WO2016092114A1 - Palier à roulement - Google Patents

Palier à roulement Download PDF

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Publication number
WO2016092114A1
WO2016092114A1 PCT/EP2015/079602 EP2015079602W WO2016092114A1 WO 2016092114 A1 WO2016092114 A1 WO 2016092114A1 EP 2015079602 W EP2015079602 W EP 2015079602W WO 2016092114 A1 WO2016092114 A1 WO 2016092114A1
Authority
WO
WIPO (PCT)
Prior art keywords
damping layer
ring
rolling bearing
inner ring
outer ring
Prior art date
Application number
PCT/EP2015/079602
Other languages
German (de)
English (en)
Inventor
Bernd Bertsche
Sabine SANZENBACHER
Original Assignee
Universität Stuttgart
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 Universität Stuttgart filed Critical Universität Stuttgart
Publication of WO2016092114A1 publication Critical patent/WO2016092114A1/fr

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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element

Definitions

  • the invention relates to a rolling bearing, in particular for a vehicle transmission, with an inner ring, an outer ring and a plurality of rolling elements arranged between the inner ring and the outer ring. Furthermore, the invention relates to a bearing assembly with a housing and a component to be stored.
  • primary measures namely the reduction of the structure-borne sound excitation itself, or secondary measures, such as the reduction of structure-borne sound transmission or sound radiation, can be carried out.
  • DE 1 966 463 A1 discloses a sound-damped bearing, e.g. As a roller or ball bearing, described, which is used between a rotor and a bearing housing. Between the parts of the bearing and the rotor, a sound damping arrangement of two or more elastic bodies is provided.
  • a shock and vibration damper for the suspension of drives in automobiles is described in DE 16 55 607 A1.
  • fillings are provided from a plurality of separately prepared and compacted metal wire cloth winding cushions.
  • a vibration-damping bearing for fixing a housing of a steering system on a vehicle-fixed component, which has an insulating element of single or multi-layer, mesh-forming metal knitted fabric is described in DE 10 2009 000 566 A1.
  • a flexible element in the radial direction is arranged, which consists of at least one corrugated in the radial direction or provided with projections ring element.
  • flexible elements are provided for vibration damping.
  • JP 2005/024046 A a bearing element with an outer ring and an inner ring is described, which has a damping element outside the outer ring or inside the inner ring.
  • a bearing arrangement with a layer of a damping material is also known from DE 10 2010 061 920 B3.
  • the damping layer divides the outer ring or the inner ring or the adapter ring into two independent parts, the propagation of the vibrations acting on one of the two independent parts is reduced to the other part.
  • the at least one damping layer From the vibration damping material so on the one hand, the propagation of the structure-borne sound waves is hindered, thus achieving an insulation of the vibrations.
  • vibration energy is converted into heat and thus in an acoustically irrelevant form of energy, which corresponds to a damping or absorption of the vibrations.
  • the damping layer which shares the Au IZring and / or the inner ring and / or the adapter ring into two independent parts and thereby prevents contact or contact of the two parts with each other, the occurrence of sound bridges is avoided, so that the structure-borne sound transmission can take place exclusively via the damping layer.
  • the damping layer on the one hand provides a sound resistance and on the other hand, the existing body sound energy, which acts on the rolling bearing according to the invention, absorbed by the damping layer.
  • the rolling bearing according to the invention requires only a relatively low cost compared to other solutions for insulation and damping of vibrations or structure-borne noise.
  • the damping layer is arranged opposite to the independent parts of the outer ring and / or the inner ring or the adapter ring or designed so that on the Au IZring and / or the inner ring or the adapter ring radial forces and axial forces are transferable.
