WO2007069654A1 - Bearing device for wheel and axle module with the same - Google Patents

Bearing device for wheel and axle module with the same Download PDF

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Publication number
WO2007069654A1
WO2007069654A1 PCT/JP2006/324862 JP2006324862W WO2007069654A1 WO 2007069654 A1 WO2007069654 A1 WO 2007069654A1 JP 2006324862 W JP2006324862 W JP 2006324862W WO 2007069654 A1 WO2007069654 A1 WO 2007069654A1
Authority
WO
WIPO (PCT)
Prior art keywords
wheel
bearing device
diameter
rolling surface
balls
Prior art date
Application number
PCT/JP2006/324862
Other languages
French (fr)
Japanese (ja)
Inventor
Kiyoshige Yamauchi
Original Assignee
Ntn Corporation
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 Corporation filed Critical Ntn Corporation
Publication of WO2007069654A1 publication Critical patent/WO2007069654A1/en

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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
    • F16C19/18—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
    • F16C19/187—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 all four raceways integrated on parts other than race rings, e.g. fourth generation hubs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/001—Hubs with roller-bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0078—Hubs characterised by the fixation of bearings
    • B60B27/0084—Hubs characterised by the fixation of bearings caulking to fix inner 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
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
    • F16D3/205—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part
    • F16D3/2055—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part having three pins, i.e. true tripod joints
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/2237—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts where the grooves are composed of radii and adjoining straight lines, i.e. undercut free [UF] type joints
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/84—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/80—Pitch circle diameters [PCD]
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member

