WO2006095603A1 - Dispositif de roulement pour une roue - Google Patents

Dispositif de roulement pour une roue Download PDF

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Publication number
WO2006095603A1
WO2006095603A1 PCT/JP2006/303725 JP2006303725W WO2006095603A1 WO 2006095603 A1 WO2006095603 A1 WO 2006095603A1 JP 2006303725 W JP2006303725 W JP 2006303725W WO 2006095603 A1 WO2006095603 A1 WO 2006095603A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring
hub
wheel
outer ring
end surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2006/303725
Other languages
English (en)
Japanese (ja)
Inventor
Minoru Suzuki
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.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
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 NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of WO2006095603A1 publication Critical patent/WO2006095603A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • 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
    • 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
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/12—Discs; Drums for disc brakes
    • F16D65/123—Discs; Drums for disc brakes comprising an annular disc secured to a hub member; Discs characterised by means for mounting
    • 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
    • F16C19/186—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 three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • 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
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
    • 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
    • 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
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D2065/13—Parts or details of discs or drums
    • F16D2065/134—Connection
    • F16D2065/1384—Connection to wheel hub

Definitions

  • the present invention relates to a drive wheel bearing device that rotatably supports drive wheels (front wheels of FF vehicles, rear wheels of FR vehicles, all wheels of 4WD vehicles) with respect to a suspension system of an automobile.
  • Fig. 4 shows a bearing device for a drive wheel.
  • the main components are a hub wheel 1 and an inner ring 2, double-row rolling elements 3 and 4, an outer ring 5 and a constant velocity universal joint 6.
  • the hub wheel 1 has a raceway surface 7 on the outboard side formed on the outer peripheral surface thereof, and includes a wheel mounting flange 9 for mounting a wheel (not shown). Hub bolts (not shown) for fixing the wheel discs are implanted at equal intervals in the circumferential direction of the wheel mounting flange 9.
  • An inner ring 2 is fitted to a small diameter step portion 12 formed on the outer peripheral surface of the hub wheel 1, and an inboard side raceway surface 8 is formed on the outer peripheral surface of the inner ring 2.
  • the inner ring 2 is press-fitted with an appropriate tightening allowance to prevent creep.
  • the outboard side raceway surface 7 formed on the outer peripheral surface of the hub wheel 1 and the inboard side raceway surface 8 formed on the outer peripheral surface of the inner ring 2 constitute a double row raceway surface.
  • the inner ring 2 is press-fitted into the small-diameter step portion 12 of the knob ring 1 and the end of the small-diameter step portion 12 of the hub wheel 1 is crimped outward to prevent the inner ring 2 from coming off with the crimping portion 11. It is integrated with the hub wheel 1 and preload is applied to the bearing 20.
  • the outer ring 5 has a double-row raceway surface 13, 4 opposite to the raceway surfaces 7, 8 of the hub wheel 1 and the inner ring 2 on the inner circumferential surface, and is mounted on a vehicle body (not shown).
  • Mounting flange 17 is provided.
  • the vehicle body mounting flange 17 is bolted to a knuckle extending from a vehicle suspension system (not shown) using a mounting hole 19.
  • the bearing portion 20 has a double-row annulus ball bearing structure, and raceway surfaces 7, 8 formed on the outer peripheral surfaces of the hub wheel 1 and the inner ring 2, and a raceway surface 13, formed on the inner peripheral surface of the outer ring 5.
  • Rolling between 14 It has a structure in which rolling bodies 3 and 4 in each row are supported at equal intervals in the circumferential direction by cages 21 and 22 with bodies 3 and 4 interposed.
  • a pair of seals 23, 24 that seal the annular space between the outer ring 5, the hub ring 1, and the inner ring 2 so as to be in sliding contact with the outer peripheral surfaces of the hub ring 1 and the inner ring 2 are provided at both ends of the bearing 20. It is fitted to the inner diameter of both ends of 5 to prevent leakage of grease filled inside and intrusion of water and foreign matters from the outside.
  • the constant velocity universal joint 6 is provided at one end of an intermediate shaft (not shown) constituting the drive shaft, a joint outer ring 15 having a track groove 32 formed on the inner peripheral surface, and a joint outer ring 15 A joint inner ring 34 having a track groove 33 opposite to the track groove 32 formed on the outer peripheral surface, and a ball 35 incorporated between the track groove 32 of the joint outer ring 15 and the track groove 33 of the joint inner ring 34.
