WO1999045286A1 - Palier a roulement a cage discoïde pour volant d'inertie - Google Patents

Palier a roulement a cage discoïde pour volant d'inertie Download PDF

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Publication number
WO1999045286A1
WO1999045286A1 PCT/EP1998/007898 EP9807898W WO9945286A1 WO 1999045286 A1 WO1999045286 A1 WO 1999045286A1 EP 9807898 W EP9807898 W EP 9807898W WO 9945286 A1 WO9945286 A1 WO 9945286A1
Authority
WO
WIPO (PCT)
Prior art keywords
flywheel
ring
bearing
cage
bearing ring
Prior art date
Application number
PCT/EP1998/007898
Other languages
German (de)
English (en)
Inventor
Werner Oberbeckmann
Original Assignee
INA Wälzlager Schaeffler oHG
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 INA Wälzlager Schaeffler oHG filed Critical INA Wälzlager Schaeffler oHG
Publication of WO1999045286A1 publication Critical patent/WO1999045286A1/fr

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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
    • 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
    • F16C19/163—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 with angular contact
    • 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
    • F16C33/38—Ball cages
    • F16C33/3806—Details of interaction of cage and race, e.g. retention, centring
    • 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
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • 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
    • F16C33/38—Ball cages
    • F16C33/42—Ball cages made from wire or sheet metal strips
    • F16C33/422—Ball cages made from wire or sheet metal strips made from sheet metal
    • F16C33/425—Ball cages made from wire or sheet metal strips made from sheet metal from a single part, e.g. ribbon cages with one corrugated annular part
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6607—Retaining the grease in or near the bearing
    • F16C33/6618—Retaining the grease in or near the bearing in a reservoir in the sealing means
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
    • 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
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13164—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by the supporting arrangement of the damper unit
    • F16F15/13171—Bearing arrangements
    • 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
    • F16C2361/55—Flywheel systems
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F16D2013/703—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members the pressure plate on the flywheel side is combined with a damper

