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WO2003006264A1 - Ensemble roulement pour un moyeu de roue a entrainement d'un vehicule automobile - Google Patents

Ensemble roulement pour un moyeu de roue a entrainement d'un vehicule automobile Download PDF

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Publication number
WO2003006264A1
WO2003006264A1 PCT/EP2002/006608 EP0206608W WO03006264A1 WO 2003006264 A1 WO2003006264 A1 WO 2003006264A1 EP 0206608 W EP0206608 W EP 0206608W WO 03006264 A1 WO03006264 A1 WO 03006264A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
ring
inner bearing
wheel hub
longitudinal axis
Prior art date
Application number
PCT/EP2002/006608
Other languages
German (de)
English (en)
Inventor
Werner Krude
Ludger Wenning
Peter Bongartz
Herbert Cermak
Original Assignee
Gkn Automotive 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 Gkn Automotive Gmbh filed Critical Gkn Automotive Gmbh
Publication of WO2003006264A1 publication Critical patent/WO2003006264A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/02—Hubs adapted to be rotatably arranged on axle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0047—Hubs characterised by functional integration of other elements
    • B60B27/0052—Hubs characterised by functional integration of other elements the element being a brake disc
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/12—Torque-transmitting axles
    • B60B35/18—Arrangement of bearings
    • 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
    • F16C35/063—Fixing them on the shaft
    • 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
    • F16C19/18—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 two or more rows of balls
    • F16C19/181—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 two or more rows of balls with angular contact
    • F16C19/183—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 two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—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 two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/185—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 two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Definitions