Definitions

  • Wheel bearing device and axle module including the same
  • the present invention relates to a wheel bearing device that rotatably supports a wheel of an automobile or the like with respect to a suspension device, and particularly, a fourth generation that achieves higher rigidity and improved durability along with a light weight external component.
  • the present invention relates to a wheel bearing device having a structure and an axle module including the same.
  • a wheel bearing device that rotatably supports a wheel of an automobile or the like has a structure in which a double-row rolling bearing called a first generation is independently used, and has a vehicle body mounting flange integrally with an outer member. It evolved into the second generation, and the third generation in which one inner rolling surface of the double row rolling bearing was integrally formed on the outer periphery of the hub ring integrally having the wheel mounting flange was further added to this wheel. A constant-velocity universal joint is integrated, and the 4th generation is developed in which the other inner rolling surface of the double row rolling bearing is integrally formed on the outer periphery of the outer joint member constituting this constant velocity universal joint. Yes.
  • the wheel bearing device shown in FIG. 3 has a light-weight, “compact” third-generation structure in which a hub wheel 50, a double row rolling bearing 51, and a constant velocity universal joint 52 are unitized. It has been done.
  • the double row rolling bearing 51 includes an outer member 53, an inner member 54, and a double IJ Bonole 55, 55 accommodated between the two members.
  • the outer member 53 integrally has a vehicle body mounting flange 53c attached to a knuckle constituting a suspension device (not shown) on the outer periphery, and double row outer rolling surfaces 53a, 53b are formed on the inner periphery.
  • the diameter of the inner side rolling surface 53a on the outer side is set to be smaller than the diameter of the inner side rolling surface 53b on the inner side.
  • the inner member 54 has a hub ring 50, an outer joint member 58, which will be described later, integrally formed with the hub ring 50, and a separate inner ring 56 press-fitted into the outer joint member 58. is doing.
  • the hub wheel 50 has a wheel mounting flange 57 for mounting a wheel (not shown) at one end integrally, and is opposed to the double row outer raceway surfaces 53a, 53b on the outer periphery (outer side).
  • Inner rolling surface 50a is directly formed, and the outer circumference of inner ring 56 is double row outer rolling surface 53a. 53b, the other (inner side) inner raceway surface 56a is formed. Thereby, the diameter force of the inner side rolling surface 50a on the outer side is set to be smaller than the diameter of the inner side rolling surface 56a on the inner side.
  • the constant velocity universal joint 52 has an outer joint member 58 composed of a cup-shaped mouth portion 59 and a shoulder portion 60 forming the bottom of the mouth portion 59, and the outer periphery of the outer joint member 58 has an inner periphery.
  • a curved track groove 58a is formed.
  • the inner ring 56 is press-fitted into the outer diameter of the mouse part 59 and is fixed in the axial direction by a retaining ring 61.
  • the hub wheel 62, the double row rolling bearing 63 and the constant velocity universal joint 64 are configured as a unit.
  • the double row rolling bearing 63 includes an outer member 65, an inner member 66, and a double IJ Bonore 67, 67 housed between the two members.
  • the outer member 65 is integrally formed with a vehicle body mounting flange 65b that is attached to a knuckle constituting a suspension device, and is formed with double row outer rolling surfaces 65a, 65a on the inner periphery, not shown on the outer periphery. It is.
  • the inner member 66 includes a hub wheel 62 and an outer joint member 71 (described later) fitted in the hub wheel 62.
  • the hub wheel 62 is integrally provided with a wheel mounting flange 68 for mounting a wheel (not shown) at one end thereof, and is opposed to the double row outer raceway surfaces 65a, 65a on the outer periphery (outer side).
  • Inner rolling surface 62a and a small cylindrical step 62b extending in the axial direction from the inner rolling surface 62a. Is formed.
  • Hub bolts 69 are implanted in the circumferential direction of the wheel mounting flange 68. Then, the surface hardness is hardened to a range of 58 to 64 HRC by induction hardening from the seal land portion in which the outer seal 78 is in sliding contact to the inner rolling surface 62a and the small diameter step portion 62b.
  • an uneven portion 70 is formed on the inner periphery of the hub wheel 62, and the surface is hardened to a predetermined surface hardness by induction hardening.
  • the concavo-convex part 70 is formed in the shape of an iris knurl, and also has a cross groove force constituted by a plurality of annular grooves formed independently by turning or the like and a plurality of axial grooves formed by broaching or the like substantially orthogonal to each other. .
  • the constant velocity universal joint 64 includes an outer joint member 71, a joint inner ring 72, a cage 73, and a torque transmission ball 74.
  • the outer joint member 71 has a cup-shaped mouth portion 75, a shoulder portion 76 forming the bottom of the mouth portion 75, and a cylindrical shaft portion 77 extending in the axial direction from the shoulder portion 76.
  • the shaft portion 77 has an in-row portion 77a that is cylindrically fitted to the small-diameter step portion 62b of the hub wheel 62 through a predetermined radial clearance, and a fitting portion 77b that is formed at the end of the in-row portion 77a. Yes.
  • An inner rolling surface 71a (inner side) is formed. Then, the surface hardness is set to a range of 58 to 64 HRC by induction hardening from the outer peripheral surface to which the inner seal 79 is fitted to the inner rolling surface 71a and the shaft portion 77.
  • the fitting portion 77b is left as it is after forging.
  • Patent Document 1 Japanese Patent Laid-Open No. 11 151904
  • Patent Document 2 Japanese Patent Laid-Open No. 2004-76872
  • the present invention has been made in view of such circumstances, and provides a wheel bearing device having a fourth generation structure that is light-weighted, compact, highly rigid, and improved in durability. It is an object.
  • the invention described in claim 1 is a wheel bearing device in which a hub wheel, a double row rolling bearing, and a constant velocity universal joint are unitized.
  • the double-row rolling bearing has a double-row outer raceway formed on the inner periphery, a reference provided for fitting a body mounting flange on the outer periphery and a mating member on the inner side of the body mounting flange.
  • An outer member formed with a surface, a wheel mounting flange at one end integrally, one inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a shaft from the inner rolling surface
  • a hub ring formed with a cylindrical small-diameter step portion extending in the direction, the other inner rolling surface that is fitted in the hub ring and faces the outer rolling surface of the double row on the outer periphery, and the inner rolling surface
  • An inner member that is an outer joint member force of the constant velocity universal joint integrally formed with a shaft portion extending in an axial direction from the surface;
  • the inner member and a double row ball group accommodated in a freely rolling manner between both rolling surfaces of the outer member, and the end of the shaft portion is plastically deformed and crimped to the hub wheel.
  • the pitch circle diameter of the inner side ball group of the double row ball group is equal to that of the outer side ball group. It is set to a diameter larger than the pitch circle diameter and A configuration was adopted in which the number of balls was set larger than the number of balls in the outer ball group.
  • the inner of the double row ball group By setting the pitch circle diameter of the ball group on the side larger than the pitch circle diameter of the ball group on the outer side, the bearing span (the direction of action of the force applied to both rolling surfaces without increasing the axial dimension) (Interval of the intersection between the line of action and the axis) can be increased. Since the number of balls in the inner side ball group is set to be larger than the number of balls in the outer side ball group, light weight and compactness can be achieved and the bearing rigidity can be increased. Further, since the number of balls in the inner ball group is increased, the load capacity of the bearing is increased and the life of the bearing can be extended. Therefore, it is possible to provide a wheel bearing device having a fourth generation structure that achieves higher rigidity and improved durability.
  • a hardened concave and convex portion is formed on the inner diameter of the hub wheel, and the hollow fitting portion formed in the shaft portion is expanded in diameter. If the hub wheel and the outer joint member are integrally plastically joined by grooving the uneven part, it is not necessary to tighten the nut tightly and manage the preload amount. It is possible to improve the strength and durability of the hub wheel and maintain the preload for a long time.
  • a drive shaft comprising the wheel bearing device according to any one of claims 1 to 3 and having one end connected to the constant velocity universal joint on the outboard side,
  • An axle module consisting of an inboard sliding type constant velocity universal joint connected to the other end of this drive shaft will reduce the unsprung weight while simplifying disassembly and assembly into the vehicle.
  • the suspension device Make up knuckle
  • the axle module can be easily inserted into the boot, and the boot can be assembled without interfering with the knuckle.
  • a wheel bearing device is a wheel bearing device in which a hub ring, a double row rolling bearing, and a constant velocity universal joint are unitized, and the double row rolling bearing has an inner circumference.
  • the wheel mounting flange is integrally formed on the outer periphery, one inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a cylindrical small-diameter stepped portion extending in the axial direction from the inner rolling surface.
  • An inner member which is an outer joint member force of the constant velocity universal joint formed integrally, and the inner member and the outer member A double row ball group accommodated in a freely rolling manner between both rolling surfaces of the member, and plastically deforming an end portion of the shaft portion and crimping the hub wheel to the hub wheel, and the outer joint.
  • the pitch circle diameter of the inner side ball group in the double row ball group is set larger than the pitch circle diameter of the outer side ball group.
  • a wheel bearing device in which a hub wheel, a double row rolling bearing, and a constant velocity universal joint are unitized, and the double row rolling bearing has a double row outer rolling surface formed on an inner periphery thereof. It has a vehicle body mounting flange on the outer periphery, an outer member formed with a reference surface for fitting with a mating member on the inner side of the vehicle body mounting flange, and a wheel mounting flange on one end. , Outer circumference And a hub ring formed with one inner rolling surface facing the outer rolling surface of the double row, a cylindrical small-diameter step portion extending in the axial direction from the inner rolling surface, and an internal fit in the hub ring.
  • the constant velocity universal joint is integrally formed on the outer periphery with the other inner rolling surface facing the outer rolling surface of the double row and a cylindrical shaft portion extending in the axial direction from the inner rolling surface.
  • the inner member of the outer joint member and a double row ball group that is slidably accommodated between the rolling surfaces of the inner member and the outer member, and is hardened on the inner diameter of the hub wheel.
  • the pitch circle diameter of the inner-side ball group of the double-row ball group has an outer one side.
  • the balls of the double row ball group are the same size, and the number of balls of the inner side ball group is the same as the number of balls of the ball side of the outer side. It is set more than the number.
  • FIG. 1 is a longitudinal sectional view showing an embodiment of a wheel bearing device according to the present invention
  • FIG. 2 is a longitudinal sectional view showing an axle module to which the wheel bearing device of FIG. 1 is applied.
  • the side closer to the outer side of the vehicle when assembled to the vehicle is the outer side (left side in the drawing), and the side closer to the center is the inner side (right side in the drawing) t.
  • the wheel bearing device includes a hub wheel 1, a double row rolling bearing 2 and a constant velocity universal joint 3 which are unitized.
  • the double row rolling bearing 2 includes an outer member 4, an inner member 5, and double rows of balls 6a and 6b.
  • the inner member 5 includes a hub wheel 1 and an outer joint member 14 which is fitted into the hub wheel 1 and will be described later.
  • the outer member 4 is made of medium carbon steel containing 0.40-0.80 wt% of carbon such as S53C, and has a vehicle body mounting flange 4c integrally attached to the vehicle body (not shown) on the outer periphery.
  • the outer circumferential rolling surfaces 4a and 4b are formed in an arc shape on the inner circumference.
  • the double row outer rolling surfaces 4a and 4b are hardened to a surface hardness of 58 to 64HRC by induction hardening.
  • the hub wheel 1 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and has a wheel mounting flange 7 for mounting a wheel to an end on one side of the outer wheel.
  • This wheel mounting A plurality of hub bolts 8 are planted at equal intervals in the circumferential direction of the flange 7.
  • a cylindrical small diameter step lb extending in the direction is formed.
  • the surface hardness is hardened to a range of 58 to 64 HRC by induction hardening from the seal land portion 7a with which the outer seal 10 is in sliding contact to the inner rolling surface la and the small diameter step portion lb.
  • This provides sufficient mechanical strength against the rotational bending load applied to the wheel mounting flange 7 by force, which improves the wear resistance of the seal land portion 7a that is the base of the wheel mounting flange 7.
  • the durability of the hub wheel 1 is improved.
  • An uneven portion 12 is formed on the inner periphery of the hub wheel 1, and the surface is hardened by heat treatment so that the surface hardness is in the range of 54 to 64HRC.
  • the concave and convex portion 12 is formed in the shape of an iris knurl, and is a cross formed by a plurality of annular grooves formed independently by turning or the like and a plurality of axial grooves formed by broaching or the like substantially orthogonal to each other. There is also a cross groove force constituted by grooves or spiral grooves inclined with respect to each other.
  • the convex portion of the concave-convex portion 12 has a tip portion formed in a spire shape such as a triangle shape in order to ensure good biting property.
  • the constant velocity universal joint 3 includes an outer joint member 14, a joint inner ring 15, a cage 16, and a torque transmission ball 17.
  • the outer joint member 14 is made of medium carbon steel containing carbon 0.40-0.80 wt% such as S53C, and has a cup-shaped mouth portion 18, a shoulder portion 19 that forms the bottom portion of the mouth portion 18, and the shoulder portion 19.
  • a cylindrical shaft portion 20 extending in the axial direction from is integrally formed.
  • the shaft portion 20 is formed with an in-row portion 20a that is cylindrically fitted to the small-diameter step portion lb of the hub wheel 1 through a predetermined radial clearance, and a fitting portion 20b is formed at the end of the in-row portion 20a.
  • an axially extending track groove 18 a having a curved portion is formed on the inner periphery of the mouth portion 18, and a track groove 15 a corresponding to the track groove 18 a is formed on the outer periphery of the joint inner ring 15. ing.
  • a torque transmission ball 17 is accommodated between the track grooves 18a and 15a via a cage 16.
  • the other (inner side) arcuate inner rolling surface 14 a facing the double row outer rolling surfaces 4 a, 4 b is formed.
  • the surface hardness is hardened within the range of 58 to 64HRC by induction hardening from the outer peripheral surface where the track groove 18a and the inner seal 11 are fitted to the inner rolling surface 14a and the shaft portion 20. ing.
  • the fitting portion 20b of the shaft portion 20 is left as it is after forging.
  • Double row balls 6a and 6b are accommodated between double row outer raceway surfaces 4a and 4b of outer member 4 and double row inner raceway surfaces la and 14a opposite to each other, and retainer It is held by 9a and 9b so that it can roll freely.
  • seals 10 and 11 are attached to the end of the outer member 4 to prevent leakage of lubricating grease sealed inside the bearing and intrusion of rainwater and dust into the external force bearing.
  • These double-row rolling bearings 2 are so-called back-fitting type double-rows in which the acting lines of the force applied to the rolling surfaces 4a, la and 4b, 14a are separated in the axial direction toward the axial center. Constructs an anguilla ball bearing.
  • the double row rolling elements 6a and 6b are temporarily assembled on the double row outer rolling surfaces 4a and 4b of the outer member 4 via the cages 9a and 9b, and seals are provided at both ends of the outer member 4. 10 and 11 are installed.
  • the hub wheel 1 and the outer joint member 14 are also inserted in both side forces of the outer member 4, and the shoulder 19 of the outer joint member 14 is abutted against the end surface of the small-diameter stepped portion lb of the hub wheel 1 so that the butt state is achieved.
  • the shaft portion 20 of the outer joint member 14 is fitted inside the nove ring 1.
  • a diameter expansion jig such as a mandrel is pushed into the inner diameter of the fitting portion 20b in the shaft portion 20 to expand the diameter of the fitting portion 20b, and the fitting portion 20b is formed on the concave and convex portion 12 of the nozzle ring 1.
  • the hub wheel 1 and the outer joint member 14 are integrally plastically joined to complete the process. This eliminates the need to control the preload by tightening with a nut or the like as in the past, so that it is possible to achieve a lightweight 'compact' and improve the strength and durability of the hub wheel 1. In addition, the preload amount can be maintained for a long time. End caps 13a and 13b are attached to the open end of the hub wheel 1 and the hollow shaft 20 to prevent rainwater and the like from entering the plastic coupling portion and causing the portion to erupt. The grease enclosed in the part 18 is prevented from leaking to the outside.
  • the shaft portion of the outer joint member is connected to the hub wheel via a selection. So that torque can be transmitted, and the end of the shaft is plastically deformed radially outward to form a crimped portion, and both members are fixed in the axial direction by the crimped portion.
  • a caulking method may be adopted.
  • the pitch circle diameter PCDi of the inner-side ball 6b is set larger than the pitch circle diameter PCDo of the outer-side ball 6a.
  • the outer diameter of these double-row balls 6a and 6b is the same force. Because of the difference in pitch circle diameter PCDo and PCDi, the number of inner-side balls 6b is set larger than the number of outer-side balls 6a. Yes.
  • the outer diameters of the double-row balls 6a and 6b it is possible to eliminate the problem of misassembly in the assembly process, reduce the manufacturing cost, and improve the reliability of quality. To do.
  • the groove bottom diameter of the inner rolling surface 14a of the outer joint member 14 in the inner member 5 is the same as that of the hub wheel 1 due to the difference in pitch circle diameters PCDo and PCDi of the left and right balls 6a and 6b.
  • the inner rolling surface is formed with a diameter larger than the groove bottom diameter of la.
  • the groove bottom diameter of the outer rolling surface 4b on the inner side is the groove bottom of the outer rolling surface 4a on the outer side. The diameter is larger than the diameter.
  • the inner-side inner rolling surface 14a is formed directly on the outer periphery of the shoulder portion 19 of the outer joint member 14, so that the pitch circle of the inner-side ball 6b is formed.
  • the diameter PCDi can be set larger than the pitch circle diameter PCDo of the outer ball 6a, and the number of balls 6b can be set more on the inner side than on the outer side. 'Compactness can be achieved, bearing rigidity can be increased and bearing life can be extended.
  • FIG. 2 is a longitudinal sectional view showing an axle module to which the wheel bearing device described above is applied.
  • the axle module includes a pair of constant velocity universal joints 3 and 21 and a drive shaft 22 connected to the constant velocity universal joints 3 and 21.
  • One end of the drive shaft 22 is fitted into the joint inner ring 15 of the constant velocity universal joint 3 on the outboard side via a selection, and the other end is slid on the inboard side fixed to a differential (not shown).
  • a dynamic constant velocity universal joint 21 Connected to a dynamic constant velocity universal joint 21!
  • This constant velocity universal joint 21 on the inboard side includes an outer joint member 23, a tripod member 24 having three leg shafts 24a projecting from the outer periphery at equal intervals, and needles on these leg shafts 24a.
  • the outer joint member 23 includes a cylindrical outer tube portion 27 formed of medium carbon steel containing carbon 0.40 to 0.80 wt% such as S53C, and a shaft portion in which the bottom portion force of the outer tube portion 27 extends in the axial direction. It has 28 as one.
  • a selection (or spline) 28a for fixing to the differential is formed on the outer periphery of the shaft portion 28.
  • Three linear track grooves 27a extending in the axial direction are formed on the inner periphery of the outer cylindrical portion 27, and the roller 26 rolls on the track grooves 27a.
  • a predetermined hardened layer is formed on the surface of the track groove 27a by induction hardening or the like.
  • a boot 29 having a synthetic rubber equivalent force is attached to the outer periphery of the outer cylinder part 27 on the opening side, and leakage of grease sealed in the outer cylinder part 27 and rainwater and dust enter the joint from the outside. This is preventing.
  • the outer cylindrical portion 27 is not limited to a cylindrical shape, and for example, the outer periphery may be formed in a flower shape corresponding to the track groove 27a. Also, the outer cylindrical portion 27 is not limited to the shaft portion 28 and is differentially formed. A structure in which a mounting flange for fixing is integrally formed may be used.
  • the force illustrated here as a triboard type for the constant velocity universal joint 21 on the inboard side is not limited to this, but a sliding type constant velocity universal joint may be used, for example, a triboard type having a different structure, such as a ball Double offset type constant velocity universal joints (DOJ) using
  • DOJ ball Double offset type constant velocity universal joints
  • the outer diameter Da of the reference surface 4d of the outer member 4 serving as a fitting portion with the knuckle is the maximum outer diameter Db, Dc of the constant velocity universal joints 3 and 21 (here The maximum outer diameter of the boots 30 and 29 is larger (Da> Db ⁇ Dc).
  • the wheel bearing device according to the present invention can be applied to a wheel bearing device of a fourth generation structure in which a hub wheel, a double row rolling bearing, and a constant velocity universal joint are unitized.
  • FIG. 1 is a longitudinal sectional view showing an embodiment of a wheel bearing device according to the present invention.
  • FIG. 2 is a longitudinal sectional view showing an axle module to which the wheel bearing device of FIG. 1 is applied.
  • FIG. 3 is a longitudinal sectional view showing a conventional wheel bearing device.
  • FIG. 4 is a longitudinal sectional view showing another conventional wheel bearing device.