  • the joint outer ring 15 has a mouth part 25 that accommodates the joint inner ring 34 and the ball 35, and a stem part 27 that extends integrally from the mouth part 25 in the axial direction and has a spline 26 formed on the outer peripheral surface.
  • the stem portion 27 is formed in the inner diameter of the stem portion 27 in a state where the stem portion 27 is inserted into the through hole 31 of the nozzle ring 1 and the shoulder portion 16 of the joint outer ring 15 is abutted against the caulking portion 11 of the hub wheel 1.
  • the constant velocity universal joint 6 is fixed to the nozzle ring 1 by tightening the bolt 30 to the female thread portion 29. Torque can be transmitted by engaging the splines 26 and 28 formed on the outer peripheral surface of the stem portion 27 and the inner peripheral surface of the through hole 31.
  • Patent Document 1 Japanese Unexamined Patent Application Publication No. 2004-353724
  • This stick-slip noise is generated when a rotational torque is applied from the joint outer ring 15 of the constant velocity universal joint 6 to the hub wheel 1 of the bearing section 20 that is stationary when the vehicle starts. Attempts to transmit rotational torque from the outer joint ring 15 to the hub wheel 1 via the splines 26 and 28, but the twisting of the outer joint ring 15 causes the hub ring 1 to be tightened 11 and the shoulder 16 of the outer joint ring 15. A sudden relative slip occurs. This sudden relative slip causes stick-slip noise. appear.
  • This bearing device As a means for preventing the above-described stick-slip noise, there is a bearing device having a structure as shown in FIG. 5 (see, for example, Patent Document 1).
  • This bearing device is provided with a tapered portion 36 in which the cylindrical portion force of the stem portion 27 of the joint outer ring 15 is also connected to the spline 26, and the inner diameter of the inboard side of the hub wheel 1 is also adapted to correspond to the aforementioned tapered portion 36.
  • a cylindrical portion 37 is also provided with a tapered portion 37 connected to the spline 28.
  • An object of the present invention is to provide a wheel bearing device capable of reliably suppressing stick-slip noise and suppressing wear at the abutting portion between the hub wheel and the constant velocity universal joint.
  • An object to which the present invention is applied includes an outer ring having a double row raceway surface formed on the inner periphery, a wheel mounting flange at one end and a double row raceway surface on the outer periphery, and a hub ring and an inner ring.
  • An inner member and a double row rolling element interposed between the raceway surfaces of the outer ring and the inner member, and the hub ring and the inner ring are joined by crimping the end of the small diameter step portion of the hub ring.
  • This is a wheel bearing device in which the stem part of the joint outer ring of the constant velocity universal joint is inserted into the inner diameter of the hub wheel and spline-fitted.
  • This wheel bearing device has a vehicle body mounting flange on the outer periphery of the outer ring, and one of the double-row track surfaces is formed on the outer periphery of the hub wheel. There is.
  • the present invention provides a brake rotor mounted on a wheel mounting flange with an in-row structure, a through hole is provided at the rotation center of the brake rotor, and an inboard of an inner peripheral edge of the through hole is provided.
  • the side end face is a butt face with the stem part, and an axial clearance is provided between the caulking part of the hub ring and the shoulder part of the joint outer ring.
  • the inboard side end surface of the brake rotor attached to the hub wheel is used as the abutting surface with the stem portion
  • the inboard side end surface of the brake rotor and the spline shaft end surface of the stem portion are abutted with each other.
  • the inner peripheral edge of the brake rotor may be extended to the inboard side in the axial direction, and the inboard side end surface of the cylindrical portion may be in contact with the spline shaft end surface of the stem portion of the joint outer ring.
  • a cylindrical member is inserted between the inboard side end surface of the brake rotor and the spline shaft end surface of the stem portion of the joint outer ring, and the inboard side end surface of the brake port and the spline shaft end surface of the stem portion are connected to the cylindrical member. You may try to match them through.
  • the axial clearance is provided between the hub ring tightening portion and the joint outer ring shoulder portion so that the hub ring tightening portion and the joint outer ring shoulder portion do not face each other. Since the ring caulking part and the shoulder of the joint outer ring are not in contact with each other, the source of stick-slip noise can be eliminated.
  • the structure that handles all of the fastening force when the stem part is fixed to the hub wheel in the axial direction is a structure in which the end face on the inboard side of the brake rotor is a butt face with the stem part.
  • the hub wheel and stem part are spline-fitted on the inboard side of the brake rotor. As a result, the torque transmission path force is deviated, so that it is difficult for wear to occur without causing relative slippage.