  • the invention relates to a bearing arrangement for a drivable wheel hub of a motor vehicle.
  • DE 198 11 184 AI shows a bearing arrangement for a wheel hub of a motor vehicle with an outer bearing ring with a bore in which two outer bearing raceways are provided.
  • the wheel hub has a cavity in which there are outer grooves for a constant velocity joint and two inner bearing raceways, the inner bearing raceways with the outer bearing raceways.
  • One of the inner bearing raceways is part of an inner bearing ring which sits on a cylindrical seat surface of the wheel hub and is held in a preloaded manner by a reshaped collar.
  • the bearing arrangement has an inner part with inner raceways, the latter forming a pair with the outer raceways, in which balls of the constant velocity joint are received.
  • the pivot point of the constant velocity joint is as close as possible or preferably on the spreading axis. orderly .
  • DE 32 02 136 AI describes a bearing arrangement for a wheel hub of a motor vehicle, which, when used on the driven wheels, comprises a constant velocity joint, the wheel hub itself being a one-piece design of a flange with the outer part of the joint, in which the inner bearing raceways of an inclined shoulder ball bearing are incorporated into the outer surface of the wheel hub.
  • the inner bearing raceways lie opposite one another and take up bearing balls with opposite outer bearing raceways which are attached to the shoulders of an inwardly pointing web of an outer bearing ring.
  • the one-piece design results in partial filling with bearing balls in order to be able to mount the outer bearing ring on the wheel hub.
  • the limited number goes hand in hand with a lower load capacity of the bearing. Also, due to this assembly, practically no preload can be achieved.
  • JP 2000-142009 A shows a bearing arrangement comprising “a wheel hub with a receiving bore and a seat surface for a separate bearing inner ring, which contains a first inner bearing raceway, and with a second inner bearing raceway machined into the wheel hub, the first inner raceway Bearing race comprising inner bearing ring is fixed to the wheel hub by a deformed collar.
  • the outer bearing ring comprises two at the two oppositely directed shoulders of a web disposed outer La ⁇ gerlaufbahnen which each form with an inner bearing race and a pair of record together with said bearing balls.
  • a constant velocity joint separate from this arrangement for transmitting the driving forces to the flange of the Wheel hub
  • which has an outer joint body arranged outside the wheel hub with external grooves and a pin integrally formed thereon for rotationally fixed connection to the wheel hub.
  • the non-rotatable connection is achieved by a pair of teeth on the pin of the outer joint body and in the bore of the wheel hub.
  • a disadvantage of this design is that, in order to avoid rotational play between the toothing of the pin and the bore of the wheel hub, there must be an interference fit that influences the bearing play.
  • this arrangement is long in the axial direction.
  • the disadvantage here is that the intermediate shaft arranged between the joint center points of the two joints belonging to a side drive shaft for driving the wheels of a motor vehicle becomes short. This leads to higher flexion angles or a low ability to bend at least the constant-velocity joint on the wheel side and thus, in particular in the case of steerable wheels, to an increase in the turning circle of the vehicle.
  • the invention is therefore based on the object of providing a bearing arrangement in which the distance between the center of the constant velocity joint and the bearing of the wheel hub in the outer bearing ring is as short as possible and in which there is a high load-bearing capacity for the bearing supporting the wheel hub.
  • a bearing arrangement for a drivable wheel hub of a motor vehicle comprising a longitudinal axis, an outer bearing ring, with a bore centered on the longitudinal axis, in which a web protrudes radially on the longitudinal axis, on the two of which
  • the outer bearing raceways are attached to the shoulders facing away from one another in the direction of the longitudinal axis, a wheel hub with a flange centered on the longitudinal axis, with a cavity in which there are outer grooves distributed around the longitudinal axis, which have a first end remote from the flange and a second end close to the flange have, with two mutually facing inner bearing raceways, comprising a first inner bearing raceway removed from the flange and a second inner bearing raceway close to it, each of which, together with an opposite outer bearing raceway, guide bearing roller bodies and thus form a bearing, at least the first inner bearing raceway being part of a first inner bearing ring, which has a first end face facing
  • Balls one of which is received by a pair of outer grooves and inner grooves.
  • the wheel hub with the outer grooves thus simultaneously forms the outer joint body of a constant velocity joint, which otherwise otherwise comprises the inner part and the balls and, if appropriate, additional guide means for the balls, for example a cage.
  • the advantage of this design is that the outer joint body of the constant velocity joint is combined with the wheel hub and the center of the joint of the constant velocity joint can be moved as close as possible to a central plane that intersects the longitudinal axis at right angles between the two rows of bearing roller bodies of the bearing. It is also advantageous that due to the at least one provided and separate inner bearing ring, it is easy to mount for the outer bearing, i.e. is given for the camp. A high degree of filling can be achieved with roller bearings. This is also associated with the fact that an axial preload can be applied, which in the solution according to the invention can be achieved simply by reshaping the ring shoulder into a collar which lies against the first end face of the first inner bearing ring.
  • the wheel hub with all the machining operations that relate to the inner bearing raceways and the outer grooves as well as the other inner contours of the cavity of the wheel hub, which relate to the joint function can be carried out, whereby during hardening it must be ensured that the ring shoulder remains in the soft state in order to enable the deformation. For this reason, the ring shoulder is located after the seat surface and the first end of the outer grooves, the latter in particular requiring hardening because of the torque transmission.
