WO2008050488A1 - Bearing device for wheel - Google Patents

Bearing device for wheel Download PDF

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Publication number
WO2008050488A1
WO2008050488A1 PCT/JP2007/001177 JP2007001177W WO2008050488A1 WO 2008050488 A1 WO2008050488 A1 WO 2008050488A1 JP 2007001177 W JP2007001177 W JP 2007001177W WO 2008050488 A1 WO2008050488 A1 WO 2008050488A1
Authority
WO
WIPO (PCT)
Prior art keywords
row
tapered roller
wheel
roller
diameter
Prior art date
Application number
PCT/JP2007/001177
Other languages
French (fr)
Japanese (ja)
Inventor
Takayuki Norimatsu
Kazuhisa Shigeoka
Akira Fujimura
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
Priority claimed from JP2006290915A external-priority patent/JP2008106860A/en
Priority claimed from JP2006290916A external-priority patent/JP2008106861A/en
Priority claimed from JP2006300145A external-priority patent/JP2008115954A/en
Priority claimed from JP2006300146A external-priority patent/JP2008114733A/en
Priority claimed from JP2006348840A external-priority patent/JP2008157394A/en
Priority claimed from JP2006352665A external-priority patent/JP2008164005A/en
Priority claimed from JP2007001674A external-priority patent/JP2008169875A/en
Priority claimed from JP2007001110A external-priority patent/JP2008169859A/en
Application filed by Ntn Corporation filed Critical Ntn Corporation
Publication of WO2008050488A1 publication Critical patent/WO2008050488A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/50Other types of ball or roller bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/50Other types of ball or roller bearings
    • F16C19/505Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30Parts of ball or roller bearings
    • F16C33/34Rollers; Needles
    • F16C33/36Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366Tapered rollers, i.e. rollers generally shaped as truncated cones
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063Fixing them on the shaft
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70Diameters; Radii
    • F16C2240/80Pitch circle diameters [PCD]
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00Articles relating to transporting
    • F16C2326/01Parts of vehicles in general
    • F16C2326/02Wheel hubs or castors

Definitions

  • the present invention relates to a wheel bearing device that rotatably supports a wheel of an automobile or the like, and more particularly to a wheel bearing device that is reduced in weight and increased in rigidity.
  • wheel bearing devices for supporting wheels of automobiles and the like support a hub wheel for mounting a wheel rotatably via a rolling bearing, and there are a drive wheel and a driven wheel.
  • the inner ring rotation method is generally used for driving wheels, and both the inner ring rotation method and outer ring rotation method are used for driven wheels.
  • a double-row angular contact ball bearing that has a desired bearing rigidity, exhibits durability against misalignment, and has a low rotational torque from the viewpoint of improving fuel efficiency is often used.
  • double row tapered roller bearings are used in vehicles with heavy vehicle body weight such as off-road force and trucks.
  • the wheel bearing device has a structure called a first generation in which a wheel bearing composed of a double-row anguilla ball bearing or the like is fitted between a knuckle and a hub wheel constituting a suspension device.
  • Second generation structure with body mounting flange or wheel mounting flange formed directly on the outer periphery of the outer member, or third generation structure with one inner raceway formed directly on the outer periphery of the hub wheel, or hub It is roughly divided into the 4th generation structure in which the inner rolling surface is directly formed on the outer circumference of the outer joint member of the wheel and constant velocity universal joint.
  • the wheel bearing device shown in Fig. 3 2 is a lightweight, compact, 4th generation structure with a hub wheel 1 0 0 and double row rolling bearing 1 0 1 and constant velocity universal joint 1 0 2 and are united.
  • the double row rolling bearing 100 includes an outer member 10 3, an inner member 10 4, and a plurality of poles 10 5 and tapered rollers 10 6 accommodated between the two members.
  • the side closer to the outer side of the vehicle in the assembled state is the outer side (left side of the drawing), and the side closer to the center is It is called the inner side (right side of the drawing).
  • the outer member 10 3 integrally has a vehicle body mounting flange 10 3 c attached to a knuckle constituting a suspension device (not shown) on the outer periphery, and a double row outer rolling surface 10 on the inner periphery. 3 a and 1 0 3 b are formed.
  • the diameter of the outer rolling surface 10 3 a on the outer side is set to be smaller than the diameter of the outer rolling surface 10 3 b on the inner side.
  • the inner member 10 04 is press-fitted into the hub wheel 100, an outer joint member 10 8, which will be described later, integrally formed with the hub wheel 100, and the outer joint member 10 8. And a separate inner ring 1 0 7.
