening part 3 from two identical insert parts 4, 4 'in a manner which is favorable in terms of production technology, by joining the insert parts 4, 4' as shown.
  • the insert parts 4, 4 'it Due to the described design of the inserts 4, 4 'it is completely irrelevant which axial end of the insert parts 4, 4 'coincides with which axial end of the later bearing. When inserting the parts into the vulcanization mold, it is therefore not necessary to pay attention to their axial orientation.
  • the insert parts 4, 4 ' have a plurality of openings 13 in the form of bores or punched-outs on their surfaces. As a result, the rubber can pass from one side of an insert 4 or 4 'through the openings 13 to the other side during vulcanization, and thus the insert parts 4 and 4' better "flow around" on all sides, which in turn reduces forces which lead to undesired deformation of the insert sheets 4 or 4 could lead.
  • FIG. 2 shows the complete rubber bearing with the stiffening element 3 profiled on the adjacent edges (cut edges) 7, 7 ', 8, 8' according to the invention.
  • This is a stiffening element 3 according to the previously explained FIG. 1 consisting of two inserts 4, 4 '.
  • the bearing has a longitudinal slot 6, which of course relates to the stiffening element 3 with one of the transition points between the two inserts forming the stiffening element 3 4, 4 'coincides.
  • the bearing can be easily opened in accordance with the illustration given in FIG. 2. In the open state, the bearing is pushed onto the rod, where it then closes again due to the restoring forces due to its material properties.
  • the bearing With a clamp or the like, the bearing is finally attached to the chassis of a motor vehicle in the case of its use for mounting motor vehicle stabilizers.
  • the bearing half-shells, ie also the half-shells (insert parts 4, 4 ') of the stiffening element 3 embedded therein, are prestressed against one another.
  • Figure 3 shows the bearing in the closed state after assembly, but without showing a clamp that may be used for fastening. It can be clearly seen how the recesses 11 or punched-out portions of the inserts 4, 4 ', which are arranged complementarily to one another, mesh with one another in a comb-like manner. However, they are the gaps formed between them are filled by the elastomer 2 forming the rest of the bearing body 1, so that the parts do not come into direct contact with their edges 7, 7 ', 8, 8' or 9, 10 even with a larger gimbal load. This avoids a stringing together of the parts and consequently a noise development resulting therefrom in bearings according to the prior art.
  • the inserts 4, 4 'and 5 may have a radial flange on their axial end faces, which deviates from the illustrated embodiment and which forms an axial stop to limit axial forces.
  • the bearing is a plain bearing, it also has correspondingly designed sliding surfaces on its inner sides, which are also integrated into the bearing body 1 in the course of the vulcanization.
  • FIG. 4 shows a one-piece embodiment of the stiffening element 3 '.
  • the insert 5 has in its peripheral surface on the side opposite the profiled edges 9, 10 a plurality of slots or openings 12, 12' running in the longitudinal direction. This significantly simplifies the deformation of the bearing when it is pushed onto a stabilizer bar, for example.
  • the length and the number of openings 12, 12 ' which are expediently provided for this purpose depend on the material of the insert 5 and its material thickness. These parameters are dependent on the desired deformation behavior of the bearing. LIST OF REFERENCE NUMBERS

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Support Of The Bearing (AREA)
  • Springs (AREA)
  • Vehicle Body Suspensions (AREA)
  • Sliding-Contact Bearings (AREA)
  • Bearings For Parts Moving Linearly (AREA)

Abstract

L'invention concerne un silentbloc, présentant un ou plusieurs éléments de renforcement (3 ; 3') de forme presque cylindrique vulcanisés dans l'élastomère du corps de palier entre la surface intérieure du palier et la surface extérieure du palier. Ces éléments de renforcement (3 ; 3') sont chacun constitués d'une ou de plusieurs parties d'insertion (4, 4' ; 5) s'étendant dans le sens axial. Des éléments de renforcement (3') en une partie et des éléments de renforcement (3) en plusieurs parties présentent respectivement en raison de leur forme et de l'agencement des parties d'insertion (4, 4') des bords (7, 7', 8, 8' ; 9, 10) adjacents, s'étendant parallèlement à l'axe. Selon ladite invention, ces bords adjacents (7, 7', 8, 8' ; 9, 10) présentent chacun un profil de bord linéaire et complémentaire. Des zones intermédiaires formées en raison dudit profil sont remplies dudit élastomère (2) entre les bords (7, 7', 8, 8' ; 9, 10).
EP01986335A 2000-10-05 2001-09-27 Silentbloc a element de renforcement Withdrawn EP1409887A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10049611 2000-10-05
DE10049611A DE10049611C2 (de) 2000-10-05 2000-10-05 Gummilager mit Versteifungselement
PCT/DE2001/003707 WO2002029275A1 (fr) 2000-10-05 2001-09-27 Silentbloc a element de renforcement