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

Abstract

[PROBLEMS] A bearing device for a wheel, having a fourth-generation structure. The bearing device is reduced in weight and size and has increased rigidity and durability. [MEANS FOR SOLVING PROBLEMS] In the bearing device, a hardened uneven surface section (12) is formed on the bore of a hub ring (1), and a fitting section (20b) formed on a shaft section (20) is expanded in diameter to make it bite into the uneven surface section (12), thereby the hub ring (1) and an outer joint member (14) are integrally plastically joined to each other. The pitch circle diameter (PCDi) of inner balls (6b) of double-row balls is set greater than the pitch circle diameter (PCDo) of outer balls (6a), the double-row balls (6a, 6b) have the same size, and the number of the inner balls (6b) is more than that of the outer balls. The bearing is light in weight and compact and has increased rigidity and service life.

Description

明 細 書  Specification
車輪用軸受装置およびこれを備えたアクスルモジュール  Wheel bearing device and axle module including the same
技術分野  Technical field
[0001] 本発明は、自動車等の車輪を懸架装置に対して回転自在に支承する車輪用軸受 装置、特に、軽量 'コンパ外化と共に、高剛性化と耐久性の向上を図った第 4世代構 造の車輪用軸受装置およびこれを備えたアクスルモジュールに関するものである。 背景技術  [0001] The present invention relates to a wheel bearing device that rotatably supports a wheel of an automobile or the like with respect to a suspension device, and particularly, a fourth generation that achieves higher rigidity and improved durability along with a light weight external component. The present invention relates to a wheel bearing device having a structure and an axle module including the same. Background art
[0002] 自動車等の車輪を回転自在に支承する車輪用軸受装置は、第 1世代と称される複 列の転がり軸受を単独に使用する構造から、外方部材に車体取付フランジを一体に 有する第 2世代に進化し、さらに、車輪取付フランジを一体に有するハブ輪の外周に 複列の転がり軸受の一方の内側転走面が一体に形成された第 3世代、さらにこのノ、 ブ輪に等速自在継手が一体化され、この等速自在継手を構成する外側継手部材の 外周に複列の転がり軸受の他方の内側転走面が一体に形成された第 4世代のもの まで開発されている。  [0002] A wheel bearing device that rotatably supports a wheel of an automobile or the like has a structure in which a double-row rolling bearing called a first generation is independently used, and has a vehicle body mounting flange integrally with an outer member. It evolved into the second generation, and the third generation in which one inner rolling surface of the double row rolling bearing was integrally formed on the outer periphery of the hub ring integrally having the wheel mounting flange was further added to this wheel. A constant-velocity universal joint is integrated, and the 4th generation is developed in which the other inner rolling surface of the double row rolling bearing is integrally formed on the outer periphery of the outer joint member constituting this constant velocity universal joint. Yes.
[0003] 図 3に示す車輪用軸受装置は、軽量 'コンパクトィ匕を図った第 3世代構造で、ハブ 輪 50と複列の転がり軸受 51および等速自在継手 52とがユニットィ匕して構成されてい る。複列の転がり軸受 51は、外方部材 53と内方部材 54と、両部材間に収容された 複歹 IJのボーノレ 55、 55とを備えて!/、る。  The wheel bearing device shown in FIG. 3 has a light-weight, “compact” third-generation structure in which a hub wheel 50, a double row rolling bearing 51, and a constant velocity universal joint 52 are unitized. It has been done. The double row rolling bearing 51 includes an outer member 53, an inner member 54, and a double IJ Bonole 55, 55 accommodated between the two members.
[0004] 外方部材 53は、外周に図示しない懸架装置を構成するナックルに取り付けられる 車体取付フランジ 53cを一体に有し、内周に複列の外側転走面 53a、 53bが形成さ れている。ここで、アウター側の内側転走面 53aの直径は、インナー側の内側転走面 53bの直径よりも小径に設定されている。一方、内方部材 54は、ハブ輪 50と、このハ ブ輪 50と一体に構成された後述する外側継手部材 58と、この外側継手部材 58に圧 入された別体の内輪 56とを有している。  [0004] The outer member 53 integrally has a vehicle body mounting flange 53c attached to a knuckle constituting a suspension device (not shown) on the outer periphery, and double row outer rolling surfaces 53a, 53b are formed on the inner periphery. Yes. Here, the diameter of the inner side rolling surface 53a on the outer side is set to be smaller than the diameter of the inner side rolling surface 53b on the inner side. On the other hand, the inner member 54 has a hub ring 50, an outer joint member 58, which will be described later, integrally formed with the hub ring 50, and a separate inner ring 56 press-fitted into the outer joint member 58. is doing.
[0005] ハブ輪 50は、一端部に車輪（図示せず)を取り付けるための車輪取付フランジ 57を 一体に有し、外周に複列の外側転走面 53a、 53bに対向する一方 (アウター側）の内 側転走面 50aが直接形成されると共に、内輪 56の外周には複列の外側転走面 53a 、 53bに対向する他方 (インナー側）の内側転走面 56aが形成されている。これにより 、アウター側の内側転走面 50aの直径力 インナー側の内側転走面 56aの直径よりも 小径に設定されている。 [0005] The hub wheel 50 has a wheel mounting flange 57 for mounting a wheel (not shown) at one end integrally, and is opposed to the double row outer raceway surfaces 53a, 53b on the outer periphery (outer side). ) Inner rolling surface 50a is directly formed, and the outer circumference of inner ring 56 is double row outer rolling surface 53a. 53b, the other (inner side) inner raceway surface 56a is formed. Thereby, the diameter force of the inner side rolling surface 50a on the outer side is set to be smaller than the diameter of the inner side rolling surface 56a on the inner side.
[0006] 等速自在継手 52は、カップ状のマウス部 59と、このマウス部 59の底部をなす肩部 60とからなる外側継手部材 58を有し、この外側継手部材 58の内周には曲線状のト ラック溝 58aが形成されている。内輪 56はマウス部 59の外径に圧入され、止め輪 61 によって軸方向に固定されて 、る。  [0006] The constant velocity universal joint 52 has an outer joint member 58 composed of a cup-shaped mouth portion 59 and a shoulder portion 60 forming the bottom of the mouth portion 59, and the outer periphery of the outer joint member 58 has an inner periphery. A curved track groove 58a is formed. The inner ring 56 is press-fitted into the outer diameter of the mouse part 59 and is fixed in the axial direction by a retaining ring 61.
[0007] 外方部材 53と内方部材 54の両転走面間には複列のボール 55、 55が転動自在に 収容されている。これら複列のボール 55、 55のうちアウター側のボール 55のピッチ 円直径は、インナー側のボール 55のピッチ円直径よりも小さく設定されている。これ により、外方部材 53のアウター側の外径を小さくすることができ、ハブ輪 50の車輪取 付フランジ 57を小さくできて軽量 'コンパクトィ匕を図ることができる（例えば、特許文献 1参照。）。  [0007] Between the rolling surfaces of the outer member 53 and the inner member 54, double-row balls 55, 55 are accommodated so as to roll freely. Of these double-row balls 55, 55, the pitch circle diameter of the outer side ball 55 is set smaller than the pitch circle diameter of the inner side ball 55. As a result, the outer diameter of the outer side of the outer member 53 can be reduced, and the wheel mounting flange 57 of the hub wheel 50 can be reduced to achieve a lighter and more compact design (for example, see Patent Document 1). .)
[0008] ところが、このような車輪用軸受装置にあっては、外側継手部材 58のマウス部 59に 内輪 56が固定される構造のため、軸方向には確かにコンパクトィ匕される力 外方部 材 53の外径自体が大きくなり、軽量ィ匕を阻害するだけでなぐナックルをはじめとする 周辺部品の設計変更を伴い好ましくない。こうした問題を解決したものとして、図 4に 示す車輪用軸受装置が知られている。この車輪用軸受装置は第 4世代構造と称され However, in such a wheel bearing device, since the inner ring 56 is fixed to the mouth portion 59 of the outer joint member 58, the force that is surely compacted in the axial direction. The outer diameter of the member 53 itself is increased, which is not preferable due to a design change of peripheral parts such as a knuckle that only obstructs light weight. A wheel bearing device shown in Fig. 4 is known as a solution to these problems. This wheel bearing device is called the 4th generation structure.
、ハブ輪 62と複列の転がり軸受 63および等速自在継手 64とがユニットィ匕して構成さ れている。複列の転がり軸受 63は、外方部材 65と内方部材 66と、両部材間に収容 された複歹 IJのボーノレ 67、 67とを備えて! /、る。 The hub wheel 62, the double row rolling bearing 63 and the constant velocity universal joint 64 are configured as a unit. The double row rolling bearing 63 includes an outer member 65, an inner member 66, and a double IJ Bonore 67, 67 housed between the two members.
[0009] 外方部材 65は、外周に図示しな 、懸架装置を構成するナックルに取り付けられる 車体取付フランジ 65bを一体に有し、内周に複列の外側転走面 65a、 65aが形成さ れている。一方、内方部材 66は、ハブ輪 62と、このハブ輪 62に内嵌された後述する 外側継手部材 71とを有して 、る。  [0009] The outer member 65 is integrally formed with a vehicle body mounting flange 65b that is attached to a knuckle constituting a suspension device, and is formed with double row outer rolling surfaces 65a, 65a on the inner periphery, not shown on the outer periphery. It is. On the other hand, the inner member 66 includes a hub wheel 62 and an outer joint member 71 (described later) fitted in the hub wheel 62.
[0010] ハブ輪 62は、一端部に車輪（図示せず)を取り付けるための車輪取付フランジ 68を 一体に有し、外周に複列の外側転走面 65a、 65aに対向する一方 (アウター側）の内 側転走面 62aと、この内側転走面 62aから軸方向に延びる円筒状の小径段部 62bが 形成されている。車輪取付フランジ 68の周方向等配にはハブボルト 69が植設されて いる。そして、アウター側のシール 78が摺接するシールランド部から内側転走面 62a および小径段部 62bに亙って高周波焼入れによって表面硬さを 58〜64HRCの範 囲に硬化処理されている。 [0010] The hub wheel 62 is integrally provided with a wheel mounting flange 68 for mounting a wheel (not shown) at one end thereof, and is opposed to the double row outer raceway surfaces 65a, 65a on the outer periphery (outer side). ) Inner rolling surface 62a and a small cylindrical step 62b extending in the axial direction from the inner rolling surface 62a. Is formed. Hub bolts 69 are implanted in the circumferential direction of the wheel mounting flange 68. Then, the surface hardness is hardened to a range of 58 to 64 HRC by induction hardening from the seal land portion in which the outer seal 78 is in sliding contact to the inner rolling surface 62a and the small diameter step portion 62b.
[0011] また、ハブ輪 62の内周には凹凸部 70が形成され、高周波焼入れによって表面が 所定の表面硬さに硬化処理されている。凹凸部 70はアヤメローレット状に形成され、 旋削等により独立して形成された複数の環状溝と、ブローチ加工等により形成された 複数の軸方向溝とを略直交させて構成した交叉溝力もなる。  [0011] Further, an uneven portion 70 is formed on the inner periphery of the hub wheel 62, and the surface is hardened to a predetermined surface hardness by induction hardening. The concavo-convex part 70 is formed in the shape of an iris knurl, and also has a cross groove force constituted by a plurality of annular grooves formed independently by turning or the like and a plurality of axial grooves formed by broaching or the like substantially orthogonal to each other. .