Definitions

  • the invention relates to a flywheel, in particular for internal combustion engines, with two flywheels that can be rotated relative to one another to a limited extent, between which a roller bearing is arranged, the outer bearing ring of which is arranged in a cylindrical bore of the second flywheel mass and the inner bearing ring of which is arranged on a cylindrical collar of the first flywheel mass, wherein a sheet metal part is arranged between the outer bearing ring and the second flywheel mass, which surrounds the rolling bearing on one end face with an axially outwardly directed formation, so that a cavity is formed, while the rolling bearing on its other end face by means of a reinforcing ring and molded sealing areas existing sealing ring is sealed.
  • a flywheel of this type is previously known from DE 42 14 655 A1.
  • This between the outer bearing ring and the second flywheel shaped sheet metal part limits with its axially outward shaping a cavity that serves to receive bearing lubricant, so that this additional lubricant chamber ensures that the bearing can be properly lubricated over a longer period of time.
  • the disadvantage here is that due to the high thermal conductivity of the molded sheet metal part, there is no thermal insulation between the components involved, so that the lubricant filling of the bearing may be overstressed by the heat flow directed inwards from the outside. In extreme cases, excessive thermal distortion of the bearing could occur, so that its function appears to be at risk. 2
  • the deep groove ball bearing arranged between the two centrifugal masses can now be designed in different ways. Is it spherical, d. H. Executed without a cage, the outer bearing ring must be blown up to fill the bearing with balls. If a snap cage is used, there is a risk that it can migrate out of the bearing if it is not properly installed. If, on the other hand, a window cage is used, it must first be made in two pieces and connected to a unit during assembly.
  • the invention has for its object to design a bearing for two rotating masses rotatable relative to each other so that it has a high level of functional reliability and is inexpensive to produce.
  • this object is achieved according to the characterizing part of claim 1 in that the outer bearing ring consists of two race halves spaced apart from one another in the axial direction, so that a circumferential gap is formed in which a freely rotatable disc cage with pockets for receiving rolling elements is guided.
  • the main advantage of this storage is that undesired lateral migration of the cage is reliably prevented by accommodating it in the circumferential gap. Due to the design of the cage according to the invention, high dynamic and static load ratings are achieved compared to conventional cage bearings, since almost the same number of rolling elements can be accommodated even in the case of full-length bearings. Another advantage lies in the fact that the bearing can be assembled in a simple manner due to the two-part design of the outer ring.
  • race half are provided on their outer surface with uniformly spaced recesses. These recesses in the jacket area act as air cushions and ensure that a temperature barrier is formed 3 is, so that the heat transfer from the outside radially inwards in the direction
  • the sheet metal part in the area of the sealing ring should engage around the sealing areas on the end face with a radially inward-pointing leg, so that a sealing bead molded onto the outer radial end of the reinforcement ring is squeezed between the latter and one of the outer raceway halves when the leg rolls on.
  • This elastic tensioning of the sealing bead ensures a particularly effective sealing of the rolling bearing.
  • the two race halves of the outer bearing ring are manufactured as separate components or can be produced by blasting an output ring.
  • the inner bearing ring can also consist of two race halves spaced apart in the axial direction, so that a circumferential gap is formed in which a freely rotatable disc cage with pockets for receiving rolling elements is guided.
  • FIG. 1 shows a flywheel consisting of two flywheels in a semi-longitudinal section
  • FIG. 2 shows a detail of FIG. 1 on an enlarged scale
  • Figures 3 u. 4 shows a side view or a longitudinal section through a race half
  • Figure 5 is a side view of a disc cage.
  • FIG. 1 shows a dual-mass flywheel combined with a friction clutch, which is used to transmit the torque from an internal combustion engine to a downstream transmission of a motor vehicle.
  • the dual mass flywheel consists of a first flywheel mass 1, which is fixed on the crankshaft of an internal combustion engine.
  • a second flywheel mass 2 can be rotated relative to the first flywheel mass 1 to a limited extent.
  • the second flywheel mass 2 is supported relative to the first flywheel mass 1 via a ball bearing 3.
  • the second flywheel mass 2 is designed as a lining carrier against which a clutch disc 5 of a friction clutch 4 can be braced via a pressure plate.
  • a cover 7 of the friction clutch 4 is rotatably connected to the second flywheel 2.
  • the clutch disc 5 is provided with a hub 9, which is used for the rotationally fixed connection to a transmission input of the motor vehicle.
  • the mounting of the two centrifugal masses 1 and 2 using the single-row ball bearing 3 is described in more detail with reference to FIG 2.
  • the two flywheels 1 and 2 each have an axial end section 10 and 11, between which the single-row ball bearing 3 is arranged.
  • a sheet metal molded part 13 is arranged between the lateral surface of the receiving bore of the axial end section 11 of the flywheel mass 2 and an outer bearing ring 12 and engages around the outer bearing ring 12 with an annular region 14 over its entire axial extent.
  • This annular region 14 of the sheet metal part 13 goes on its the flywheel 1 5 opposite end into a radially inward region 15, which covers the outer bearing ring 12 on its end face.
  • This area 15 is adjoined by an area 16 extending in the axial direction, which in turn is followed by an area 17 pointing radially inward. This merges into an axial region 18 pointing in the direction of the center of the bearing 3, which is adjoined by a radially extending region 19, which in turn is detached from an axially extending region 20.
  • An inner ring 21 of the ball bearing 3 is encompassed on its end face by the region 19 and on its outer surface by the region 20 of the sheet metal molded part 13. In this way, a lubricant storage space 22 is formed which, filled with lubricant, ensures a long service life of the rolling bearing 3.
  • the other side of the ball bearing 3 is closed by a sealing ring, which consists of a reinforcement ring 23 with molded sealing areas.
  • the sealing areas are formed, on the one hand, by a sealing bead 24, which is arranged at the radially outer end of the reinforcing ring 23, and, on the other hand, by sealing lips 25, which are arranged at the radially inner end of the reinforcing ring 23 and abut the inner circumferential surface of the inner ring 21.
  • the sealing bead 24 is squeezed by a radial leg 26 of the sheet metal part 13 between the latter and the bearing outer ring 12 or the race half 27, so that a good seal of the ball bearing 3 is ensured.
  • the outer bearing ring 12 is composed of the two raceway halves 27 and 28, which are spaced apart from one another in the axial direction, so that a circumferential gap 29 is formed, in which a disk cage 30 shown in a side view in FIG. 5 is freely rotatable.
  • This disc cage 30 has pockets 32, which are separated from one another by webs 31 and serve to receive the bearing balls 33. The thinner the webs 31 in the circumferential direction, the more bearing balls 33 can be accommodated in the disc cage 30 and the higher its load-bearing capacity. By guiding the disc cage 30 in the circumferential gap 29, its axial displaceability is made impossible. 6
  • the two race halves 27, 28 of the outer bearing ring 12 are provided with recesses 34 which are uniformly spaced apart on their outer surface. These recesses act as air cushions and ensure that the heat transfer due to friction is reduced from the outside in the direction of the ball bearing 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

Un volant d'inertie comporte deux masses d'inertie (1, 2) pouvant tourner l'une par rapport à l'autre de manière limitée, entre lesquelles est disposé un palier à roulement (3). Ce dernier se présente sous la forme d'un roulement rainuré à simple rangée de billes, dont la bague de roulement extérieure (12) est formée de deux demi-bagues de roulement (27, 28) espacées l'une de l'autre en sens axial, de manière à créer une fente périphérique (29). Dans cette fente (29), une cage discoïde (30) est guidée de manière à tourner librement. Ainsi, cette cage discoïde (30) ne peut sortir du palier (3) dans le sens axial. En outre, les deux demi-bagues de roulement (27, 28) sont pourvues, sur leur surface latérale, d'évidements (34) faisant office de barrière thermique sous forme d'un matelas d'air isolant.
PCT/EP1998/007898 1998-03-04 1998-12-04 Palier a roulement a cage discoïde pour volant d'inertie WO1999045286A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19809176.1 1998-03-04
DE19809176A DE19809176A1 (de) 1998-03-04 1998-03-04 Schwungrad