  • the hub wheel 1 0 0 has a wheel mounting flange 1 OO b for mounting a wheel (not shown) at one end, and a double row outer rolling surface 1 0 3 a, 1 on the outer periphery.
  • 0 3 b Outer rolling surface on one side of outer side 1 0 3 a Inner rolling surface facing 1 0 3 a is directly formed, and the outer ring of inner ring 1 0 7 has double row outer rolling surface
  • An inner rolling surface 1 0 7 a facing the outer rolling surface 1 0 3 b on the inner side of 1 0 3 a and 1 0 3 b is formed.
  • the constant velocity universal joint 1 0 2 has an outer joint member 1 0 8 composed of a cup-shaped mouth portion 1 0 9 and a shoulder portion 1 1 0 which forms the bottom of the mouth portion 1 0 9, A curved track groove 10 8 a is formed on the inner periphery of the outer joint member 10 8.
  • the inner ring 10 07 is press-fitted into the outer diameter of the mouse portion 10 9 and is fixed in the axial direction by a retaining ring 1 1 1.
  • a plurality of tapered rollers 1 0 6 are rotatably accommodated between the faces 1 0 3 b and 1 0 7 a, respectively, and the pole 1 on the outer side of the rows 1 0 5 and 1 0 6
  • the pitch circle diameter of the fifth row is set smaller than the pitch circle diameter of the inner row of tapered rollers.
  • This wheel bearing device has a vehicle body mounting flange 1 1 2 c integrally attached to a knuckle (not shown) on the outer periphery, and a double row outer rolling surface 1 1 2 on the inner periphery.
  • the inner ring 1 1 5 is fixed in the axial direction by a caulking portion 1 1 4 c formed by plastically deforming the small diameter step portion 1 1 4 b of the hub wheel 1 1 4 radially outward.
  • the seal 1 2 1 and 1 2 2 are installed in the opening of the annular space formed between the outer member 1 1 2 and the inner member 1 1 6, and the lubricating grease sealed inside the bearing And prevents rainwater and dust from entering the bearings from the outside.
  • the pitch circle diameter D1 of the pole 1 17 row on the one side of the counter is set larger than the pitch circle diameter D2 of the pole 1 1 8 row on the inner side.
  • the inner raceway 1 1 4 a of the hub wheel 1 1 4 is the inner raceway 1 1 5 of the inner race 1 1 5
  • the outer side rolling surface 1 1 2 a on the outer side of the outer member 1 1 2 has a larger diameter than the outer rolling surface 1 1 2 b on the inner side. And more poles 1 1 7 on the outer side are accommodated than poles 1 1 8 on the inner side.
  • Patent Document 1 Japanese Patent Laid-Open No. 1-9-9 30 8
  • Patent Document 2 Japanese Patent Laid-Open No. 2 0 0 4 _ 1 0 8 4 4 9
  • the pitch circle diameter D 1 of the outer pole 1 117 row is set larger than the pitch circle diameter D 2 of the inner pole 1 1 8 row.
  • the inner raceway surface 1 1 4 a of the hub wheel 1 1 4 has a larger diameter than the inner raceway surface 1 1 5 a of the inner race 1 1 5.
  • the loads applied to the inner and outer bearing rows are different from each other, and the load applied to the inner bearing row is generally larger than the load applied to the outer bearing row.
  • the basic load rating of the inner side bearing row is smaller than the basic load rating of the outer side bearing row, resulting in a shorter life.
  • the present invention has been made in view of such circumstances, and simultaneously solves the conflicting problems of light weight and compactness and high rigidity of the device, and at the same time, has improved strength and durability.
  • An object of the present invention is to provide a bearing device for a vehicle.
  • the present invention includes an outer member integrally having a vehicle body mounting flange to be attached to a knuckle on the outer periphery, and a double row outer rolling surface formed on the inner periphery.
  • a hub wheel having a wheel mounting flange for mounting a wheel on one end and a small diameter step portion formed on the outer periphery, and press fitting into the small diameter step portion of this hub ring
  • An inner member comprising at least one inner ring formed on the outer periphery with an inner rolling surface facing the double row outer rolling surface, and both rolling surfaces of the inner member and the outer member.
  • a wheel bearing device having a double row tapered roller row accommodated in a freely rolling manner between the pitch roller diameters of the inner side conical roller row of the double row conical roller row and having a conical shape on the outer side.
  • the roller diameter is set to be larger than the pitch circle diameter of the roller row, and further, the roller diameter of the inner side tapered roller row is set to be larger than the roller diameter of the outer side tapered roller row,
  • the roller length of the outer side tapered roller row is set to be longer than the roller length of the inner side tapered roller row.