[0012] 等速自在継手 64は、外側継手部材 71と継手内輪 72、ケージ 73、およびトルク伝 達ボール 74とからなる。外側継手部材 71は、カップ状のマウス部 75と、このマウス部 75の底部をなす肩部 76と、この肩部 76から軸方向に延びる円筒状の軸部 77がー 体に形成されている。この軸部 77は、ハブ輪 62の小径段部 62bに所定の径方向す きまを介して円筒嵌合するインロウ部 77aと、このインロウ部 77aの端部に嵌合部 77b がそれぞれ形成されている。  The constant velocity universal joint 64 includes an outer joint member 71, a joint inner ring 72, a cage 73, and a torque transmission ball 74. The outer joint member 71 has a cup-shaped mouth portion 75, a shoulder portion 76 forming the bottom of the mouth portion 75, and a cylindrical shaft portion 77 extending in the axial direction from the shoulder portion 76. . The shaft portion 77 has an in-row portion 77a that is cylindrically fitted to the small-diameter step portion 62b of the hub wheel 62 through a predetermined radial clearance, and a fitting portion 77b that is formed at the end of the in-row portion 77a. Yes.
[0013] 肩部 76の外周には、外方部材 65の複列の外側転走面 65a、 65aに対向する他方  [0013] On the outer periphery of the shoulder 76, the other side of the outer member 65 facing the double-row outer raceway 65a, 65a
(インナー側）の内側転走面 71aが形成されている。そして、インナー側のシール 79 が嵌合する外周面から内側転走面 71aおよび軸部 77に亙って高周波焼入れによつ て表面硬さを 58〜64HRCの範囲に硬化処理されている。ここで、嵌合部 77bは鍛 造後の生のままとされて 、る。  An inner rolling surface 71a (inner side) is formed. Then, the surface hardness is set to a range of 58 to 64 HRC by induction hardening from the outer peripheral surface to which the inner seal 79 is fitted to the inner rolling surface 71a and the shaft portion 77. Here, the fitting portion 77b is left as it is after forging.
[0014] ハブ輪 62と複列の転がり軸受 63および等速自在継手 64の組立は、まず、外方部 材 65の複列の外側転走面 65a、 65aにそれぞれ保持器 80を介してボール 67が仮 組みされる。次に、ハブ輪 62の小径段部 62bの端面に外側継手部材 71の肩部 76 が衝合され、突合せ状態になるまでハブ輪 62に軸部 77が内嵌される。さらに、この 軸部 77における嵌合部 77bの内径にマンドレル等の拡径治具を押し込んで嵌合部 77bを拡径し、この嵌合部 77bをノヽブ輪 62の凹凸部 70に食い込ませて加締め、ノヽ ブ輪 62と外側継手部材 71とを一体に塑性結合させることによって行われる。こうした 第 4世代構造により軽量 'コンパクトィ匕が図れると共に、緩みのない結合部を備えた 車輪用軸受装置を得ることができる (例えば、特許文献 2参照。 )0 特許文献 1：特開平 11 151904号公報 [0014] Assembling the hub wheel 62, the double row rolling bearing 63, and the constant velocity universal joint 64, first, the balls are respectively placed on the double row outer rolling surfaces 65a and 65a of the outer member 65 via the cage 80. 67 is temporarily assembled. Next, the shoulder portion 76 of the outer joint member 71 is abutted against the end face of the small-diameter stepped portion 62b of the hub wheel 62, and the shaft portion 77 is fitted into the hub wheel 62 until it comes into a butted state. Further, a diameter expanding jig such as a mandrel is pushed into the inner diameter of the fitting portion 77b in the shaft portion 77 to increase the diameter of the fitting portion 77b. It is performed by caulking and plastically coupling the nose ring 62 and the outer joint member 71 together. These together with the fourth-generation structure by attained lightweight 'compact I spoon, it is possible to obtain a wheel bearing apparatus provided with a slack-free coupling portion (e.g., see Patent Document 2.) 0 Patent Document 1: Japanese Patent Laid-Open No. 11 151904
特許文献 2：特開 2004 - 76872号公報  Patent Document 2: Japanese Patent Laid-Open No. 2004-76872
発明の開示  Disclosure of the invention
発明が解決しょうとする課題  Problems to be solved by the invention
[0015] 然しながら、近年、車両の燃費向上とばね下重量軽量ィ匕による運動性能向上のた め、さらなる軽量ィ匕が求められている。また、大きなモーメント荷重等が負荷されても 充分な強度 ·耐久性を発揮すると共に、安定した走行のために軸受剛性を高めること が望まれる。こうした従来の車輪用軸受装置において、車両の燃費向上やばね下重 量軽量ィ匕による運動性能の向上のために軽量 'コンパクトィ匕を図りつつ、さらに耐久 性と共に軸受剛性を高めることが望まれて 、る。  [0015] However, in recent years, further light weight has been demanded in order to improve vehicle fuel efficiency and to improve exercise performance by unsprung weight and light weight. In addition, it is desirable to exhibit sufficient strength and durability even when a large moment load or the like is applied, and to increase bearing rigidity for stable running. In such a conventional wheel bearing device, it is desired to increase the bearing rigidity as well as the durability while reducing the weight and compactness in order to improve the fuel efficiency of the vehicle and the movement performance by the unsprung weight and light weight. And
[0016] 本発明は、このような事情に鑑みてなされたもので、軽量'コンパクト化と共に、高剛 性化と耐久性の向上を図った第 4世代構造の車輪用軸受装置を提供することを目的 としている。  [0016] The present invention has been made in view of such circumstances, and provides a wheel bearing device having a fourth generation structure that is light-weighted, compact, highly rigid, and improved in durability. It is an object.
課題を解決するための手段  Means for solving the problem
[0017] 係る目的を達成すベぐ本発明のうち請求項 1記載の発明は、ハブ輪と複列の転が り軸受と等速自在継手とがユニット化された車輪用軸受装置であって、前記複列の 転がり軸受が、内周に複列の外側転走面が形成され、外周に車体取付フランジと、こ の車体取付フランジのインナー側に相手部材との嵌合に供される基準面が形成され た外方部材と、一端部に車輪取付フランジを一体に有し、外周に前記複列の外側転 走面に対向する一方の内側転走面と、この内側転走面から軸方向に延びる円筒状 の小径段部が形成されたハブ輪、およびこのハブ輪に内嵌され、外周に前記複列の 外側転走面に対向する他方の内側転走面と、この内側転走面から軸方向に延びる 軸部が一体に形成された前記等速自在継手の外側継手部材力 なる内方部材と、 この内方部材と前記外方部材の両転走面間に転動自在に収容された複列のボール 群とを備え、前記軸部の端部を塑性変形させて前記ハブ輪に加締ることにより前記 ハブ輪と外側継手部材とが一体に塑性結合された車輪用軸受装置にぉ 、て、前記 複列のボール群のうちインナー側のボール群のピッチ円直径がアウター側のボール 群のピッチ円直径よりも大径に設定されると共に、インナー側のボール群のボールの 個数がアウター側のボール群のボールの個数よりも多く設定されている構成を採用し た。 [0017] Of the present invention that achieves such an object, the invention described in claim 1 is a wheel bearing device in which a hub wheel, a double row rolling bearing, and a constant velocity universal joint are unitized. The double-row rolling bearing has a double-row outer raceway formed on the inner periphery, a reference provided for fitting a body mounting flange on the outer periphery and a mating member on the inner side of the body mounting flange. An outer member formed with a surface, a wheel mounting flange at one end integrally, one inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a shaft from the inner rolling surface A hub ring formed with a cylindrical small-diameter step portion extending in the direction, the other inner rolling surface that is fitted in the hub ring and faces the outer rolling surface of the double row on the outer periphery, and the inner rolling surface An inner member that is an outer joint member force of the constant velocity universal joint integrally formed with a shaft portion extending in an axial direction from the surface; The inner member and a double row ball group accommodated in a freely rolling manner between both rolling surfaces of the outer member, and the end of the shaft portion is plastically deformed and crimped to the hub wheel. Thus, in the wheel bearing device in which the hub wheel and the outer joint member are integrally plastically coupled, the pitch circle diameter of the inner side ball group of the double row ball group is equal to that of the outer side ball group. It is set to a diameter larger than the pitch circle diameter and A configuration was adopted in which the number of balls was set larger than the number of balls in the outer ball group.
[0018] このように、ハブ輪と等速自在継手を構成する外側継手部材とが塑性結合によりュ ニット化された第 4世代構造の車輪用軸受装置において、複列のボール群のうちイン ナー側のボール群のピッチ円直径がアウター側のボール群のピッチ円直径よりも大 径に設定されることで、軸方向寸法の増大なしに、軸受スパン（両転走面に加わる力 の作用方向の作用線と軸心との交点の間隔）の増大を図ることができる。カロえて、ィ ンナー側のボール群のボールの個数がアウター側のボール群のボールの個数よりも 多く設定されるので、軽量 'コンパクトィ匕を図ることができると共に、軸受剛性の増大 が図れる。また、インナー側のボール群のボールの個数が多くなることで、軸受の負 荷容量が増大し、軸受の長寿命化を図ることができる。したがって、高剛性化と耐久 性の向上を図った第 4世代構造の車輪用軸受装置を提供することができる。  [0018] As described above, in the fourth-generation wheel bearing device in which the hub wheel and the outer joint member constituting the constant velocity universal joint are unitized by plastic coupling, the inner of the double row ball group. By setting the pitch circle diameter of the ball group on the side larger than the pitch circle diameter of the ball group on the outer side, the bearing span (the direction of action of the force applied to both rolling surfaces without increasing the axial dimension) (Interval of the intersection between the line of action and the axis) can be increased. Since the number of balls in the inner side ball group is set to be larger than the number of balls in the outer side ball group, light weight and compactness can be achieved and the bearing rigidity can be increased. Further, since the number of balls in the inner ball group is increased, the load capacity of the bearing is increased and the life of the bearing can be extended. Therefore, it is possible to provide a wheel bearing device having a fourth generation structure that achieves higher rigidity and improved durability.
[0019] 好ましくは、請求項 2に記載の発明のように、前記ハブ輪の内径に硬化した凹凸部 が形成され、前記軸部に形成された中空状の嵌合部を拡径させて当該凹凸部に食 Vヽ込ませることにより、前記ハブ輪と外側継手部材とが一体に塑性結合されて ヽれば 、ナット等で強固に緊締して予圧量を管理する必要がなぐ軽量 'コンパクトィ匕を図る ことができると共に、ハブ輪の強度 ·耐久性を向上させ、かつ長期間その予圧量を維 持することができる。  [0019] Preferably, as in the invention described in claim 2, a hardened concave and convex portion is formed on the inner diameter of the hub wheel, and the hollow fitting portion formed in the shaft portion is expanded in diameter. If the hub wheel and the outer joint member are integrally plastically joined by grooving the uneven part, it is not necessary to tighten the nut tightly and manage the preload amount. It is possible to improve the strength and durability of the hub wheel and maintain the preload for a long time.
[0020] また、請求項 3に記載の発明は、前記複列のボールが同じサイズであれば、組立ェ 程における誤組みの問題を解消でき、製造コストが低減できると共に、品質の信頼性 が向上する。  [0020] Further, in the invention according to claim 3, if the double row balls have the same size, the problem of misassembly in the assembly process can be solved, the manufacturing cost can be reduced, and the reliability of the quality can be improved. improves.