  • the tubular ring extension can be in one piece, i.e. be designed to run continuously around the longitudinal axis. However, it can also be interrupted in the U direction around the longitudinal axis.
  • the second inner bearing race near the flange is machined into the outer surface of the wheel hub and that the cylindrical first seat surface in the direction of the flange in a plane that intersects the longitudinal axis at right angles, ends parallel first contact surface against which the first inner bearing ring can be brought into contact with its second end face.
  • one of the inner bearing raceways in this embodiment is part of the outer surface of the wheel hub, a material that has the quality required for rolling bearings can be selected.
  • the small number of components is advantageous.
  • the amount of preload can be limited in that the first inner bearing ring comes to rest with its second end face against the first contact face of the wheel hub at the end of the first seat face near the flange.
  • the second inner bearing raceway is part of a second inner bearing ring
  • the wheel hub has a cylindrical second seat surface for the second inner bearing ring
  • the second inner bearing ring has a third end face facing away from the flange and a fourth end face facing it has that the second seating surface towards the flange has a second bearing surface parallel to a plane that intersects the longitudinal axis at right angles, against which the second inner bearing ring is supported with the fourth end face, and that the first inner bearing ring with the second end face against the third end face of the second inner bearing ring.
  • a material of special quality can be selected for the wheel hub.
  • a material suitable for rolling bearings is only required for the outer bearing ring and the two inner bearing rings.
  • a material can be selected for the wheel hub that particularly meets the demands placed on the constant velocity joint.
  • Wheel hub has a larger diameter than the first seat.
  • the formability of the ring approach can be favored in that the wall thickness of the ring approach decreases towards its end remote from the second end of the outer grooves. It is provided that the reduction in the wall thickness of the ring shoulder is shown by a conically widened course of the ring shoulder bore towards its end.
  • the first inner bearing ring with an annular projection which at least partially covers the collar formed from the annular projection radially on the outside in the axial direction, so that the outer surface of the annular projection represents a fastening surface for a seal.
  • a cap can be attached to this, to which a bellows is connected, which bridges the distance to the shaft connected to the inner part in order to prevent lubricant from escaping or dirt from entering the constant velocity joint.
  • the ring extension of the wheel hub can directly axially connect to the second end of the outer grooves or be provided at a distance thereafter.
  • FIG. 1 shows a view of a first embodiment of a bearing arrangement according to the invention
  • FIG. 2 shows a section II-II according to FIG. 1,
  • FIG. 3 shows a view corresponding to FIG. 1 of a second embodiment according to the invention with two inner bearing rings
  • Figure 4 shows a section IV-IV according to Figure 3 and
  • Figure 5 shows the assignment of the two inner bearing rings to the wheel hub and their definition.
  • a longitudinal axis 1 with regard to the exemplary embodiments according to FIGS. 1 and 2 and 101 in the embodiment according to FIGS. 3 to 5.
  • a plane 2 or 102 is assumed as the reference plane, on which the longitudinal axis 1 or 101 is perpendicular.
  • the wheel hub designated by 3 has a flange 4 offset to level 2 on the longitudinal axis 1, which flange is used in a motor vehicle for attaching the wheel and the brake disc.
  • the wheel hub 3 has a cavity 5, which has in its wall outer grooves 6 which extend from a first end 7 remote from the flange 4 to a second end 8 close to the flange 4 and which are distributed around the longitudinal axis 1 and arranged in meridian planes.
  • the inner part 9 is received, in the outer surface corresponding to the outer grooves 6 of the wheel hub 3 inner grooves 10 are incorporated circumferentially, wherein an inner groove 10 with an opposite outer groove 6 forms a pair.
  • a cage 11 is accommodated between the outer surface of the inner part 9 and the inner surface of the wheel hub 3 in the region of the cavity 5 between the outer grooves 6 following the circumference.
  • this has distributed windows 12 which are open to them and each serve to guide a ball 13.
  • the ball 13 projects beyond the cage 11 radially outwards from the longitudinal axis 1 and inwards towards it, each engaging in an outer race 6 and an inner race 10.
  • the balls 13 serve to transmit torque between the inner part 9 and the wheel hub 3.
  • the inner part 9 can be pivoted on all sides about the center of the joint 0 with respect to the wheel hub 3. This lies at the intersection of level 2 with the longitudinal axis 1.
  • the inner part 9 has a bore centered on the longitudinal axis 1 for connecting an intermediate shaft, at the other end of which, for example, a constant velocity joint is connected, which is connected in a rotationally fixed manner to the differential of a motor vehicle, so that starting from the differential via the constant velocity joint assigned to it, the intermediate shaft and the constant velocity joint integrated in the wheel hub 3 enables torque transmission to a wheel of a motor vehicle.
  • the wheel hub 3 On the outer surface, the wheel hub 3 has a first seat 14, which is at least partially still in the area of the axial extension of the outer grooves 6. It has an in-plane 2 and to this extending first parallel to ⁇ bearing surface 15 on which a radially from the longitudinal axis Forms 1 extending shoulder.
  • the first inner bearing race 16 removed from the flange 4 is part of a first inner bearing ring 17 which has a first end face 18 pointing away from the flange 4 and a second end face 19 facing the flange 4.
  • the first inner bearing race 16 faces level 2.
  • a second inner bearing race 20 is directly incorporated into the outer surface of the wheel hub 3 and faces the first inner bearing race 16. Both are arranged symmetrically to level 2, so that this represents the middle level in this case.
  • the first inner bearing ring 17 bears with its second end face 19 against the first contact face 15.