  • the brake rotor is attached to the wheel mounting flange with an inlay structure, and a through hole is provided at the center of the brake rotor, and the inboard side end surface of the inner peripheral edge of the through hole is defined as the stem portion.
  • the axial clearance is provided between the hub ring crimped part and the joint outer ring shoulder, so that both the hub ring crimped part and joint outer ring shoulder are not butted together.
  • the contact surface pressure in the abutment state between the both is high due to the fastening force when the stem portion is fixed to the hub wheel in the axial direction. Even in this state, the hub wheel and the stem portion are spline-fitted on the inboard side of the brake rotor, so that the torque transmission path force is disengaged. It is hard to occur. As a result, the durability of the wheel bearing device can be improved and the life of the wheel bearing device can be extended.
  • FIGS. 1 to 3 An embodiment of a wheel bearing device according to the present invention will be described in detail below.
  • Each of the embodiments shown in FIGS. 1 to 3 is a bearing device for a drive wheel, and includes a hub wheel 101 and an inner ring 102 which are inner members, double-row rolling elements 103 and 104, an outer ring 105, and a constant velocity universal joint 106 as main components. As a component.
  • the hub wheel 101 has a raceway surface 107 on the outboard side formed on the outer peripheral surface, and an inner ring 102 is fitted to a small-diameter step 112 formed on the outer peripheral surface, and the outer peripheral surface of the inner ring 102 is The track surface 108 on the inboard side is formed.
  • the hub wheel 101 includes a wheel mounting flange 109 for mounting the wheel disk 141 and the brake rotor 142. Hub bolts 110 for fixing the wheel disc 141 and the brake rotor 142 are implanted at equal intervals in the circumferential direction of the wheel mounting flange 109! /.
  • the brake rotor 142 has an inlay structure so that the brake rotor pilot portion 143 formed on the outboard side end surface 101a of the hub wheel 101 can be aligned.
  • a through hole 144 having an inner diameter smaller than the inner diameter of the hub wheel 101 is formed at the rotation center of the brake rotor 142.
  • the wheel disc 141 is fastened and fixed to the hub bolt 110 of the hub wheel 101 by the nut 146 together with the brake rotor 142 while being centered by a wheel pilot portion 145 formed on the side of the brake rotor 142 on the board.
  • the inner ring 102 is press-fitted with an appropriate tightening margin to prevent creep.
  • the outboard side raceway surface 107 formed on the outer peripheral surface of the hub wheel 101 and the inboard side raceway surface 108 formed on the outer peripheral surface of the inner ring 102 constitute a double row raceway surface.
  • the inner ring 102 is press-fitted into the small-diameter step portion 112 of the nozzle ring 101, and the end portion of the small-diameter step portion 112 of the hub wheel 101 is crimped to the outside to prevent the inner ring 102 from coming off with the crimping portion 111. It is integrated with the hub wheel 101 and preload is applied to the bearing 120.
  • the outer ring 105 is formed with double-row raceway surfaces 113 and 114 facing the raceway surfaces 107 and 108 of the hub wheel 101 and the inner ring 102 on the inner peripheral surface, and is attached to the vehicle body (not shown).
  • a flange 117 is provided.
  • the vehicle body mounting flange 117 is bolted to a knuckle extending from a vehicle suspension system (not shown) using the mounting hole 119.
  • Bearing 120 has a double-row angular bearing structure, raceway surfaces 107, 108 formed on the outer peripheral surface of hub ring 101 and inner ring 102, and raceway surface 113 formed on the inner peripheral surface of outer ring 105. , 114, and rolling elements 103, 104 are interposed between them, and the rolling elements 103, 104 in each row are supported at equal intervals in the circumferential direction by retainers 121, 122.
  • a pair of seals 123, 124 that seal the annular space between the outer ring 105, the hub ring 101, and the inner ring 102 so that they are in sliding contact with the outer peripheral surfaces of the hub ring 101 and the inner ring 102 are provided at both ends of the bearing 120. Fits into the inner diameter of both ends of 105, and prevents leakage of grease filled inside and intrusion of water and foreign matter from external force!
  • the constant velocity universal joint 106 is provided at one end of an intermediate shaft (not shown) constituting the drive shaft, and a joint outer ring 115 in which a track groove 132 is formed on the inner peripheral surface, and a joint of the joint outer ring 115.
  • a ball incorporated between a joint inner ring 134 having a track groove 133 formed on the outer peripheral surface thereof and a track groove 133 of the joint outer ring 115 and a track groove 133 of the joint inner ring 134. 135 and power.
  • the joint outer ring 115 has a mouth part 125 that accommodates the joint inner ring 134 and the ball 135, and a stem part 127 that extends integrally from the mouth part 125 in the axial direction and has a spline 126 formed on the outer peripheral surface.
  • the stem portion 127 has a hollow shape having a through hole 147 in the center of the shaft, and a female screw portion 129 is formed on the inboard side of the inner peripheral surface thereof.