[0021] また、請求項 4に記載の発明のように、請求項 1乃至 3いずれかの車輪用軸受装置 を備え、前記アウトボード側の等速自在継手に一端が連結されたドライブシャフトと、 このドライブシャフトの他端に連結されたインボード側の摺動型の等速自在継手とか らなるアクスルモジュールであれば、ばね下重量の軽量化を図ると共に、車両への分 解 ·組立が簡便化できる。  [0021] Further, as in the invention according to claim 4, a drive shaft comprising the wheel bearing device according to any one of claims 1 to 3 and having one end connected to the constant velocity universal joint on the outboard side, An axle module consisting of an inboard sliding type constant velocity universal joint connected to the other end of this drive shaft will reduce the unsprung weight while simplifying disassembly and assembly into the vehicle. Can be
[0022] また、請求項 5に記載の発明のように、前記外方部材の基準面の外径が前記等速 自在継手の最大外径よりも大径に設定されて ヽれば、懸架装置を構成するナックル に対してアクスルモジュールを容易に嵌挿でき、ブーツ等がナックルに干渉して傷付 くことなく組み立てることができる。 [0022] Further, as in the invention described in claim 5, if the outer diameter of the reference surface of the outer member is set to be larger than the maximum outer diameter of the constant velocity universal joint, the suspension device Make up knuckle The axle module can be easily inserted into the boot, and the boot can be assembled without interfering with the knuckle.
発明の効果  The invention's effect
[0023] 本発明に係る車輪用軸受装置は、ハブ輪と複列の転がり軸受と等速自在継手とが ユニット化された車輪用軸受装置であって、前記複列の転がり軸受が、内周に複列 の外側転走面が形成され、外周に車体取付フランジと、この車体取付フランジのイン ナー側に相手部材との嵌合に供される基準面が形成された外方部材と、一端部に車 輪取付フランジを一体に有し、外周に前記複列の外側転走面に対向する一方の内 側転走面と、この内側転走面から軸方向に延びる円筒状の小径段部が形成された ハブ輪、およびこのハブ輪に内嵌され、外周に前記複列の外側転走面に対向する 他方の内側転走面と、この内側転走面から軸方向に延びる軸部が一体に形成され た前記等速自在継手の外側継手部材力 なる内方部材と、この内方部材と前記外 方部材の両転走面間に転動自在に収容された複列のボール群とを備え、前記軸部 の端部を塑性変形させて前記ハブ輪に加締ることにより前記ハブ輪と外側継手部材 とが一体に塑性結合された車輪用軸受装置において、複列のボール群のうちインナ 一側のボール群のピッチ円直径がアウター側のボール群のピッチ円直径よりも大径 に設定されることで、軸方向寸法の増大なしに、軸受スパン（両転走面に加わる力の 作用方向の作用線と軸心との交点の間隔）の増大を図ることができる。カロえて、イン ナー側のボール群のボールの個数がアウター側のボール群のボールの個数よりも多 く設定されるので、軽量 'コンパクトィ匕を図ることができると共に、軸受剛性の増大が 図れる。また、インナー側のボール群のボールの個数が多くなることで、軸受の負荷 容量が増大し、軸受の長寿命化を図ることができる。したがって、高剛性化と耐久性 の向上を図った第 4世代構造の車輪用軸受装置を提供することができる。  [0023] A wheel bearing device according to the present invention is a wheel bearing device in which a hub ring, a double row rolling bearing, and a constant velocity universal joint are unitized, and the double row rolling bearing has an inner circumference. An outer member having a double-row outer raceway formed on the outer periphery, a vehicle body mounting flange on the outer periphery, and an outer member having a reference surface for mating with a mating member on the inner side of the vehicle body mounting flange. The wheel mounting flange is integrally formed on the outer periphery, one inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a cylindrical small-diameter stepped portion extending in the axial direction from the inner rolling surface. Formed on the hub ring, the other inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a shaft portion extending in the axial direction from the inner rolling surface. An inner member which is an outer joint member force of the constant velocity universal joint formed integrally, and the inner member and the outer member A double row ball group accommodated in a freely rolling manner between both rolling surfaces of the member, and plastically deforming an end portion of the shaft portion and crimping the hub wheel to the hub wheel, and the outer joint. In the wheel bearing device in which the members are integrally plastically coupled, the pitch circle diameter of the inner side ball group in the double row ball group is set larger than the pitch circle diameter of the outer side ball group. As a result, it is possible to increase the bearing span (interval between the line of action in the direction of action of the force applied to both rolling surfaces and the axis) without increasing the axial dimension. Since the number of balls in the inner side ball group is set to be larger than the number of balls in the outer side ball group, it is possible to achieve a light-weight 'compact' and increase bearing rigidity. . Further, since the number of balls in the inner ball group is increased, the load capacity of the bearing is increased and the life of the bearing can be extended. Therefore, it is possible to provide a fourth-generation wheel bearing device that achieves high rigidity and improved durability.
発明を実施するための最良の形態  BEST MODE FOR CARRYING OUT THE INVENTION
[0024] ハブ輪と複列の転がり軸受と等速自在継手とがユニット化された車輪用軸受装置で あって、前記複列の転がり軸受が、内周に複列の外側転走面が形成され、外周に車 体取付フランジと、この車体取付フランジのインナー側に相手部材との嵌合に供され る基準面が形成された外方部材と、一端部に車輪取付フランジを一体に有し、外周 に前記複列の外側転走面に対向する一方の内側転走面と、この内側転走面から軸 方向に延びる円筒状の小径段部が形成されたハブ輪、およびこのハブ輪に内嵌さ れ、外周に前記複列の外側転走面に対向する他方の内側転走面と、この内側転走 面から軸方向に延びる円筒状の軸部が一体に形成された前記等速自在継手の外側 継手部材力 なる内方部材と、この内方部材と前記外方部材の両転走面間に転動 自在に収容された複列のボール群とを備え、前記ハブ輪の内径に硬化した凹凸部 が形成され、前記軸部に形成された嵌合部を拡径させて当該凹凸部に食い込ませ ることにより、前記ハブ輪と外側継手部材とが一体に塑性結合された車輪用軸受装 置において、前記複列のボール群のうちインナー側のボール群のピッチ円直径がァ ウタ一側のボール群のピッチ円直径よりも大径に設定されると共に、前記複列のボー ル群のボールが同じサイズで、かつインナー側のボール群のボールの個数がァウタ 一側のボール群のボールの個数よりも多く設定されている。 [0024] A wheel bearing device in which a hub wheel, a double row rolling bearing, and a constant velocity universal joint are unitized, and the double row rolling bearing has a double row outer rolling surface formed on an inner periphery thereof. It has a vehicle body mounting flange on the outer periphery, an outer member formed with a reference surface for fitting with a mating member on the inner side of the vehicle body mounting flange, and a wheel mounting flange on one end. , Outer circumference And a hub ring formed with one inner rolling surface facing the outer rolling surface of the double row, a cylindrical small-diameter step portion extending in the axial direction from the inner rolling surface, and an internal fit in the hub ring. The constant velocity universal joint is integrally formed on the outer periphery with the other inner rolling surface facing the outer rolling surface of the double row and a cylindrical shaft portion extending in the axial direction from the inner rolling surface. The inner member of the outer joint member and a double row ball group that is slidably accommodated between the rolling surfaces of the inner member and the outer member, and is hardened on the inner diameter of the hub wheel. A wheel bearing in which the hub wheel and the outer joint member are integrally plastically bonded by expanding the diameter of the fitting portion formed in the shaft portion and causing the fitting portion formed in the shaft portion to bite into the uneven portion. In the apparatus, the pitch circle diameter of the inner-side ball group of the double-row ball group has an outer one side. It is set to be larger than the pitch circle diameter of the ball group, the balls of the double row ball group are the same size, and the number of balls of the inner side ball group is the same as the number of balls of the ball side of the outer side. It is set more than the number.
実施例  Example
[0025] 以下、本発明の実施の形態を図面に基づいて詳細に説明する。  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
図 1は、本発明に係る車輪用軸受装置の一実施形態を示す縦断面図、図 2は、図 1の車輪用軸受装置が適用されたアクスルモジュールを示す縦断面図である。なお、 以下の説明では、車両に組み付けた状態で車両の外側寄りとなる側をアウター側（ 図面左側）、中央寄り側をインナー側（図面右側） t 、う。  FIG. 1 is a longitudinal sectional view showing an embodiment of a wheel bearing device according to the present invention, and FIG. 2 is a longitudinal sectional view showing an axle module to which the wheel bearing device of FIG. 1 is applied. In the following description, the side closer to the outer side of the vehicle when assembled to the vehicle is the outer side (left side in the drawing), and the side closer to the center is the inner side (right side in the drawing) t.
[0026] この車輪用軸受装置は、ハブ輪 1と複列の転がり軸受 2および等速自在継手 3とが ユニットィ匕して構成されている。複列の転がり軸受 2は、外方部材 4と内方部材 5と複 列のボール 6a、 6bとを備えている。内方部材 5は、ハブ輪 1と、このハブ輪 1に内嵌さ れた後述する外側継手部材 14とからなる。  [0026] The wheel bearing device includes a hub wheel 1, a double row rolling bearing 2 and a constant velocity universal joint 3 which are unitized. The double row rolling bearing 2 includes an outer member 4, an inner member 5, and double rows of balls 6a and 6b. The inner member 5 includes a hub wheel 1 and an outer joint member 14 which is fitted into the hub wheel 1 and will be described later.
[0027] 外方部材 4は、 S53C等の炭素 0. 40-0. 80wt%を含む中炭素鋼からなり、外周 に車体（図示せず）に取り付けるための車体取付フランジ 4cを一体に有し、内周に円 弧状の複列の外側転走面 4a、 4bが形成されている。この複列の外側転走面 4a、 4b は、高周波焼入れによって表面硬さを 58〜64HRCの範囲に硬化処理されている。  [0027] The outer member 4 is made of medium carbon steel containing 0.40-0.80 wt% of carbon such as S53C, and has a vehicle body mounting flange 4c integrally attached to the vehicle body (not shown) on the outer periphery. The outer circumferential rolling surfaces 4a and 4b are formed in an arc shape on the inner circumference. The double row outer rolling surfaces 4a and 4b are hardened to a surface hardness of 58 to 64HRC by induction hardening.
[0028] 一方、ハブ輪 1は S53C等の炭素 0. 40〜0. 80wt%を含む中炭素鋼からなり、ァ ウタ一側の端部に車輪を取り付けるための車輪取付フランジ 7を有し、この車輪取付 フランジ 7の周方向等配に複数のハブボルト 8が植設されている。また、ハブ輪 1の外 周には、前記複列の外側転走面 4a、 4bに対向する一方 (アウター側）の円弧状の内 側転走面 laと、この内側転走面 laから軸方向に延びる円筒状の小径段部 lbが形成 されている。そして、アウター側のシール 10が摺接するシールランド部 7aから内側転 走面 laおよび小径段部 lbに亙って高周波焼入れによって表面硬さを 58〜64HRC の範囲に硬化処理されている。これにより、車輪取付フランジ 7の基部となるシールラ ンド部 7aの耐摩耗性が向上するば力りでなぐ車輪取付フランジ 7に負荷される回転 曲げ荷重に対して充分な機械的強度を有し、ハブ輪 1の耐久性が向上する。 [0028] On the other hand, the hub wheel 1 is made of medium carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and has a wheel mounting flange 7 for mounting a wheel to an end on one side of the outer wheel. This wheel mounting A plurality of hub bolts 8 are planted at equal intervals in the circumferential direction of the flange 7. Further, on the outer periphery of the hub wheel 1, one (outer side) arcuate inner rolling surface la facing the double row outer rolling surfaces 4a and 4b, and an axis from the inner rolling surface la A cylindrical small diameter step lb extending in the direction is formed. Then, the surface hardness is hardened to a range of 58 to 64 HRC by induction hardening from the seal land portion 7a with which the outer seal 10 is in sliding contact to the inner rolling surface la and the small diameter step portion lb. This provides sufficient mechanical strength against the rotational bending load applied to the wheel mounting flange 7 by force, which improves the wear resistance of the seal land portion 7a that is the base of the wheel mounting flange 7. The durability of the hub wheel 1 is improved.