  • the first inner bearing ring 17 is held against this first bearing surface 15 in that a collar 21a formed from a ring shoulder 21 bears against the first end face 18 of the first inner bearing ring 17.
  • the first inner bearing ring 17 has in the area of its ring projection 23, which at least partially covers the collar 21a in the axial direction, on the outside a fastening surface 22 for a cap of an otherwise not shown sealing arrangement.
  • the ring extension 21 formed into the collar 21a is shown in broken lines in the lower half of FIG. 2. It can be seen that, following the first end 7 of the outer grooves 6, it then extends away from the flange 4 and has a conical widening 24 in its bore toward the end remote from the flange 4. It is also seen that the first face of the first inner La ⁇ gerringes 17 is arranged at a small axial distance from the first end 7 of the outer grooves 6 18, ie the seat ⁇ surface 14 also overhangs, but in a small extent, the first end 7 of the outer grooves 6 in the direction away from the flange 4. Due to this arrangement, the deformation of the annular shoulder 21 to the collar 21a does not influence the quality of the first seat surface 14 and that of the outer grooves 6 and thus also the guide surface for the cage 11.
  • An outer bearing ring 25 is arranged coaxially around the wheel hub 3, which has a continuous bore in which a web 26 projects radially inward towards the longitudinal axis 1, the two shoulders of which, facing away from one another in the longitudinal direction, with a first outer bearing raceway 27 or one second outer bearing race 28 are provided.
  • the second outer bearing race 28 lies opposite the second inner bearing race 28, likewise runs circumferentially about the longitudinal axis 1 and accommodates bearing roller bodies designed as bearing balls 29 with the second inner bearing race 20.
  • the bearing balls 29 can be assigned to both outer bearing raceways 27, 28 before the outer bearing ring 25 is assembled.
  • This unit is then pushed onto the wheel hub 3, so that the bearing balls 29 belonging to the second outer bearing race 28 come into contact with the second inner bearing race 20.
  • the first inner bearing ring 17 is then pushed over the still undeformed ring shoulder 21 onto the first seat surface 14, so that the bearing balls 29 come into contact with the first inner bearing race 16.
  • the diameter D1 of the first seat surface 14 is equal to or larger than the outer diameter D2 of the ring extension 21. This is followed by an axial radial deformation of the ring extension 21 to the collar 21a, with the first inner bearing ring 17 in the direction to the flange 4 is applied.
  • the collar 21a is completely in contact with the first end face 18 of the first inner bearing ring 17.
  • the arrangement of the first inner bearing race 16 and the first outer bearing race 17 and thus the center of the bearing balls 29 guided by them is preferably selected such that the one associated with it Level to level 2 has the same distance as that of the bearing balls 29, which are guided between the second inner bearing race 20 and the second outer bearing race 28. This creates a double row angular shoulder ball bearing.
  • the wheel hub is not only a first seat 114 for receiving a first inner bearing ring 117, but subsequent to the first abutment surface 115 is an enlarged diameter second seat ⁇ surface 31 for receiving a second inner bearing ring 30, which by Flange 104 has a third end face 31 and a fourth end face 32 toward flange 4.
  • the second seat 33 ends toward the flange 104 in a second contact surface 34. It can also be seen that the first end 107 of the External grooves 106 substantially coincide with the end of the first seat surface 114 remote from the flange 104 in the axial direction.
  • the diameter of the second seat 114 can be seen in FIG. 5 and is designated D3.
  • the diameter D3 is larger than the diameter D1 of the first seat 114.
  • the first inner bearing ring 117 in turn is supported with its second end face 119 against the third end face 31 of the second inner bearing ring 30 and acts on it with its fourth end face 32 for abutment against the second contact face 34.
  • the bearing preload is determined by the dimensions of the two inner faces Bearing rings 117 and 30 determined.
  • the second end face 119 of the first inner bearing ring 117 is not supported against the first contact surface 15.
  • the ring extension 121 is interrupted in the circumferential direction around the longitudinal axis 101. This facilitates the forming. The interruptions are particularly visible in FIG. 3 and represented by slots 35.
  • the collar 21a or 121a which is integrally connected to the wheel hub 3 or 103, ensures that a preload can be permanently achieved by means of the forming, starting from the ring shoulder 21 or 121. A positive fit is achieved. Settlements occur, which could arise in connection with the usual fixing agents for bearing rings not on. A correspondingly high load-bearing capacity is achieved, in addition to the possibility of increasing this by a high degree of filling for the inclined shoulder ball bearing.
  • bearing balls as bearing rolling elements
  • other rolling element shapes for example tapered rollers, can also be used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un ensemble roulement pour un moyeu (3) de roue à entraînement d'un véhicule automobile. Dans la cavité (5) du moyeu (3) de roue se trouvent des gorges de roulement extérieures (6), présentant une première extrémité (7) éloignée de la bride (4). Une première bague de roulement intérieure (17), qui comprend la première bande de roulement intérieure (116) d'un roulement, est placée sur une première surface d'appui (14) du moyeu (3) de roue. La deuxième bande de roulement intérieure (20) est directement incorporée dans la face extérieure du moyeu (103) de roue. Les bandes de roulement extérieures correspondantes (27) et (28) se trouvent dans une bague de roulement extérieure (25). La première bague de roulement intérieure (17), qui est maintenue sur le moyeu (3) de roue par un rebord annulaire (21) sous la forme d'une collerette (21a), applique une précontrainte sur le roulement ainsi formé.
PCT/EP2002/006608 2001-07-11 2002-06-15 Ensemble roulement pour un moyeu de roue a entrainement d'un vehicule automobile WO2003006264A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10133094A DE10133094A1 (de) 2001-07-11 2001-07-11 Lagerungsanordnung für eine antreibbare Radnabe eines Kraftfahrzeuges
DE10133094.4 2001-07-11