  • the pitch circle of the tapered roller row on the inner side of the double row tapered roller row is provided.
  • the diameter is set larger than the pitch circle diameter of the tapered roller row on the outer side
  • the roller diameter of the tapered roller row on the inner side is set larger than the roller diameter of the tapered roller row on the outer side.
  • the roller length of the outer tapered roller train is set to be longer than the roller length of the inner tapered roller train, so that the rigidity and life of the bearing can be improved, and the bearing The space can be used effectively to make it lighter and more compact. Therefore, it is possible to provide a wheel bearing device that can simultaneously solve the conflicting problems of light weight and compactness and high rigidity of the device, and that has improved strength and durability.
  • the present invention also includes an outer member integrally having a vehicle body mounting flange to be attached to a knuckle on the outer periphery, and a double-row outer rolling surface formed on the inner periphery;
  • a hub wheel that has a wheel mounting flange for mounting the wheel and has a small-diameter step formed on the outer periphery, and is press-fitted into the small-diameter step portion of the hub wheel, and faces the outer surface of the double row on the outer periphery.
  • An inner member formed of at least one inner ring formed with an inner raceway, and a double row conical roller row accommodated between the inner member and the outer member so as to roll freely.
  • the pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row,
  • the inner The roller diameter of the tapered roller row on the side is set to a large diameter as well.
  • the pitch circle diameter of the tapered roller row on the inner side of the double row tapered roller row is provided. Is set to be larger than the pitch circle diameter of the outer tapered roller train, and the roller diameter of the inner tapered roller train is set to be larger than the roller diameter of the outer tapered roller train.
  • the number of rollers of the double row tapered roller row may be set to be the same.
  • the present invention also includes an outer member integrally including a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end.
  • a hub wheel having a wheel mounting flange for mounting the outer ring, and a small-diameter step portion formed on the outer periphery, and a small-diameter step portion of the hub wheel, and press-fitted into the outer periphery of the double row on the outer periphery.
  • An inner member composed of at least one inner ring formed with an inner rolling surface, and a double row tapered roller row accommodated so as to roll between the inner member and both rolling surfaces of the outer member.
  • the pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row
  • the roller length of the inner side tapered roller row is the outer It is set to be longer than the roller length of the tapered roller rows of the force, one, number rollers of the tapered roller rows of the inner one side the Auta -More than the number of rollers in the tapered roller row on the side.
  • the pitch circle diameter of the row is set to be larger than the pitch circle diameter of the outer side tapered roller row
  • the roller length of the inner side tapered roller row is larger than the length of the outer side tapered roller row.
  • the number of rollers in the tapered roller train on the inner side is set to be larger than the number of rollers in the tapered roller row on the outer side, so the weight of the device is compact and the rigidity is increased.
  • the present invention also includes an outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end.
  • a hub wheel having a wheel mounting flange for mounting the outer ring, and a small-diameter step portion formed on the outer periphery, and a small-diameter step portion of the hub wheel, and press-fitted into the outer periphery of the double row on the outer periphery.
  • An inner member composed of at least one inner ring formed with an inner rolling surface, and a double row tapered roller row accommodated so as to roll between the inner member and both rolling surfaces of the outer member.
  • a pitch circle diameter of an outer side tapered roller row of the double row tapered roller rows is set larger than a pitch circle diameter of an inner side tapered roller row
  • the roller length of the inner side tapered roller row is the outer Is set to be longer than the roller length of the tapered roller rows of the force
  • one, number rollers of the tapered roller rows of the outer side the inner - is set larger than the number roller on the side of the tapered roller rows.
  • the pitch circle diameter of the inner roller is set to be larger than the pitch circle diameter of the inner side tapered roller train, and the roller length of the inner side tapered roller train is larger than the length of the outer tapered roller train. Is set longer and the number of rollers in the outer tapered roller row is set to be larger than the number of rollers in the inner tapered roller row. It is possible to provide a wheel bearing device that improves the rigidity and life of the bearing without increasing the outer diameter of the outer member, and the basic rated load of the bearing row on the inner side is increased. it can.
  • a roller diameter of the inner side tapered roller train and a roller diameter of the outer tapered roller train may be set to be the same.
  • an outer member having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end
  • a hub wheel having a wheel mounting flange for mounting the outer ring, and a small-diameter step portion formed on the outer periphery, and a small-diameter step portion of the hub wheel, and press-fitted into the outer periphery of the double row on the outer periphery.