  • the rolling bearing according to the invention can transmit forces both in the axial and in the radial direction.
  • this is advantageous in gearbox construction, since due to the use of helical gearwheels, axial forces must frequently be accommodated in addition to the radial forces which occur in any case.
  • the damping layer is formed of a plurality of metal wires pressed into each other.
  • metal wires pressed into one another for example in the form of a woven fabric, a mesh, a knitted fabric, a knitted fabric, a tangle or another structure made of metal wires results in a multiplicity of joints, contact points and parting surfaces, resulting in a high degree of friction and thus a high energy dissipation within the damping layer is achieved.
  • a woven fabric, a mesh, a knitted fabric, a knitted fabric, a tangle or another structure made of metal wires results in a multiplicity of joints, contact points and parting surfaces, resulting in a high degree of friction and thus a high energy dissipation within the damping layer is achieved.
  • the vibrations are damped.
  • metal wires damping layer reflections of the structure-borne sound waves, which can lead to an acoustic short circuit. Due to these reflection processes at boundary layers, for example at the transition between the individual wires or at the transition from the solid material to the damping layer, a further strong sound insulation is achieved.
  • a further advantage of the use of metal wires au au term is that in this way the rigidity of the entire bearing is reduced only slightly.
  • the damping layer consists of a plastic or rubber.
  • a plurality of damping layers are arranged next to one another in the radial direction.
  • the at least one damping layer is integrated into the outer ring of the rolling bearing.
  • a further advantageous embodiment of the invention may consist in that the damping layer is compressed, and that the thickness of the at least one damping layer before pressing slightly is greater than a distance between the two independent parts of the outer ring and / or the inner ring and / or the adapter ring. In this way, there is a compression and a bias of the damping layer, whereby the rigidity of the entire bearing increases.
  • a structurally simple embodiment for enabling the transmission of axial forces arises when on at least one lateral edge of the Au texs and / or the inner ring or the adapter ring shoulders are formed on which the damping layer is applied.
  • the damping layer is roof-shaped or V-shaped, then axial forces can be absorbed in both directions.
  • a bearing assembly with a housing, a component to be stored and a rolling bearing according to the invention is specified.
  • Such a bearing assembly is particularly suitable for use in a vehicle transmission for insulation and damping of vibrations and the resulting structure-borne noise.
  • FIG. 1 shows a first embodiment of a bearing assembly with a rolling bearing according to the invention.
  • FIG. 2 is a more detailed illustration of a first embodiment of a rolling bearing of the bearing assembly of Fig. 1;
  • Fig. 3 is a more detailed illustration of a second embodiment of a rolling bearing of the bearing assembly of Fig. 1;
  • Fig. 4 is a more detailed illustration of a third embodiment of a rolling bearing of the bearing assembly of Fig. 1;
  • Fig. 5 is a more detailed view of a fourth embodiment of a rolling bearing of the bearing assembly of Fig. 1;
  • Fig. 6 is a more detailed illustration of a fifth embodiment of a rolling bearing of the bearing assembly of Fig. 1;
  • Fig. 7 is a more detailed illustration of a sixth embodiment of a rolling bearing of the bearing assembly of Fig. 1;
  • FIG. 8 shows a second embodiment of a bearing arrangement with a rolling bearing according to the invention
  • Fig. 9 is a more detailed illustration of a first embodiment of an adapter ring of the bearing assembly of Fig. 8;
  • Fig. 10 is a more detailed illustration of a second embodiment of an adapter ring of the bearing assembly of Fig. 8;
  • Fig. 1 1 is a more detailed illustration of a third embodiment of an adapter ring of the bearing assembly of Fig. 8;
  • Fig. 12 is a more detailed illustration of a fourth embodiment of an adapter ring of the bearing assembly of Fig. 8;