  • the stem portion 127 is inserted into the through hole 131 of the hub wheel 101, and the bolt 130 is inserted into the female screw portion 129 formed on the inner diameter of the stem portion 127 from the through hole 144 of the brake rotor 142 and screwed together.
  • the constant velocity universal joint 106 is fastened and fixed to the knob wheel 101.
  • the torque can be transmitted by engaging the stems 127 and 128 with the outer peripheral surface of the stem portion 127 and the inner peripheral surface of the through hole 131 of the hub wheel.
  • the constant velocity universal joint 106 can be fixed to the hub wheel 101 by screwing a nut into a male screw portion formed at the tip of the stem portion 127.
  • FIG. 1 to 3 there are embodiments shown in Figs. 1 to 3 as structures that handle all of the fastening force when the constant velocity universal joint 106 is fixed to the hub 101 in the axial direction.
  • the inboard side end surface 142a of the inner peripheral edge of the brake rotor 142 and the spline shaft end surface 127a of the stem portion 127 of the joint outer ring 115 are brought into contact with each other.
  • the axial length of the stem portion 127 is slightly longer than the axial end surface force of the caulking portion 111 of the hub wheel 101 to the inboard side end surface 142a of the brake rotor 142.
  • the axial clearance n between the two is preferably 2 mm or less, for example.
  • the inner peripheral edge of the brake rotor 142 extends toward the inboard side in the axial direction, and the inboard side end surface 142a of the cylindrical portion 142b is connected to the joint outer ring 115.
  • the spline shaft end surface 127a of the stem portion 127 of the butt is abutted.
  • the axial length of the stem portion 127 can be shortened as compared with the embodiment of FIG. 1 described above, so that the component cost of the constant velocity universal joint 101 can be reduced. .
  • a cylindrical member 148 is provided between the inboard side end surface 142a of the inner periphery of the brake rotor 142 and the spline shaft end surface 127a of the stem portion 127 of the joint outer ring 115.
  • the inboard side end surface 142a of the brake rotor 142 and the spline shaft end surface 127a of the stem portion 127 are brought into contact with each other via the cylindrical member 148.
  • the material of the cylindrical member 148 is not particularly specified as long as the compressive strength and abrasion resistance are appropriate. Therefore, if aluminum is used, it can contribute to light weight. In this embodiment as well, as in the embodiment of FIGS.
  • the inboard side end surface 142a of the brake rotor 142 and the spline shaft end surface 127a of the stem portion 127 are in contact with each other via the cylindrical member 148.
  • An axial clearance n is formed between the caulking portion 111 of the hub wheel 101 and the shoulder portion 116 of the joint outer ring 115.
  • the stem portion 127 of the joint outer ring 115 is inserted into the through hole 131 of the hub ring 101 and the splines 126 and 128 of both are fitted.
  • the shaft end surface 127a of the stem portion 127 is directly connected to the inboard side end surface 142a of the brake rotor 142 or the cylinder before the shoulder portion 116 of the joint outer ring 115 abuts the caulking portion 111 of the hub wheel 101.
  • the joint outer ring 115 can be regulated in position in the axial direction with respect to the hub wheel 101 by abutting with each other via the shaped member 148.
  • the caulking portion 111 of the hub ring 101 and the shoulder 116 of the joint outer ring 115 are not brought into contact with each other, and the caulking portion 111 of the hub ring 101 and the shoulder 116 of the joint outer ring 115 are not brought into contact with each other. Since the clearance n in the axial direction is formed in this manner, the caulking portion 111 of the hub wheel 101 and the shoulder portion 116 of the joint outer ring 115 are brought into a non-contact state, so that the source of stick-slip noise can be eliminated.
  • a seal member 149 such as an O-ring is interposed in the axial clearance n between the caulking portion 111 of the hub wheel 101 and the shoulder portion 116 of the joint outer ring 115.
  • the seal member 149 can prevent intrusion of water and foreign matters from the outside.
  • FIG. 1 is a cross-sectional view showing a configuration in which an impeller side end surface of a brake rotor and a spline shaft end surface of a stem portion are butted in one embodiment of a wheel bearing device according to the present invention.
  • FIG. 2 is a cross-sectional view showing another embodiment of the present invention in which an inboard side end surface of a cylindrical portion of a brake rotor and a spline shaft end surface of a stem portion are brought into contact with each other.
  • FIG. 3 is a cross-sectional view showing a form in which an inboard side end surface of a brake rotor and a spline shaft end surface of a stem portion are butted via a cylindrical member in another embodiment of the present invention.
  • 4] A sectional view showing a conventional example of a wheel bearing device.
  • FIG. 5 is a sectional view showing another conventional example of a wheel bearing device.