  • An inner member composed of at least one inner ring formed with an inner rolling surface, and a double row tapered roller row accommodated so as to roll between the inner member and both rolling surfaces of the outer member.
  • the pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row
  • the roller length of the inner side tapered roller row is the outer It is set to be longer than the roller length of the tapered roller row of and the number roller diameter Oyobi rollers of these tapered rollers is set to the same.
  • the pitch circle diameter of the tapered roller row on the inner side of the double row tapered roller row is provided. Is set to be larger than the pitch circle diameter of the outer side tapered roller row, the roller length of the inner side tapered roller row is set to be longer than the outer length of the tapered roller row of the outer side, and Since these tapered rollers have the same roller diameter and the same number of rollers, they can be made lighter and more compact, and the inner diameter can be reduced while preventing the cage strength from being reduced by increasing the roller diameter and number of rollers. It is possible to provide a wheel bearing device in which the basic load rating of the side bearing row is increased and the rigidity and life of the bearing are improved.
  • the present invention provides a vehicle body mounting flange for mounting to a knuckle on the outer periphery.
  • the outer member with a double row outer raceway formed on the inner periphery and the wheel mounting flange for mounting the wheel on one end are integrated, and the small diameter step is formed on the outer periphery.
  • an inner member comprising at least one inner ring that is press-fitted into a small-diameter step portion of the hub ring and has an inner rolling surface facing the outer rolling surface of the double row on the outer periphery.
  • a pitch circle diameter of the double-row tapered roller row is The roller diameter of the inner side tapered roller row of the double row tapered roller rows is set to be larger than the roller diameter of the outer side tapered roller row, and these tapered rollers The number of rollers in the row is set to be the same.
  • the pitch circle diameters of the double row tapered roller rows are set to be the same, and
  • the roller diameter of the tapered roller row on the inner side of the row of tapered roller rows is set larger than the roller diameter of the tapered roller row on the outer side, and the number of rollers in these tapered roller rows is set to be the same. Therefore, it is possible to increase the basic rated load of the inner side bearing row without increasing the pitch circle diameter of the inner one side, and to prevent the outer member from increasing its outer diameter.
  • the roller length of the inner side tapered roller row is set to be longer than the roller length of the outer side tapered roller row, the inner one side tapered roller It is possible to further increase the basic load rating of the inner side bearing row without increasing the pitch circle diameter of the row, to suppress the outer diameter of the outer member, and to reduce the outer diameter of the outer member, while reducing the weight and reducing the rigidity of the bearing.
  • the service life can be improved.
  • the present invention has a vehicle body mounting flange integrally attached to a knuckle on the outer periphery, and an outer side in which a double row outer rolling surface is formed on the inner periphery.
  • a hub wheel having a wheel mounting flange for mounting a wheel at one end, a small-diameter step portion formed on the outer periphery, and press-fitted into the small-diameter step portion of the hub wheel.
  • An inner member composed of at least one inner ring formed with an inner rolling surface opposite to the outer rolling surface, and a composite member housed in a freely rolling manner between the inner and the outer member.
  • the pitch circle diameter of the double row tapered roller rows is set to be the same, and the outer side tapered roller row of the double row tapered roller rows is arranged. Set the roller length longer than the roller length of the tapered roller row on the inner side. It is, and the number rollers of these tapered rollers column same - is set to. ⁇ ⁇ ⁇ Claim 1 2
  • the pitch circle diameter of the double row tapered roller row is set to be the same, and
  • the roller length of the outer tapered roller row in the row is set to be longer than the roller length of the inner tapered roller row, and the number of rollers in these tapered roller rows is set to be the same. Therefore, the basic load rating of the outer side bearing row can be increased without increasing the pitch circle diameter of the outer side tapered roller row and without increasing the number of rollers of the tapered roller. -It is possible to provide a wheel bearing device in which the rigidity and life of the bearing are improved while achieving compactness.
  • roller diameter of the outer tapered roller row and the roller diameter of the inner tapered roller row are set to be the same, the outer side of the outer member An increase in the outer diameter can be suppressed.
  • the present invention also includes an outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end.
  • a hub wheel integrally having a wheel mounting flange for mounting, and having a small-diameter step portion extending in the axial direction from the wheel mounting flange on the outer periphery, and An inner member composed of at least one inner ring press-fitted into the small-diameter step portion of the ring and formed with an inner rolling surface facing the outer rolling surface of the double row on the outer circumference, and the inner member
  • the pitch circle diameter of the double row tapered roller row is set to be the same.