  • FIG. 13 is a more detailed view of a fifth embodiment of an adapter ring of the bearing assembly of FIG. 8. 1 shows a bearing arrangement 1 which has a housing 2, a component 3 to be stored in the housing 2 and a roller bearing 4.
  • the housing 2 is a transmission housing, in particular for a vehicle transmission, and in the component 3 to be mounted around a shaft on which a gear wheel is located.
  • the rolling bearing 4 may be a ball bearing, a roller bearing or any other form of rolling bearing.
  • a double-row embodiment of the rolling bearing 4 shown in single-row in FIG. 1 would also be conceivable. In principle, the rolling bearing 4 could also be used in other applications, ie not only in a vehicle transmission.
  • FIGS. 2 to 7 show six different embodiments of the roller bearing 4. It can be seen that the rolling bearing 4 in a conventional manner an inner ring 5, an outer ring 6 and a plurality of between the inner ring 5 and the Au touchring 6 arranged rolling elements 7 has.
  • the rolling elements 7 are balls, but as mentioned above, other types of rolling elements 7 could be provided.
  • the inner ring 5 is in contact with the component 3, which is not shown in FIGS. 2 to 7, and the outer ring 6 is in contact with the housing 2, likewise not shown.
  • the outer ring 6 of the rolling bearing is located in the outer ring 4 integrates a damping layer 8 consisting of a vibration-damping material or arranged in the outer ring 6.
  • the damping layer 8 which could also be referred to as a damping element or as a damping and insulating element, is arranged in the outer ring 6, that it is divided by the damping layer 8 into two independent parts, namely an inner part 6a and an outer part 6b is. The two parts 6a and 6b are only in contact with each other via the damping layer 8 consisting of the vibration-damping material.
  • the damping layer 8 is designed for insulation and damping of vibrations and the Au tungsring 6 divides into the two independent parts 6 a and 6 b and thus avoids the formation of sound bridges, which are on the rolling elements 7 transmitted to the inner part 6a vibrations transmitted only slightly to the externa ßere part 6b, so that a further transmission of the vibrations to the housing 2 is prevented.
  • the damping layer 8 so vibrations or due to vibrations in the outer ring 6 propagating structure-borne sound waves are hindered or interrupted. Furthermore, a conversion of vibration energy into heat takes place in the damping layer 8, resulting in a damping of the vibrations.
  • the damping layer 8 While in the embodiment of Fig. 2, the damping layer 8 is disposed opposite to the independent parts 6a and 6b of the outer ring 6 that on the Au OWring 6 radial forces are transferable, the damping layer 8 in the embodiment of Fig. 3 so compared to arranged independent parts 6a and 6b of the outer ring 6 that on the outer ring 6 both radial and axial forces are transferable.
  • the damping layer 8 in the embodiment of Fig. 3 so compared to arranged independent parts 6a and 6b of the outer ring 6 that on the outer ring 6 both radial and axial forces are transferable.
  • the damping layer 8 at the lateral edges of the parts 6a and 6b of the outer ring 6 each formed on one side shoulders 10, where the damping layer 8 is applied. If, as in the embodiment of Fig. 3, the shoulders 10 are not provided on both sides, the absorption of axial forces in one direction is possible.
  • an embodiment of the rolling bearing 4 would be conceivable in which only axial forces
  • the shoulders 10 are provided in each case. As a result, axial forces can be absorbed in both directions.
  • the shoulders 10 it would be possible, for example, the shoulders 10 by crimping the outer ring 6, by caulking with the outer ring 6 and / or by pressing the damping layer 8 by means of an additional element, not shown.
  • FIGS. 5 to 7 have in common that the damping layer 8 runs obliquely or at an angle different from 0 ° relative to the central axis of the roller bearing 4. This also makes it possible to absorb axial forces in at least one direction in addition to the radial forces. While in the embodiment of FIG. 5 the damping layer 8 extends continuously in one direction, whereby axial forces can be absorbed in one direction, it is roof-shaped in the embodiments of FIGS. 5 and 6, so that axial forces can be absorbed in both directions. Of course, the roof shape may also be arranged vice versa, ie in a V-shape. In the embodiments of Fig.