[0029] ハブ輪 1の内周には凹凸部 12が形成され、熱処理によって表面硬さを 54〜64HR Cの範囲に表面が硬化処理されている。熱処理としては、局部加熱ができ、硬化層 深さの設定が比較的容易にできる高周波誘導加熱による焼入れが好適である。なお 、凹凸部 12はアヤメローレット状に形成され、旋削等により独立して形成された複数 の環状溝と、ブローチ加工等により形成された複数の軸方向溝とを略直交させて構 成した交叉溝、あるいは、互いに傾斜した螺旋溝で構成した交叉溝力もなる。また、 凹凸部 12の凸部は良好な食い込み性を確保するために、その先端部が三角形状等 の尖塔形状に形成されて ヽる。  [0029] An uneven portion 12 is formed on the inner periphery of the hub wheel 1, and the surface is hardened by heat treatment so that the surface hardness is in the range of 54 to 64HRC. As the heat treatment, local heating and quenching by high-frequency induction heating that can set the hardened layer depth relatively easily are suitable. The concave and convex portion 12 is formed in the shape of an iris knurl, and is a cross formed by a plurality of annular grooves formed independently by turning or the like and a plurality of axial grooves formed by broaching or the like substantially orthogonal to each other. There is also a cross groove force constituted by grooves or spiral grooves inclined with respect to each other. In addition, the convex portion of the concave-convex portion 12 has a tip portion formed in a spire shape such as a triangle shape in order to ensure good biting property.
[0030] 等速自在継手 3は、外側継手部材 14と継手内輪 15、ケージ 16、およびトルク伝達 ボール 17と力らなる。外側継手部材 14は S53C等の炭素 0. 40-0. 80wt%を含む 中炭素鋼からなり、カップ状のマウス部 18と、このマウス部 18の底部をなす肩部 19と 、この肩部 19から軸方向に延びる円筒状の軸部 20とが一体に形成されている。この 軸部 20には、ハブ輪 1の小径段部 lbに所定の径方向すきまを介して円筒嵌合する インロウ部 20aと、このインロウ部 20aの端部に嵌合部 20bがそれぞれ形成されてい る。  The constant velocity universal joint 3 includes an outer joint member 14, a joint inner ring 15, a cage 16, and a torque transmission ball 17. The outer joint member 14 is made of medium carbon steel containing carbon 0.40-0.80 wt% such as S53C, and has a cup-shaped mouth portion 18, a shoulder portion 19 that forms the bottom portion of the mouth portion 18, and the shoulder portion 19. A cylindrical shaft portion 20 extending in the axial direction from is integrally formed. The shaft portion 20 is formed with an in-row portion 20a that is cylindrically fitted to the small-diameter step portion lb of the hub wheel 1 through a predetermined radial clearance, and a fitting portion 20b is formed at the end of the in-row portion 20a. The
[0031] また、マウス部 18の内周には曲線部を有する軸方向に延びるトラック溝 18aが形成 されると共に、継手内輪 15の外周にこのトラック溝 18aに対応するトラック溝 15aが形 成されている。そして、これら両トラック溝 18a、 15a間にケージ 16を介してトルク伝達 ボール 17が収容されている。また、肩部 19の外周には、前記複列の外側転走面 4a 、 4bに対向する他方 (インナー側）の円弧状の内側転走面 14aが形成されている。そ して、トラック溝 18aと、インナー側のシール 11が嵌合する外周面から内側転走面 14 aおよび軸部 20に亙って高周波焼入れによって表面硬さを 58〜64HRCの範囲に 硬化処理されている。ここで、軸部 20のうち嵌合部 20bは鍛造後の生のままとされて いる。 In addition, an axially extending track groove 18 a having a curved portion is formed on the inner periphery of the mouth portion 18, and a track groove 15 a corresponding to the track groove 18 a is formed on the outer periphery of the joint inner ring 15. ing. A torque transmission ball 17 is accommodated between the track grooves 18a and 15a via a cage 16. Further, on the outer periphery of the shoulder portion 19, the other (inner side) arcuate inner rolling surface 14 a facing the double row outer rolling surfaces 4 a, 4 b is formed. So Then, the surface hardness is hardened within the range of 58 to 64HRC by induction hardening from the outer peripheral surface where the track groove 18a and the inner seal 11 are fitted to the inner rolling surface 14a and the shaft portion 20. ing. Here, the fitting portion 20b of the shaft portion 20 is left as it is after forging.
[0032] 外方部材 4の複列の外側転走面 4a、 4bと、これらに対向する複列の内側転走面 la 、 14a間には複列のボール 6a、 6bが収容され、保持器 9a、 9bによって転動自在に 保持されている。また、外方部材 4の端部にはシール 10、 11が装着され、軸受内部 に封入された潤滑グリースの漏洩と、外部力 軸受内部に雨水やダスト等が侵入する のを防止している。これらの複列の転がり軸受 2は、両転走面 4a、 laおよび 4b、 14a に加わる力の作用方向の作用線が軸心に向うほど軸方向に離反する、所謂背面合 せタイプの複列アンギユラ玉軸受を構成して 、る。  [0032] Double row balls 6a and 6b are accommodated between double row outer raceway surfaces 4a and 4b of outer member 4 and double row inner raceway surfaces la and 14a opposite to each other, and retainer It is held by 9a and 9b so that it can roll freely. In addition, seals 10 and 11 are attached to the end of the outer member 4 to prevent leakage of lubricating grease sealed inside the bearing and intrusion of rainwater and dust into the external force bearing. These double-row rolling bearings 2 are so-called back-fitting type double-rows in which the acting lines of the force applied to the rolling surfaces 4a, la and 4b, 14a are separated in the axial direction toward the axial center. Constructs an anguilla ball bearing.
[0033] 次に、ハブ輪 1と複列の転がり軸受 2および等速自在継手 3のユニットィ匕の方法に ついて詳細に説明する。  [0033] Next, a method of uniting the hub wheel 1, the double row rolling bearing 2 and the constant velocity universal joint 3 will be described in detail.
まず、外方部材 4の複列の外側転走面 4a、 4bに保持器 9a、 9bを介して複列の転 動体 6a、 6bが仮組みされると共に、外方部材 4の両端部にシール 10、 11が装着さ れる。次に、外方部材 4の両側力もハブ輪 1と外側継手部材 14が内挿され、ハブ輪 1 の小径段部 lbの端面に外側継手部材 14の肩部 19が衝合され、突合せ状態になる までノヽブ輪 1に外側継手部材 14の軸部 20が内嵌される。そして、この軸部 20におけ る嵌合部 20bの内径にマンドレル等の拡径治具を押し込んで嵌合部 20bを拡径し、 この嵌合部 20bをノヽブ輪 1の凹凸部 12に食 、込ませて加締め、ハブ輪 1と外側継手 部材 14とが一体に塑性結合されて完了する。これにより、従来のようにナット等で強 固に緊締して予圧量を管理する必要がないため、軽量 'コンパクトィ匕を図ることができ ると共に、ハブ輪 1の強度 ·耐久性を向上させ、かつ長期間その予圧量を維持するこ とができる。なお、ハブ輪 1の開口端部と中空の軸部 20にはエンドキャップ 13a、 13b が装着され、塑性結合部に雨水等が浸入してその部位が発鲭するのを防止すると共 に、マウス部 18内に封入されたグリースが外部に漏洩するのを防止している。  First, the double row rolling elements 6a and 6b are temporarily assembled on the double row outer rolling surfaces 4a and 4b of the outer member 4 via the cages 9a and 9b, and seals are provided at both ends of the outer member 4. 10 and 11 are installed. Next, the hub wheel 1 and the outer joint member 14 are also inserted in both side forces of the outer member 4, and the shoulder 19 of the outer joint member 14 is abutted against the end surface of the small-diameter stepped portion lb of the hub wheel 1 so that the butt state is achieved. Until that, the shaft portion 20 of the outer joint member 14 is fitted inside the nove ring 1. Then, a diameter expansion jig such as a mandrel is pushed into the inner diameter of the fitting portion 20b in the shaft portion 20 to expand the diameter of the fitting portion 20b, and the fitting portion 20b is formed on the concave and convex portion 12 of the nozzle ring 1. The hub wheel 1 and the outer joint member 14 are integrally plastically joined to complete the process. This eliminates the need to control the preload by tightening with a nut or the like as in the past, so that it is possible to achieve a lightweight 'compact' and improve the strength and durability of the hub wheel 1. In addition, the preload amount can be maintained for a long time. End caps 13a and 13b are attached to the open end of the hub wheel 1 and the hollow shaft 20 to prevent rainwater and the like from entering the plastic coupling portion and causing the portion to erupt. The grease enclosed in the part 18 is prevented from leaking to the outside.
[0034] なお、ハブ輪 1と外側継手部材 14とを塑性結合する手段として例示した構成以外 にも、例えば、図示はしないが、ハブ輪に外側継手部材の軸部をセレーシヨンを介し てトルク伝達可能に嵌合すると共に、この軸部の端部を径方向外方に塑性変形させ て加締部を形成し、この加締部で両部材を軸方向に固定する、所謂揺動加締方式を 採用しても良い。 [0034] In addition to the configuration exemplified as means for plastically coupling the hub wheel 1 and the outer joint member 14, for example, although not shown, the shaft portion of the outer joint member is connected to the hub wheel via a selection. So that torque can be transmitted, and the end of the shaft is plastically deformed radially outward to form a crimped portion, and both members are fixed in the axial direction by the crimped portion. A caulking method may be adopted.
[0035] ここで、本実施形態では、インナー側のボール 6bのピッチ円直径 PCDiがアウター 側のボール 6aのピッチ円直径 PCDoよりも大径に設定されている。これら複列のボー ル 6a、 6bの外径は同じである力 このピッチ円直径 PCDo、 PCDiの違いにより、イン ナー側のボール 6bの個数がアウター側のボール 6aの個数よりも多く設定されている 。本実施形態の場合、複列のボール 6a、 6bの外径を同じにすることにより、組立工程 における誤組みの問題を解消することができ、製造コストが低減できると共に、品質 の信頼性が向上する。  Here, in the present embodiment, the pitch circle diameter PCDi of the inner-side ball 6b is set larger than the pitch circle diameter PCDo of the outer-side ball 6a. The outer diameter of these double-row balls 6a and 6b is the same force. Because of the difference in pitch circle diameter PCDo and PCDi, the number of inner-side balls 6b is set larger than the number of outer-side balls 6a. Yes. In the case of this embodiment, by making the outer diameters of the double-row balls 6a and 6b the same, it is possible to eliminate the problem of misassembly in the assembly process, reduce the manufacturing cost, and improve the reliability of quality. To do.