  • the diameter of the outer tapered roller row of the double row tapered roller rows is set to be smaller than the roller diameter of the inner side tapered roller row, and the outer roller side tapered roller row
  • the number of rollers is set to be greater than the number of rollers in the inner side tapered roller row, and the roller length of the inner side tapered roller row is set to be longer than the roller length of the outer side tapered roller row.
  • the pitch circle diameters of the double-row tapered roller rows are set to be the same, and the double-row cone rollers
  • the roller diameter of the outer tapered roller train is set to be smaller than the roller diameter of the inner one, and the number of rollers in the outer tapered roller train is the inner one. Since the roller length of the inner tapered roller row is set to be longer than the roller length of the outer tapered roller row, the pitch of the outer tapered roller row is set. It is possible to increase the basic load rating of both bearing rows without increasing the diameter of the circle, and to provide a wheel bearing device that is lightweight and compact, while improving the rigidity and life of the bearing. .
  • an outer-side inner rolling surface is directly formed on the outer periphery of the hub wheel, and the small-diameter step portion extending in the axial direction from the inner-rolling surface is formed. If the inner ring on the inner side is press-fitted into the small diameter step portion through a predetermined opening, the device can be made lighter and more compact, and the pitch circle diameter in the tapered roller array on the inner side can be reduced. The inner ring on the inner side corresponding to the amount of diameter expansion The hoop stress generated on the inner raceway surface and the outer diameter of the inner ring due to plastic deformation of the caulking part can be suppressed to improve the strength of the hub ring and inner ring. Can do. ⁇ ⁇ ⁇ Claim 1 6
  • the small-diameter step portion of the hub wheel is It can be formed into any shape, and the workability can be improved, and the inner ring inner wall thickness can be increased corresponding to the amount of pitch circle diameter expansion in the inner roller taper row. It is possible to improve the strength and durability of the inner ring by suppressing the hoop stress generated on the inner raceway surface and outer diameter of the inner ring due to plastic deformation of the caulking portion. ⁇ ⁇ ⁇ Claim 1 7
  • An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel attachment for attaching the wheel to one end
  • a hub wheel having a flange integrally formed and formed on the outer periphery thereof with an inner rolling surface facing one of the outer rolling surfaces of the double row, and a small-diameter step portion extending in an axial direction from the inner rolling surface; and
  • An inner member comprising an inner ring that is press-fitted into a small-diameter step portion of the hub wheel and has an inner rolling surface facing the other of the outer rolling surfaces of the double row on the outer periphery; and the inner member and the outer A double row tapered roller row that is rotatably accommodated between both rolling surfaces of the member, and is formed by a caulking portion that is formed by plastically deforming an end portion of the small diameter step portion radially outward.
  • the double-row tapered roller In a bearing device for a wheel in which an inner ring is fixed in an axial direction with respect to a hub wheel, the double-row tapered roller
  • the pitch circle diameter of the inner side tapered roller train is set to be larger than the pitch circle diameter of the outer tapered roller train, and the number of rollers of the double row tapered roller train is set to be the same.
  • the roller diameter of the inner tapered roller train is set to be larger than the roller diameter of the outer tapered roller train, and the roller length of the outer tapered roller train is It is set longer than the roller length of the tapered roller row on the side.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1, A wheel bearing 2 fixed to the hub wheel 1 is provided.
  • the hub wheel 1 integrally has a wheel mounting flange 3 for mounting a wheel (not shown) at one end portion on the outer side, and has a small diameter extending in an axial direction from the wheel mounting flange 3 through a shoulder portion 1a.
  • a step 1b is formed.
  • Hub ports 3 a are planted on the wheel mounting flange 3 at equal intervals in the circumferential direction.
  • the wheel bearing 2 is press-fitted into the small-diameter step portion 1b through a predetermined shimiro while being in contact with the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.
  • the hub ring 1 is formed of medium and high carbon steel containing carbon 0.40 to 0.8 O wt% such as S 53 C, and is hardened by induction hardening from the shoulder 1a to the small diameter step 1b. Has been cured to a range of 5 8 to 6 4 HRC. Note that the caulking portion 1c remains the surface hardness after forging.
  • the wheel bearing 2 is integrally provided with a vehicle body mounting flange 4c to be attached to a knuckle (not shown) constituting a suspension device on the outer periphery, and a double row outer rolling surface 4 on the inner periphery.
  • Two outer rings with outer members 4 with a and 4 b and inner rolling surfaces 5 a and 6 a facing the outer circumferential surfaces 4 a and 4 b of the double row on the outer circumference. 5, 6 and double rolling tapered rollers 9, 10 which are accommodated in a rolling manner via cages 7, 8 between both rolling surfaces 4a, 5a and 4b, 6a. Yes.