  • the externa ßere part 6 b of the Au tungsrings is also made in two parts, in order to simplify the assembly of the rolling bearing 4 with the roof-shaped damping layer 8.
  • the course of the damping layer 8 according to FIG. 5 could also be reversed, ie instead of from bottom left to top right from bottom right to top left, as shown, in order to absorb forces in the other direction.
  • the damping layer 8 is arranged in the outer ring 6.
  • the damping layer 8 in the inner ring 5 and thereby divide it into two independent parts, similar to the two parts 6a and 6b of the outer ring 6.
  • An arrangement of the damping layer 8 in both the outer ring 6 and in the inner ring 5 is conceivable. All other embodiments and developments described herein are of course also suitable for this embodiment, in which the damping layer 8 is alternatively or additionally arranged in the inner ring 5.
  • an adapter ring 9 is provided on the outer circumference of the outer ring 6 of the rolling bearing 4, in which the already described with reference to the figures 2 to 7 damping layer 8 is arranged.
  • the damping layer 8 divides the adapter ring 9 into two independent parts, namely an inner part 9a and an outer part 9b.
  • the embodiment of the adapter ring 9 according to FIG. 9 for the transmission of radial forces and the embodiment of FIGS. 10 to 13 for the transmission of radial and axial forces are provided.
  • the damping layer 8 thus extends continuously over the entire width of the outer ring 6 and the adapter ring 9, while in the embodiments of Figures 3, 4, 10 and 1 1 at the lateral edges of the Au texrings 6 and of the adapter ring 9, in turn, the respective shoulders 10 are formed, against which the damping layer 8 rests.
  • the shoulders 10 are provided on one side of the adapter ring 9, ie on the side of the two parts 9a and 9b, while on the opposite side a shoulder 10 replacing the retaining element 1 1 is screwed to the adapter ring 9 to allow the mounting of the damping layer 8.
  • the embodiment of Fig. 1 1 corresponds in principle to that of Fig. 5.
  • the embodiment of Fig. 12 corresponds in principle to that of Figures 6 and 7.
  • the outer part 9b of the adapter ring 9 is made in two parts.
  • a screw connection of these two parts of the externa ßeren part 9 b of the adapter ring 9 is provided.
  • the damping layer 8 is formed from a multiplicity of metal wires which are pressed into one another and may be in the form of a woven fabric, a knitted fabric, a braid, a knitted fabric, a tangle or another structure, for example, and are preferably pressed together.
  • a suitable shape may be used to produce the ring shape of the cushion layer 8 desired in this case.
  • Such a structure of metal wires pressed into one another has a multiplicity of joints, contact points and parting surfaces, as a result of which good sound insulation is achieved on account of friction and reflections.
  • the metal wires may be made of stainless steel, such as a suitable chromium-nickel steel.
  • the metal wires may, for example, have a thickness of 0.25 mm. Of course, completely different thicknesses or
  • the damping layer 8 from a plastic material or from rubber or an elastomer.
  • the damping layer 8 and the associated absorption of axial forces according to the embodiments of Figures 5, 6, 7, 12 and 13 can be absorbed at a high thrust load very much energy.
  • damping layers 8 may be provided in the radial direction of the rolling bearing 4 or of the adapter ring 9 denoted by "x".
  • the thickness of the damping layer 8 may be slightly greater than a distance between the two independent parts 6a and 6b of the outer ring 6 or of the inner ring 5 or of the adapter ring 9 before the pressing thereof. This results in a prestressing of the damping layer 8 within the rolling bearing 4 and the adapter ring.
  • the damping layer 8 for example, between the two parts 6a and 6b of the outer ring 6 and the two parts 9a and 9b of the adapter ring 9 and the two parts, not shown, of the inner ring 5 are pressed.
  • corresponding bevels can be located on the two parts 6a and 6b or 9a and 9b, which facilitate insertion of the damping layer 8.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)