Publications (1)

Publication Number Publication Date
EP1409887A1 true EP1409887A1 (fr) 2004-04-21

Family

ID=7658934

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01986335A Withdrawn EP1409887A1 (fr) 2000-10-05 2001-09-27 Silentbloc a element de renforcement

Country Status (7)

Country Link
US (1) US6755405B2 (fr)
EP (1) EP1409887A1 (fr)
JP (1) JP2004510930A (fr)
BR (1) BR0107284B1 (fr)
DE (1) DE10049611C2 (fr)
MX (1) MXPA02004869A (fr)
WO (1) WO2002029275A1 (fr)

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ES2297562T3 (es) 2005-05-12 2008-05-01 Stabitec Stanz-Biegetechnik Gmbh Cojinete, especialmente cojinete de goma.
DE102006006687B4 (de) * 2006-02-14 2014-10-16 Bayerische Motoren Werke Aktiengesellschaft Gummilager für einen Stabilisator im Fahrwerk eines Kraftfahrzeugs
US20090230601A1 (en) * 2008-03-14 2009-09-17 Gm Global Technology Operations, Inc. Biaxial Exhaust Isolator With Dual-Band Reinforcement
JP5386591B2 (ja) * 2010-01-29 2014-01-15 東海ゴム工業株式会社 車両用スタビライザブッシュ
JP5622654B2 (ja) 2011-05-23 2014-11-12 住友理工株式会社 車両用スタビライザブッシュとその製造方法
CN102297201A (zh) * 2011-07-29 2011-12-28 威海利奥泰儆自动化设备有限公司 一种滚轮花键副
DE102012206453B4 (de) 2012-04-19 2019-02-28 Zf Friedrichshafen Ag Elastomerlager zur Lagerung eines als Stabilisator ausgebildeten stabförmigen Lagerelements
CN102635656A (zh) * 2012-05-04 2012-08-15 无锡市中捷减震器有限公司 发动机支架减震橡胶内嵌装置
AU2013359965B2 (en) * 2012-12-11 2018-06-07 Rotacaster Wheel Limited Axel bush
US9702411B2 (en) * 2014-04-10 2017-07-11 Roller Bearing Company Of America, Inc. Bearing assembly with split outer ring having interference fit tabs and method of assembly of bearing
CN104358763A (zh) * 2014-10-29 2015-02-18 无锡市中捷减震器有限公司 一种用于汽车悬挂减震系统的弹簧垫圈
EP3242803B1 (fr) 2015-01-06 2023-06-07 Rotacaster Wheel Pty Ltd Composant de châssis de roue
DE102015016454B4 (de) * 2015-12-21 2018-02-08 Jörn GmbH Elastisches Lager
DE102016223615A1 (de) 2016-11-29 2018-05-30 Schaeffler Technologies AG & Co. KG Stabilisatorlager für ein Fahrwerk
CN108463647B (zh) * 2016-12-15 2020-06-02 住友理工株式会社 筒形防振装置
DE102018108029A1 (de) * 2018-04-05 2019-10-10 Boge Elastmetall Gmbh Gummilager
GB201805838D0 (en) * 2018-04-09 2018-05-23 Dtr Vms Ltd Bush
DE102018113503A1 (de) * 2018-06-06 2019-12-12 Vibracoustic Gmbh Aggregatelager

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JPS6122944U (ja) * 1984-07-16 1986-02-10 トヨタ自動車株式会社 ブッシュ組立体
FR2683874B1 (fr) * 1991-11-15 1995-05-05 Hutchinson Palier de barre de torsion.
DE4204252C2 (de) * 1992-02-13 1996-09-05 Lemfoerder Metallwaren Ag Kunststofflager für Stabilisatoren in Kraftfahrzeugen
DE4309425C1 (de) * 1993-03-24 1994-06-01 Lemfoerder Metallwaren Ag Gummilager für den Mittelzapfen einer Blattfederaufhängung in einem Kraftfahrzeug
DE4413666C1 (de) * 1994-04-20 1995-06-14 Lemfoerder Metallwaren Ag Kunststofflager für Stabilisatoren in Kraftfahrzeugen
JPH08219210A (ja) 1995-02-13 1996-08-27 Tokai Rubber Ind Ltd 防振支持体
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Also Published As

Publication number Publication date
US6755405B2 (en) 2004-06-29
US20020186905A1 (en) 2002-12-12
MXPA02004869A (es) 2003-01-28
BR0107284A (pt) 2002-07-30
WO2002029275A1 (fr) 2002-04-11
JP2004510930A (ja) 2004-04-08
BR0107284B1 (pt) 2010-06-29
DE10049611C2 (de) 2002-08-29
DE10049611A1 (de) 2002-04-25

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