  • Seals 1 1 and 1 2 are attached to the opening of the annular space formed between the outer member 4 and the two inner rings 5 and 6, and leakage of grease sealed inside the bearing Prevents rainwater and dust from entering the bearing.
  • Inner raceway surfaces 5a and 6a of inner rings 5 and 6 are line contoured to tapered rollers 9 and 10 This is a so-called back-to-back type double-row tapered roller bearing that is formed in a tapered shape with a small diameter side (front) end face 5d and 6d abutting in a butted state. Then, the large rollers 5 b and 6 b for guiding the tapered rollers 9 and 10 to the large diameter side of the inner rolling surfaces 5 a and 6 a and the tapered rollers 9 and 10 to drop off on the small diameter side are provided. Gavels 5 c and 6 c are formed for prevention.
  • the outer member 4 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the double row outer rolling surfaces 4 a and 4 b are hardened by induction hardening. Hardened to a range of 58-64 H RC.
  • the inner rings 5 and 6 and the tapered rollers 9 and 10 are made of high carbon chrome steel such as SU 2 and hardened in the range of 58 to 64 H RC to the core part by quenching.
  • the pitch circle diameter P CD i of the inner row of tapered rollers 10 on the inner side is larger than the pitch circle diameter PCD o of the row of 9 tapered rollers on the outer side (P CD i> PCDo).
  • the roller diameter di of the 10-row tapered roller on the inner side is set to a larger diameter (di> do) than the roller diameter do of the 9-side tapered roller on the outer side, and the roller length is The roller length L o of the 9-row tapered roller is set to be longer than the roller length L i of the 10-side tapered roller 10 (L o> L i).
  • the number of rollers in the tapered rollers 9 and 10 row is set to be the same. As a result, it is possible to improve the rigidity and life of the bearing, and to provide a wheel bearing device that is lightweight and compact by effectively utilizing the bearing space.
  • the inner diameters of the inner rings 5 and 6 are made the same so that the inner diameters 5 and 6 are fitted to each other.
  • the part 1 b can be formed into a straight shaft shape with the shaft diameter d 1, which can improve the workability of the hub wheel 1, and the pitch circle diameter PC D i in the row of tapered rollers 10 on the inner side
  • the wall thickness t of the inner ring 6 on the inner side can be increased corresponding to the amount of diameter expansion, and the inner raceway surface 6a and the outer diameter 6e of the inner ring 6 can be increased with plastic deformation of the caulking portion 1c.
  • the hoop stress generated can be suppressed and the strength and durability of the inner ring 6 can be improved.
  • FIG. 2 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described embodiment only in the configuration of the hub wheel, and other parts and parts having the same parts or the same functions are denoted by the same reference numerals for detailed description. Omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 1 3 and the small diameter step portion 1 3 b of the hub wheel 13. And an inner member 14 composed of an inner ring 6.
  • the hub wheel 1 3 has an outer outer rolling surface 4 a that faces the outer outer rolling surface 4 a on the outer periphery, and a small-diameter step portion 1 3 that extends in the axial direction from the inner rolling surface 1 3 a. b is formed.
  • the inner ring 6 is abutted against the shoulder 1 3 c of the hub ring 1 3 in abutting condition, is press-fitted into the small-diameter stepped portion 1 3 b through a predetermined shimiro, and is fixed in the axial direction by the crimping portion 1 c. .
  • Seals 15 and 1 2 are attached to the openings of the annular space formed between the outer member 4 and the hub ring 13 and the inner ring 6, and the grease sealed inside the bearing is exposed to the outside. It prevents leakage and rainwater and dust from entering the bearing.
  • the hub wheel 13 is made of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and the inner rolling surface from the seal land portion 3 b in which the seal 15 is in sliding contact.
  • the surface hardness is hardened to a range of 58 to 64 HRC by induction hardening over 1 3 a and small diameter step 1 3 b.
  • the tapered roller on the inner side is similar to the above-described embodiment.
  • pitch circle diameter PCD i is set larger than pitch circle diameter PCD o of 9 rows of pitch rollers (PCD i> PCD o), and inner side of tapered rollers 10 rows
  • the roller diameter di is set to a larger diameter (di> do) than the roller diameter do of the outer side tapered roller 9 rows
  • the roller length L o of the outer side tapered roller 9 rows is the inner side cone.
  • the roller length is set to be longer than the roller length L i of row 10 (L o> L i). This makes it possible to improve the rigidity and life of the bearing while achieving light weight and compactness, and also to increase the pitch circle diameter PCD i in the inner row of tapered rollers 10 on the inner side.