[0036] このように、左右のボール 6a、 6bのピッチ円直径 PCDo、 PCDiの違いに伴い、内 方部材 5において、外側継手部材 14の内側転走面 14aの溝底径はハブ輪 1の内側 転走面 laの溝底径よりも拡径して形成されている。一方、外方部材 4において、左右 のボール 6a、 6bのピッチ円直径 PCDo、 PCDiの違いに伴い、インナー側の外側転 走面 4bの溝底径がアウター側の外側転走面 4aの溝底径よりも拡径して形成されて いる。  [0036] Thus, the groove bottom diameter of the inner rolling surface 14a of the outer joint member 14 in the inner member 5 is the same as that of the hub wheel 1 due to the difference in pitch circle diameters PCDo and PCDi of the left and right balls 6a and 6b. The inner rolling surface is formed with a diameter larger than the groove bottom diameter of la. On the other hand, in the outer member 4, due to the difference in pitch circle diameters PCDo and PCDi of the left and right balls 6a and 6b, the groove bottom diameter of the outer rolling surface 4b on the inner side is the groove bottom of the outer rolling surface 4a on the outer side. The diameter is larger than the diameter.
[0037] こうした構成の車輪用軸受装置では、インナー側の内側転走面 14aを外側継手部 材 14の肩部 19の外周に直接形成するようにしたので、インナー側のボール 6bのピッ チ円直径 PCDiをアウター側のボール 6aのピッチ円直径 PCDoよりも大径に設定す ることができると共に、ボール 6bの個数もインナー側の個数をアウター側よりも多く設 定することができるため、軽量 'コンパクトィ匕を図ることができると共に、軸受剛性の増 大と軸受の長寿命化を図ることができる。  [0037] In the wheel bearing device having such a configuration, the inner-side inner rolling surface 14a is formed directly on the outer periphery of the shoulder portion 19 of the outer joint member 14, so that the pitch circle of the inner-side ball 6b is formed. The diameter PCDi can be set larger than the pitch circle diameter PCDo of the outer ball 6a, and the number of balls 6b can be set more on the inner side than on the outer side. 'Compactness can be achieved, bearing rigidity can be increased and bearing life can be extended.
[0038] 図 2は前述した車輪用軸受装置を適用したアクスルモジュールを示す縦断面図で ある。このアクスルモジュールは、一対の等速自在継手 3、 21と、これら等速自在継 手 3、 21に連結されたドライブシャフト 22とを備えている。このドライブシャフト 22の一 端は、アウトボード側の等速自在継手 3の継手内輪 15にセレーシヨンを介して内嵌さ れ、他端はディファレンシャル（図示せず）に固定されるインボード側の摺動型の等速 自在継手 21に連結されて!、る。 [0039] このインボード側の等速自在継手 21は、外側継手部材 23と、外周部に 3本の脚軸 24aが等配に突設されたトリポード部材 24と、これらの脚軸 24aに針状ころ 25を介し て回転自在に外挿されたローラ 26とを備えている。外側継手部材 23は、 S53C等の 炭素 0. 40〜0. 80wt%を含む中炭素鋼で形成された円筒状の外筒部 27と、この外 筒部 27の底部力も軸方向に延びる軸部 28を一体に有して 、る。軸部 28の外周には ディファレンシャルに固定するためのセレーシヨン（またはスプライン） 28aが形成され ている。 FIG. 2 is a longitudinal sectional view showing an axle module to which the wheel bearing device described above is applied. The axle module includes a pair of constant velocity universal joints 3 and 21 and a drive shaft 22 connected to the constant velocity universal joints 3 and 21. One end of the drive shaft 22 is fitted into the joint inner ring 15 of the constant velocity universal joint 3 on the outboard side via a selection, and the other end is slid on the inboard side fixed to a differential (not shown). Connected to a dynamic constant velocity universal joint 21! [0039] This constant velocity universal joint 21 on the inboard side includes an outer joint member 23, a tripod member 24 having three leg shafts 24a projecting from the outer periphery at equal intervals, and needles on these leg shafts 24a. And a roller 26 that is rotatably inserted through a roller 25. The outer joint member 23 includes a cylindrical outer tube portion 27 formed of medium carbon steel containing carbon 0.40 to 0.80 wt% such as S53C, and a shaft portion in which the bottom portion force of the outer tube portion 27 extends in the axial direction. It has 28 as one. A selection (or spline) 28a for fixing to the differential is formed on the outer periphery of the shaft portion 28.
[0040] 外筒部 27の内周には軸方向に延びる直線状の 3本のトラック溝 27aが形成され、こ のトラック溝 27a上をローラ 26が転動する。外側継手部材 23において、トラック溝 27a の表面に高周波焼入れ等によって所定の硬化層が形成されている。また、外筒部 27 の開口側の外周には合成ゴム等力もなるブーツ 29が装着され、外筒部 27内に封入 されたグリースの漏洩と、外部から雨水やダスト等が継手内に侵入するのを防止して いる。  [0040] Three linear track grooves 27a extending in the axial direction are formed on the inner periphery of the outer cylindrical portion 27, and the roller 26 rolls on the track grooves 27a. In the outer joint member 23, a predetermined hardened layer is formed on the surface of the track groove 27a by induction hardening or the like. In addition, a boot 29 having a synthetic rubber equivalent force is attached to the outer periphery of the outer cylinder part 27 on the opening side, and leakage of grease sealed in the outer cylinder part 27 and rainwater and dust enter the joint from the outside. This is preventing.
[0041] なお、外筒部 27は円筒状に限らず、例えば、外周がトラック溝 27aに対応した花形 形状に形成されたものであっても良ぐまた、軸部 28に限らず、ディファレンシャルに 固定するための取付フランジが一体に形成されている構造であっても良い。また、こ こでは、インボード側の等速自在継手 21にトリボード型を例示した力 これに限らず、 摺動型の等速自在継手なら良ぐ他の構造のトリボード型をはじめ、例えば、ボール を使用したダブルオフセット型の等速自在継手 (DOJ)であっても良 、。  [0041] The outer cylindrical portion 27 is not limited to a cylindrical shape, and for example, the outer periphery may be formed in a flower shape corresponding to the track groove 27a. Also, the outer cylindrical portion 27 is not limited to the shaft portion 28 and is differentially formed. A structure in which a mounting flange for fixing is integrally formed may be used. In addition, the force illustrated here as a triboard type for the constant velocity universal joint 21 on the inboard side is not limited to this, but a sliding type constant velocity universal joint may be used, for example, a triboard type having a different structure, such as a ball Double offset type constant velocity universal joints (DOJ) using
[0042] ここで、本実施形態では、ナックルとの嵌合部となる外方部材 4の基準面 4dの外径 Daが、等速自在継手 3、 21の最大外径 Db、 Dc (ここでは、ブーツ 30、 29の最大外 径)よりも大径に形成されている（Da >Db≥Dc)。これにより、ばね下重量の軽量ィ匕 を図り、車両への分解 '組立が簡便化できるだけでなぐナックルに対してアクスルモ ジュールを容易に嵌挿でき、ブーツ 30、 29がナックルに干渉して傷付くことなく組み 立てることができる。  [0042] Here, in the present embodiment, the outer diameter Da of the reference surface 4d of the outer member 4 serving as a fitting portion with the knuckle is the maximum outer diameter Db, Dc of the constant velocity universal joints 3 and 21 (here The maximum outer diameter of the boots 30 and 29 is larger (Da> Db≥Dc). As a result, the unsprung weight can be reduced and the axle module can be easily inserted into the knuckle that can be easily disassembled into the vehicle, and the boots 30 and 29 can be damaged by interference with the knuckle. It can be assembled without any problems.
[0043] 以上、本発明の実施の形態について説明を行ったが、本発明はこうした実施の形 態に何等限定されるものではなぐあくまで例示であって、本発明の要旨を逸脱しな い範囲内において、さらに種々なる形態で実施し得ることは勿論のことであり、本発 明の範囲は、特許請求の範囲の記載によって示され、さらに特許請求の範囲に記載 の均等の意味、および範囲内のすべての変更を含む。 [0043] While the embodiments of the present invention have been described above, the present invention is not limited to these embodiments and is merely an example, and does not depart from the gist of the present invention. Of course, the present invention can be implemented in various forms. The clear range is indicated by the description of the scope of claims, and further includes the equivalent meanings of the scope of claims and all modifications within the scope.
産業上の利用可能性  Industrial applicability
[0044] 本発明に係る車輪用軸受装置は、ハブ輪と複列の転がり軸受と等速自在継手とが ユニット化された第 4世代構造の車輪用軸受装置に適用することができる。  [0044] The wheel bearing device according to the present invention can be applied to a wheel bearing device of a fourth generation structure in which a hub wheel, a double row rolling bearing, and a constant velocity universal joint are unitized.
図面の簡単な説明  Brief Description of Drawings
[0045] [図 1]本発明に係る車輪用軸受装置の一実施形態を示す縦断面図である。 FIG. 1 is a longitudinal sectional view showing an embodiment of a wheel bearing device according to the present invention.
[図 2]図 1の車輪用軸受装置を適用したアクスルモジュールを示す縦断面図である。  2 is a longitudinal sectional view showing an axle module to which the wheel bearing device of FIG. 1 is applied.
[図 3]従来の車輪用軸受装置を示す縦断面図である。  FIG. 3 is a longitudinal sectional view showing a conventional wheel bearing device.
[図 4]他の従来の車輪用軸受装置を示す縦断面図である。  FIG. 4 is a longitudinal sectional view showing another conventional wheel bearing device.
符号の説明  Explanation of symbols
[0046] 1 ハブ輪  [0046] 1 hub wheel
la、 14a 内側転走面  la, 14a Inner rolling surface
lb 小径段部  lb small diameter step
2 複列の転がり軸受  2 Double row rolling bearing
3. 21 等速自在継手  3. 21 constant velocity universal joint
4 外方部材  4 Outer member
4a、 4b 外側転走面  4a, 4b Outer rolling surface
4c 車体取付フランジ  4c Body mounting flange
4d 基準面  4d Reference plane
5 内方部材  5 Inner member
6a、 6b ボール  6a, 6b ball
7 車輪取付フランジ  7 Wheel mounting flange
7a シールランド部  7a Seal land
8 ハブボルト  8 Hub bolt
9a、 9b 保持器  9a, 9b Cage
10 アウター側のシーノレ  10 The outer side
11 インナー側のシーノレ 凹凸部a、 13b エンドキャップ. 23 外側継手部材 継手内輪a、 18a、 27a トラック溝 11 Inner side Uneven part a, 13b End cap. 23 Outer joint member Fitting inner ring a, 18a, 27a Track groove
ケージ  Cage
トルク伝達ボール マウス部 肩部 Torque transmission ball Mouse part Shoulder part
. 28 軸部.28 Shaft
a インロウ部b 嵌合部 a In-row part b Fitting part
ドライブシャフト トリポード部材a 脚軸  Drive shaft Tripod member a Leg shaft
針状ころ ローラ  Needle roller Roller
外筒部 Outer cylinder
a セレーシヨン 、 30 ブーツ 、 62 ハブ輪a、 56a、 62a, 71a · ·内側転走面 、 63 複列の転がり軸受 、 64 等速自在継手 、 65 外方部材a、 53b、 65a 外側転走面 、 66 内方部材 、 67 ボール 56 内輪 a Serration, 30 Boots, 62 Hub Wheels a, 56a, 62a, 71aInner rolling surface, 63 Double row rolling bearing, 64 Constant velocity universal joint, 65 Outer member a, 53b, 65a Outer rolling surface, 66 Inner member, 67 balls 56 Inner ring
57、 68 車輪取付フランジ  57, 68 Wheel mounting flange
58、 71 外側継手部材  58, 71 Outer joint member
58a 卜ラック溝  58a 卜 Rack groove
59、 75 マウス部  59, 75 Mouse part
60、 76 肩部  60, 76 shoulder
61 止め輪  61 Retaining ring
69 ノヽブボノレ卜  69 Nobbonore
70 凹凸部  70 Concavity and convexity
72 継手内輪  72 Fitting inner ring
73 ケージ  73 cage
74 トルク伝達ボール  74 Torque transmission ball
77 軸部  77 Shaft
77a インロウ部  77a Inrow
77b 嵌合部  77b Mating part
78 アウター側のシーノレ  78 Outer side
79 インナー側のシーノレ  79 Inner side
80 保持器  80 Cage
Da 外方部材のインナー側の外径  Da Outer member inner diameter
Db アウトボード側の等速自在継手の最大外径 Db Maximum outer diameter of the constant velocity universal joint on the outboard side
Dc インボード側の等速自在継手の最大外径Dc Maximum outside diameter of constant velocity universal joint on inboard side
PCDi インナー側のボールのピッチ円直径PCDi Pitch circle diameter of inner side ball
PCDo アウター側のボーノレのピッチ円直径 PCDo Outer side bonole pitch circle diameter