Abstract

La présente invention concerne un palier à roulement (4), en particulier pour la boîte de vitesses d'un véhicule, qui présente une bague interne (5), une bague externe (6) et plusieurs corps de roulement (7) disposés entre la bague interne et la bague externe. Le palier à roulement présente également au moins un matériau amortissant les vibrations composé d'une couche d'amortissement (8) qui est disposée dans la bague externe et/ou dans la bague interne et/ou dans une bague d'adaptation (9) entourant le palier à roulement sur sa circonférence extérieur de telle façon que la bague externe et/ou la bague interne et/ou la bague d'adaptation sont séparées en deux pièces distinctes (6a, 6b) par la couche d'amortissement. La couche d'amortissement est disposée ou réalisée par rapport aux deux pièces distinctes de la bague externe et/ou de la bague interne ou de la bague d'adaptation de telle façon que les forces radiales et les forces axiales puissent être transmises via la bague externe et/ou la bague interne ou la bague d'adaptation.
PCT/EP2015/079602 2014-12-12 2015-12-14 Palier à roulement WO2016092114A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014118553.6 2014-12-12
DE102014118553.6A DE102014118553A1 (de) 2014-12-12 2014-12-12 Wälzlager

Publications (1)

Publication Number Publication Date
WO2016092114A1 true WO2016092114A1 (fr) 2016-06-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/079602 WO2016092114A1 (fr) 2014-12-12 2015-12-14 Palier à roulement

Country Status (2)

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DE (1) DE102014118553A1 (fr)
WO (1) WO2016092114A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106763482A (zh) * 2016-12-29 2017-05-31 吴利祥 一种耐用的减震套
WO2018028822A1 (fr) * 2016-08-06 2018-02-15 Daimler Ag Palier à roulement, vis à billes comprenant ce palier à roulement, et mécanisme de direction comprenant cette vis à bille ou ce palier à roulement
EP3418595A1 (fr) * 2017-06-19 2018-12-26 MPS Micro Precision Systems AG Roulement à billes pour pièce d'horlogerie
CN110397676A (zh) * 2018-04-24 2019-11-01 斯凯孚公司 具有电绝缘材料的滚动轴承和该滚动轴承的制造方法

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DE102017114491A1 (de) 2017-06-29 2019-01-03 Schaeffler Technologies AG & Co. KG Getriebewelle sowie Kraftfahrzeuggetriebe
DE102017114484A1 (de) 2017-06-29 2019-01-03 Schaeffler Technologies AG & Co. KG Wälzlager sowie Kraftfahrzeuggetriebe mit einem Wälzlager
DE102017114490A1 (de) 2017-06-29 2019-01-03 Schaeffler Technologies AG & Co. KG Getriebegehäuse sowie Kraftfahrzeuggetriebe
DE102018111721A1 (de) * 2018-05-16 2019-11-21 Schaeffler Technologies AG & Co. KG Planetenträger für ein Planetengetriebe sowie Planetengetriebe
DE102018131102A1 (de) 2018-12-06 2019-12-19 Schaeffler Technologies AG & Co. KG Verfahren zur Schwingungsdämpfung in einem Kraftfahrzeuggetriebe
DE102018131111A1 (de) 2018-12-06 2020-06-10 Schaeffler Technologies AG & Co. KG Schwingungstilger für ein Kraftfahrzeuggetriebe
JP7216585B2 (ja) * 2019-03-19 2023-02-01 ミネベアミツミ株式会社 遠心ファン
DE102019121273A1 (de) * 2019-08-07 2020-09-17 Schaeffler Technologies AG & Co. KG Wälzlager
DE102020104725A1 (de) 2020-02-24 2021-08-26 Schaeffler Technologies AG & Co. KG Verbindungsplatte und Antriebseinheit mit einer solchen Verbindungsplatte
DE102020121162A1 (de) 2020-08-12 2021-08-12 Schaeffler Technologies AG & Co. KG Schwingungsentkoppeltes Wälzlager
DE102022129678A1 (de) 2022-11-10 2024-05-16 Schaeffler Technologies AG & Co. KG Wälzlager