  • Inner ring The hub ring 1 3 can be made thicker, and the hoop stress generated on the inner raceway surface 6a and outer diameter 6e of the inner ring 6 due to plastic deformation of the caulking portion 1c can be suppressed. And Strength of inner ring 6 ⁇ Durability can be improved.
  • FIG. 3 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention.
  • This embodiment is basically the same as the first embodiment (FIG. 1) described above except that the configuration of the wheel bearing is different, and other parts and parts having the same parts or functions having the same parts have the same reference numerals. The detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 ′ and a wheel bearing 16 fixed to the hub wheel 1 ′.
  • the wheel bearing 16 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening in contact with the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′. It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.
  • the wheel bearing 16 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and formed with a plurality of outer rolling surfaces 4a and 4b on the inner periphery, and on the outer periphery.
  • Two inner rings 5 ′, 6 ′ formed with inner rolling surfaces 5 a, 6 a facing the outer rolling surfaces 4 a, 4 b of the double row, and both rolling surfaces 4 a, 5 a and
  • a plurality of tapered rollers 9 and 10 are provided between 4 b and 6 a so as to roll freely through cages 7 and 8.
  • the tapered roller on the inner side is similar to the above-described embodiment.
  • pitch circle diameter PCD i is set larger than pitch circle diameter PCD o of 9 rows of pitch rollers (PCD i> PCD o), and inner side of tapered rollers 10 rows
  • the roller diameter di is set to a larger diameter (di> do) than the roller diameter do of the outer side tapered roller 9 rows
  • the roller length L o of the outer side tapered roller 9 rows is the inner side cone.
  • the roller length is set to be longer than the roller length L i of row 10 (L o> L i). This makes it possible to improve the rigidity and life of the bearing while achieving light weight and compactness, and also to increase the pitch circle diameter PCD i in the inner row of tapered rollers 10 on the inner side.
  • Hub of The shaft diameter d2 of the small-diameter step 1b 'in the wheel 1' can be formed as a large diameter (d2> d1 (Fig. 1)), and the strength of the hub wheel 1 'can be improved.
  • FIG. 4 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing device according to the present invention.
  • This embodiment is basically the same as the third embodiment described above (Fig. 3) except that the structure of the wheel is different, and that the same parts and parts having the same function or the same function are the same. Reference numerals are assigned and detailed description is omitted.
  • This wheel bearing device is for a driven wheel referred to as a third generation, and includes an outer member 4, a hub wheel 1 3 ', and a small-diameter step portion 1 3 b' of the hub wheel 1 3 '. And an inner member 17 made of an inner ring 6 'press-fitted into the inner ring.
  • Hub wheel 1 3 ' is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the inner rolling surface from seal land portion 3 b in which seal 15 is in sliding contact.
  • the surface hardness is hardened to a range of 58 to 64 H RC by induction hardening over 1 3 a and the small diameter step portion 1 3 b ′.
  • the pitch circle diameter of the inner one side tapered roller 10 row 10 PCi is the pitch circle diameter of the outer row tapered roller 9 row.
  • PCDo PCDo
  • inner roller tapered roller diameter 10 is larger than roller diameter di of outer side tapered roller 9 rows.
  • the roller length L o of the outer side conical roller 9 row is set to be longer than the roller length L i of the inner one side tapered roller 10 row (L o> L i).
  • the rigidity and life of the bearing can be improved while achieving light weight and compactness, and the expansion diameter of the pitch circle diameter P CD i in the tapered row on the inner side 10 can be accommodated.
  • the shaft diameter d2 of the small diameter step 1 3 b 'in the hub ring 1 3' on the inner side can be made larger (d 2> d 1 (Fig. 2)), and the strength of the hub ring 1 3 ' ⁇ Durability can be improved.
  • FIG. 5 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing device according to the present invention.
  • This embodiment is basically the same as the first embodiment (FIG. 1) described above except that the configuration of the tapered roller on the outer side is different, and other parts and parts having the same parts or the same functions.
  • the same reference numerals are given to the same parts and detailed explanations are omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 18 fixed to the hub wheel 1.
  • the wheel bearing 18 is press-fitted into the small-diameter step 1 b through a predetermined squeeze opening while being abutted against the shoulder 1 a of the hub wheel 1 and the end of the small-diameter step 1 b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this manner.
  • the wheel bearing 18 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and a plurality of outer rolling surfaces 4a and 4b formed on the inner periphery, and on the outer periphery.