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

Abstract

L’invention propose d'éradiquer le bruit de broutage de manière fiable et l’abrasion d’une zone où un moyeu de roue et un joint universel à vitesse constante buttent l’un contre l'autre. Un dispositif de roulement pour une roue comporte une roue extérieure (105), un noyau (101), une rondelle interne (102) et des corps de roulement à doubles rangées de billes (103, 104). Le noyau (101) et la rondelle interne (102) sont intégrés audit dispositif de roulement en agrafant un bout de section d’arrêt de petit diamètre (112) du noyau (101). Un tourillon (127) de joint universel à vitesse constante (106) est inséré dans l’alésage du noyau (101) et fixé par des cannelures. Un disque de frein (142) est attaché au moyeu (101) en utilisant un ensemble de jonction. Un orifice traversant (144) est fourni au centre de la partie rotative du disque de frein (142), tandis que le diamètre de l’orifice traversant (144) est réglé à un diamètre inférieur au diamètre intérieur du moyeu (101). Un côté et une face interne (142a) du disque de frein (142) et une face frontale de l’essieu à cannelures (127a) du tourillon (127) sont aboutés. Un écart axial est fourni entre un écrou de moyeu (111) du moyeu (101) et un épaulement (116) de la rondelle extérieure de joint (115).
PCT/JP2006/303725 2005-03-10 2006-02-28 Dispositif de roulement pour une roue Ceased WO2006095603A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005067390A JP2006248373A (ja) 2005-03-10 2005-03-10 車輪用軸受装置
JP2005-067390 2005-03-10