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US2674505A (en) * 1951-07-07 1954-04-06 Connecticut Hard Rubber Co Rubber mounted bearing
DE1037211B (de) * 1957-01-26 1958-08-21 Duerkoppwerke Ag Kegelrollenlager
DE19642193A1 (de) * 1996-10-12 1998-04-16 Teves Gmbh Alfred Lageranordnung
EP0840024A1 (fr) * 1996-11-05 1998-05-06 Firma Carl Freudenberg Palier à roulement amorti
WO1998026190A1 (fr) * 1996-12-12 1998-06-18 Skf Engineering And Research Centre B.V. Systeme de palier a element roulant, dote d'un amortissement ameliore
DE19701178A1 (de) * 1997-01-15 1998-07-16 Umfotec Umformtechnik Gmbh Lagerring
DE102007060968A1 (de) * 2007-01-11 2008-07-17 Ab Skf Lageranordnung für eine Tragrolle
EP1950433A2 (fr) * 2007-01-26 2008-07-30 JTEKT Corporation Dispositif de palier à roulement
EP2738393A1 (fr) * 2012-11-30 2014-06-04 Agilent Technologies, Inc. Support pour paliers à roulement

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FR1519650A (fr) 1967-01-03 1968-04-05 Vibrachoc Sa Nouveau dispositif amortisseur pour véhicule automobile
JP4839473B2 (ja) * 2001-02-01 2011-12-21 シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト 軸受装置
JP2005024046A (ja) * 2003-07-04 2005-01-27 Koyo Seiko Co Ltd ダンパー、ならびに転がり軸受装置
DE102009000566A1 (de) 2009-02-03 2010-08-05 Zf Lenksysteme Gmbh Schwingungsdämpfendes Lager
DE102010061920B3 (de) * 2010-11-25 2012-05-16 Aktiebolaget Skf Lageranordnung

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2674505A (en) * 1951-07-07 1954-04-06 Connecticut Hard Rubber Co Rubber mounted bearing
DE1037211B (de) * 1957-01-26 1958-08-21 Duerkoppwerke Ag Kegelrollenlager
DE19642193A1 (de) * 1996-10-12 1998-04-16 Teves Gmbh Alfred Lageranordnung
EP0840024A1 (fr) * 1996-11-05 1998-05-06 Firma Carl Freudenberg Palier à roulement amorti
WO1998026190A1 (fr) * 1996-12-12 1998-06-18 Skf Engineering And Research Centre B.V. Systeme de palier a element roulant, dote d'un amortissement ameliore
DE19701178A1 (de) * 1997-01-15 1998-07-16 Umfotec Umformtechnik Gmbh Lagerring
DE102007060968A1 (de) * 2007-01-11 2008-07-17 Ab Skf Lageranordnung für eine Tragrolle
EP1950433A2 (fr) * 2007-01-26 2008-07-30 JTEKT Corporation Dispositif de palier à roulement
EP2738393A1 (fr) * 2012-11-30 2014-06-04 Agilent Technologies, Inc. Support pour paliers à roulement

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018028822A1 (fr) * 2016-08-06 2018-02-15 Daimler Ag Palier à roulement, vis à billes comprenant ce palier à roulement, et mécanisme de direction comprenant cette vis à bille ou ce palier à roulement
CN106763482A (zh) * 2016-12-29 2017-05-31 吴利祥 一种耐用的减震套
EP3418595A1 (fr) * 2017-06-19 2018-12-26 MPS Micro Precision Systems AG Roulement à billes pour pièce d'horlogerie
CH713898A1 (fr) * 2017-06-19 2018-12-28 Mps Micro Prec Systems Ag Roulement à billes pour pièce d'horlogerie.
CN110397676A (zh) * 2018-04-24 2019-11-01 斯凯孚公司 具有电绝缘材料的滚动轴承和该滚动轴承的制造方法

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