Claims

請求の範囲 The scope of the claims
[1] ハブ輪と複列の転がり軸受と等速自在継手とがユニット化された車輪用軸受装置で あって、  [1] A wheel bearing device in which a hub wheel, a double row rolling bearing, and a constant velocity universal joint are unitized.
前記複列の転がり軸受が、内周に複列の外側転走面が形成され、外周に車体取 付フランジと、この車体取付フランジのインナー側に相手部材との嵌合に供される基 準面が形成された外方部材と、  The double-row rolling bearing has a double-row outer rolling surface formed on the inner periphery, a standard provided for fitting with a body mounting flange on the outer periphery and a mating member on the inner side of the body mounting flange. An outer member having a surface formed thereon;
一端部に車輪取付フランジを一体に有し、外周に前記複列の外側転走面に対向 する一方の内側転走面と、この内側転走面から軸方向に延びる円筒状の小径段部 が形成されたノ、ブ輪、およびこのハブ輪に内嵌され、外周に前記複列の外側転走面 に対向する他方の内側転走面と、この内側転走面から軸方向に延びる軸部が一体 に形成された前記等速自在継手の外側継手部材カゝらなる内方部材と、  A wheel mounting flange is integrally formed at one end, one inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a cylindrical small diameter step portion extending in the axial direction from the inner rolling surface. The other inner rolling surface that is fitted into the formed ring, hub ring, and hub ring and that faces the outer rolling surface of the double row on the outer periphery, and a shaft portion that extends in the axial direction from the inner rolling surface An inner member which is an outer joint member of the constant velocity universal joint formed integrally with
この内方部材と前記外方部材の両転走面間に転動自在に収容された複列のボー ル群とを備え、  The inner member and a double row ball group accommodated in a freely rolling manner between the rolling surfaces of the outer member,
前記軸部の端部を塑性変形させて前記ハブ輪に加締ることにより前記ハブ輪と外 側継手部材とが一体に塑性結合された車輪用軸受装置において、  In the wheel bearing device in which the hub ring and the outer joint member are integrally plastically coupled by plastically deforming an end of the shaft portion and crimping the hub ring,
前記複列のボール群のうちインナー側のボール群のピッチ円直径がアウター側の ボール群のピッチ円直径よりも大径に設定されると共に、インナー側のボール群の個 数がアウター側のボール群のボールの個数よりも多く設定されていることを特徴とす る車輪用軸受装置。  The pitch circle diameter of the inner side ball group in the double row ball group is set larger than the pitch circle diameter of the outer side ball group, and the number of inner side ball groups is the outer side ball group. A wheel bearing device characterized in that the number of balls is set to be larger than the number of balls in the group.
[2] 前記ハブ輪の内径に硬化した凹凸部が形成され、前記軸部に形成された中空状 の嵌合部を拡径させて当該凹凸部に食い込ませることにより、前記ハブ輪と外側継 手部材とが一体に塑性結合されている請求項 1に記載の車輪用軸受装置。  [2] A hardened concave and convex portion is formed on the inner diameter of the hub wheel, and a hollow fitting portion formed in the shaft portion is expanded to bite into the concave and convex portion. The wheel bearing device according to claim 1, wherein the hand member is integrally plastically coupled.
[3] 前記複列のボール群のボールが同じサイズである請求項 1または 2に記載の車輪 用軸受装置。  [3] The wheel bearing device according to claim 1 or 2, wherein the balls of the double row ball group have the same size.
[4] 請求項 1乃至 3いずれかに記載の車輪用軸受装置を備え、前記アウトボード側の等 速自在継手に一端が連結されたドライブシャフトと、このドライブシャフトの他端に連 結されたインボード側の摺動型の等速自在継手とからなることを特徴とするアクスル モジユーノレ。 前記外方部材の基準面の外径が前記等速自在継手の最大外径よりも大径に設定 されて!/、る請求項 4に記載のアクスルモジュール。 [4] A drive shaft comprising the wheel bearing device according to any one of claims 1 to 3, one end connected to the constant velocity universal joint on the outboard side, and the other end of the drive shaft. Axle modular joint characterized by comprising a sliding-type constant velocity universal joint on the inboard side. 5. The axle module according to claim 4, wherein an outer diameter of the reference surface of the outer member is set larger than a maximum outer diameter of the constant velocity universal joint!
PCT/JP2006/324862 2005-12-14 2006-12-13 Bearing device for wheel and axle module with the same WO2007069654A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005360247A JP2007162835A (en) 2005-12-14 2005-12-14 Bearing system for wheel, and axle module provided therewith
JP2005-360247 2005-12-14

Publications (1)

Publication Number Publication Date
WO2007069654A1 true WO2007069654A1 (en) 2007-06-21

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117989231A (en) * 2024-04-07 2024-05-07 苏州铁近机电科技股份有限公司 Double-row ball bearing and radiator fan
CN117989231B (en) * 2024-04-07 2024-06-11 苏州铁近机电科技股份有限公司 Double-row ball bearing and radiator fan

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010021225A1 (en) * 2008-08-18 2010-02-25 Ntn株式会社 Bearing device for wheel, and axle module

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Publication number Priority date Publication date Assignee Title
JP2004090732A (en) * 2002-08-30 2004-03-25 Ntn Corp Bearing device of driving wheel
JP2005256938A (en) * 2004-03-11 2005-09-22 Ntn Corp Joint assembly with unit cover, and bearing device total assembly for driving wheel with the same
JP2005335585A (en) * 2004-05-27 2005-12-08 Ntn Corp Axle module

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004090732A (en) * 2002-08-30 2004-03-25 Ntn Corp Bearing device of driving wheel
JP2005256938A (en) * 2004-03-11 2005-09-22 Ntn Corp Joint assembly with unit cover, and bearing device total assembly for driving wheel with the same
JP2005335585A (en) * 2004-05-27 2005-12-08 Ntn Corp Axle module

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117989231A (en) * 2024-04-07 2024-05-07 苏州铁近机电科技股份有限公司 Double-row ball bearing and radiator fan
CN117989231B (en) * 2024-04-07 2024-06-11 苏州铁近机电科技股份有限公司 Double-row ball bearing and radiator fan

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