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WO2006095603A1 true WO2006095603A1 (fr) 2006-09-14

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008078511A1 (fr) * 2006-12-27 2008-07-03 Ntn Corporation Dispositif de roulement pour roue
EP2189674A4 (fr) * 2007-09-18 2011-07-27 Ntn Toyo Bearing Co Ltd Dispositif de palier pour roue
WO2014032834A1 (fr) * 2012-08-28 2014-03-06 Schaeffler Technologies AG & Co. KG Montage de roue comprenant un disque de frein à centrage de roue
US20140239706A1 (en) * 2007-03-22 2014-08-28 Ntn Corporation Bearing device for a wheel
DE102015014523A1 (de) 2015-11-11 2017-05-11 Rolf Jung Bremsscheibe mit ergänzender Spurverbreiterungsfunktion für Personenkraftwagen
WO2018059748A1 (fr) * 2016-09-29 2018-04-05 Continental Teves Ag & Co. Ohg Bol de disque de frein et disque de frein à interface véhicule améliorée
EP3351403A1 (fr) * 2017-01-11 2018-07-25 Audi Ag Roulement de roue pour un véhicule automobile

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Publication number Priority date Publication date Assignee Title
JP2010106917A (ja) * 2008-10-29 2010-05-13 Advics Co Ltd ディスクロータ
JP5641705B2 (ja) * 2009-04-02 2014-12-17 Ntn株式会社 車輪用軸受装置

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Publication number Priority date Publication date Assignee Title
JP2000227132A (ja) * 1998-12-02 2000-08-15 Ntn Corp ブレーキロータ付き車輪軸受装置
JP2004353724A (ja) * 2003-05-28 2004-12-16 Ntn Corp 駆動車輪用軸受装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000227132A (ja) * 1998-12-02 2000-08-15 Ntn Corp ブレーキロータ付き車輪軸受装置
JP2004353724A (ja) * 2003-05-28 2004-12-16 Ntn Corp 駆動車輪用軸受装置

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8382378B2 (en) 2006-12-27 2013-02-26 Ntn Corporation Wheel bearing device
WO2008078511A1 (fr) * 2006-12-27 2008-07-03 Ntn Corporation Dispositif de roulement pour roue
US9511629B2 (en) * 2007-03-22 2016-12-06 Ntn Corporation Bearing device for a wheel
US20140239706A1 (en) * 2007-03-22 2014-08-28 Ntn Corporation Bearing device for a wheel
EP2189674A4 (fr) * 2007-09-18 2011-07-27 Ntn Toyo Bearing Co Ltd Dispositif de palier pour roue
US8801294B2 (en) 2007-09-18 2014-08-12 Ntn Corporation Bearing device for a wheel
EP2940330A1 (fr) * 2007-09-18 2015-11-04 NTN Corporation Dispositif de palier pour roue
US9308777B2 (en) 2007-09-18 2016-04-12 Ntn Corporation Bearing device for a wheel
WO2014032834A1 (fr) * 2012-08-28 2014-03-06 Schaeffler Technologies AG & Co. KG Montage de roue comprenant un disque de frein à centrage de roue
DE102015014523A1 (de) 2015-11-11 2017-05-11 Rolf Jung Bremsscheibe mit ergänzender Spurverbreiterungsfunktion für Personenkraftwagen
WO2018059748A1 (fr) * 2016-09-29 2018-04-05 Continental Teves Ag & Co. Ohg Bol de disque de frein et disque de frein à interface véhicule améliorée
CN109891115A (zh) * 2016-09-29 2019-06-14 大陆-特韦斯贸易合伙股份公司及两合公司 制动盘毂和具有改进的车辆接口的制动盘
EP3351403A1 (fr) * 2017-01-11 2018-07-25 Audi Ag Roulement de roue pour un véhicule automobile
US10267355B2 (en) 2017-01-11 2019-04-23 Audi Ag Wheel bearing for a motor vehicle

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