Publications (1)

Publication Number Publication Date
WO2003006264A1 true WO2003006264A1 (fr) 2003-01-23

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ID=7691032

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2002/006608 WO2003006264A1 (fr) 2001-07-11 2002-06-15 Ensemble roulement pour un moyeu de roue a entrainement d'un vehicule automobile

Country Status (2)

Country Link
DE (1) DE10133094A1 (fr)
WO (1) WO2003006264A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITTO20040317A1 (it) 2004-05-14 2004-08-14 Skf Ab Dispositivo di connessione di un cuscinetto volvente ad un mozzo ruota
DE102007016414A1 (de) * 2007-04-05 2008-10-09 Schaeffler Kg Radlagereinheit
DE102013012482A1 (de) * 2013-07-26 2015-01-29 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Achseinrichtung, Verfahren zur Herstellung derselben und Kraftfahrzeug

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3202136A1 (de) * 1981-01-27 1982-11-04 Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt Radlagereinheit
DE3209690C1 (de) * 1982-03-17 1983-07-28 Uni-Cardan Ag, 5200 Siegburg Lagerungsanordnung
DE19811184A1 (de) * 1998-03-14 1999-09-16 Daimler Chrysler Ag Radlagerung mit integriertem Gleichlaufgelenk für ein lenkbares Kraftfahrzeugrad
JP2000142009A (ja) * 1998-02-16 2000-05-23 Nsk Ltd 車輪駆動用車軸ユニット

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3202136A1 (de) * 1981-01-27 1982-11-04 Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt Radlagereinheit
DE3209690C1 (de) * 1982-03-17 1983-07-28 Uni-Cardan Ag, 5200 Siegburg Lagerungsanordnung
JP2000142009A (ja) * 1998-02-16 2000-05-23 Nsk Ltd 車輪駆動用車軸ユニット
DE19811184A1 (de) * 1998-03-14 1999-09-16 Daimler Chrysler Ag Radlagerung mit integriertem Gleichlaufgelenk für ein lenkbares Kraftfahrzeugrad

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 08 6 October 2000 (2000-10-06) *

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Publication number Publication date
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