Publications (1)

Publication Number Publication Date
WO1999045286A1 true WO1999045286A1 (fr) 1999-09-10

Family

ID=7859648

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1998/007898 WO1999045286A1 (fr) 1998-03-04 1998-12-04 Palier a roulement a cage discoïde pour volant d'inertie

Country Status (2)

Country Link
DE (1) DE19809176A1 (fr)
WO (1) WO1999045286A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018218631A1 (de) * 2018-10-31 2020-04-30 Zf Friedrichshafen Ag Drehschwingungsdämpfungsanordnung

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2866085B1 (fr) * 2004-02-11 2007-06-29 Skf Ab Dispositif de buee axiale de volant d'inertie.
DE102005008006A1 (de) * 2005-02-22 2006-08-31 Schaeffler Kg Zweimassenschwungrad für ein Kraftfahrzeug sowie Wälzlager für ein Zweimassenschwungrad
DE102008048517A1 (de) 2008-09-23 2010-03-25 Schaeffler Kg Wälzlager eines Zweimassen-Schwungrades
EP2489889B1 (fr) * 2011-02-21 2015-06-10 Aktiebolaget SKF Roulement à rouleaux précontraint, particulièrement pour colonne de direction
DE202011105635U1 (de) 2011-09-13 2012-02-17 Schaeffler Technologies Gmbh & Co. Kg Wälzlager eines Zweimassen-Schwungrades
WO2015176722A1 (fr) * 2014-05-20 2015-11-26 Schaeffler Technologies AG & Co. KG Amortisseur de vibrations de torsion
DE102018210701A1 (de) * 2018-06-29 2020-01-02 Zf Friedrichshafen Ag Kupplungsanordnung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3684336A (en) * 1970-03-11 1972-08-15 Pierre Mathys Miniature type ball bearing
US3980359A (en) * 1975-05-08 1976-09-14 United Technologies Corporation Ball bearing
EP0042325A1 (fr) * 1980-06-17 1981-12-23 Regie Nationale Des Usines Renault Joint de cardan à axes décalés
DE4214655A1 (de) * 1991-06-01 1992-12-03 Luk Lamellen & Kupplungsbau Waelzlager
DE4340458A1 (de) * 1993-11-27 1995-06-01 Schaeffler Waelzlager Kg Zylinderrollenlager

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
US3698777A (en) * 1970-12-08 1972-10-17 Timken Co Tapered roller bearing with minimum heat generating characteristics
DE2555923C3 (de) * 1975-12-12 1984-02-02 FAG Kugelfischer Georg Schäfer KGaA, 8720 Schweinfurt Wälzlagerlaufring
DE3506818C2 (de) * 1984-03-05 1994-08-04 Luk Lamellen & Kupplungsbau Dämpfungseinrichtung zum Aufnehmen bzw. Ausgleichen von Drehstößen
DE8406743U1 (de) * 1984-03-05 1993-02-25 LuK Lamellen und Kupplungsbau GmbH, 7580 Bühl Dämpfungseinrichtung zum Aufnehmen bzw. Ausgleichen von Drehstößen, insbesondere von Drehmomentschwankungen einer Brennkraftmaschine
DE3876092T2 (de) * 1988-05-14 1993-03-25 Chubu Bearing Kk Lager.
DE4244091C2 (de) * 1992-06-02 1997-07-24 Schaeffler Waelzlager Kg Zylinderrollenlager
DE4414584B4 (de) * 1993-05-07 2008-12-18 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehschwingungsdämpfende Einrichtung
DE19631725B4 (de) * 1995-09-02 2017-01-05 Schaeffler Technologies AG & Co. KG Mechanische Sicherung für Bauteile

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3684336A (en) * 1970-03-11 1972-08-15 Pierre Mathys Miniature type ball bearing
US3980359A (en) * 1975-05-08 1976-09-14 United Technologies Corporation Ball bearing
EP0042325A1 (fr) * 1980-06-17 1981-12-23 Regie Nationale Des Usines Renault Joint de cardan à axes décalés
DE4214655A1 (de) * 1991-06-01 1992-12-03 Luk Lamellen & Kupplungsbau Waelzlager
DE4340458A1 (de) * 1993-11-27 1995-06-01 Schaeffler Waelzlager Kg Zylinderrollenlager

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018218631A1 (de) * 2018-10-31 2020-04-30 Zf Friedrichshafen Ag Drehschwingungsdämpfungsanordnung

Also Published As

Publication number Publication date
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