  • Two inner races 1 9 and 6 formed with inner rolling surfaces 1 9 a and 6 a opposite to these double-row outer rolling surfaces 4 a and 4 b, and both rolling surfaces 4 a and 19 Double row tapered rollers 21 and 10 rows are provided between a and 4 b and 6 a so as to be freely rollable via cages 20 and 8.
  • Inner raceway surfaces 19a and 6a of inner rings 19 and 6 are formed in a taper shape in line contact with tapered rollers 21 and 10 and have a small diameter (front) side end surface 5d, 6d constitutes a back-to-back type double row tapered roller bearing where they are abutted in abutting condition.
  • the large roller 5 b, 6 b to guide the tapered rollers 2 1, 10 on the large diameter side of the inner rolling surfaces 1 9 a, 6 a, and the tapered rollers 2 1, 1 on the small diameter side Gavels 5c and 6c are formed to prevent 0 from falling off.
  • the pitch circle diameter P CD i of the inner one side tapered roller 10 row is larger than the pitch circle diameter P CD o of the outer side tapered roller 21 row (P CD i> P CD o) and the roller diameter di of the inner one side 10 row is set larger than the roller diameter do of the outer row 2 roller row do (di> do) ing.
  • the number of rollers in the 2 1 and 1 0 rows is set to be the same.
  • 6 can be formed into a straight shaft shape with the shaft diameter d 1 and the small diameter stepped portion 1 b can improve the workability of the hub wheel 1 and the tapered roller on the inner side 1 0
  • the inner diameter of inner ring 6 on the inner side can be increased corresponding to the amount of expansion of pitch circle diameter PCD i in the row, and the inner raceway surface 6 of inner ring 6 can be increased along with plastic deformation of caulking portion 1c.
  • FIG. 6 is a longitudinal sectional view showing a sixth embodiment of the wheel bearing device according to the invention.
  • This embodiment is basically the same as the second embodiment (FIG. 2) described above except that the configuration of the tapered roller on the outer side is different, and other parts and parts having the same parts or the same functions.
  • the same reference numerals are given to the same parts and detailed explanations are omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 2 2, and the small-diameter step portion 1 3 b of the hub wheel 2 2. And an inner member 23 made of an inner ring 6.
  • the hub wheel 2 2 has an outer rolling surface 4 a on the outer side facing the outer rolling surface 4 a on the outer side and a small diameter step portion 1 extending in the axial direction from the inner rolling surface 2 2 a. 3 b is formed.
  • the hub wheel 2 2 is formed of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and the inner surface of the rolling contact 2 2 from the seal land 3 b in which the seal 15 is in sliding contact.
  • the surface hardness is hardened to a range of 58 to 64 HRC by induction hardening over a and the small diameter step 1 3 b.
  • the tapered roller on the inner side is the same as the above-described embodiment.
  • 1 0 row pitch circle diameter PCD i outer tapered roller 2
  • 1 row pitch circle diameter PCD o is larger than PCD o (PCD i> PCD o) and inner one tapered roller
  • the roller diameter di of the 10th row is set to a larger diameter (di> do) than the tapered diameter do of the 2nd row.
  • the number of rollers in the 2 1 and 1 0 rows is set to be the same.
  • the inner wall 6 on the inner side 6 can be increased in thickness t in accordance with the amount of expansion of the pitch circle diameter PCD i in the row of tapered rollers 10 on the inner side, and the plasticity of the caulking portion 1 c can be increased.
  • the hoop stress generated on the inner raceway surface 6a and outer diameter 6e of the inner ring 6 due to deformation can be suppressed to improve the strength and durability of the hub wheel 22 and inner ring 6
  • FIG. 7 is a longitudinal sectional view showing a seventh embodiment of the wheel bearing device according to the invention.
  • This embodiment is basically the same as the above-described fifth embodiment (FIG. 5) except that the structure of the wheel and the wheel bearing is partially different, and has the same parts and the same functions. Parts and parts are denoted by the same reference numerals, and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 'and a wheel bearing 24 fixed to the hub wheel 1'.
  • the wheel bearing 2 4 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening while being in contact with the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′. It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.
  • the wheel bearing 24 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and formed with a plurality of outer rolling surfaces 4a, 4b on the inner periphery, and on the outer periphery.
  • Two inner races 1 9 ′, 6 ′ formed with inner rolling surfaces 19 a, 6 a facing the outer rolling surfaces 4 a, 4 b of these double rows, and both rolling surfaces 4 a, Between 1 9 a and 4 b, 6 a Are provided with a plurality of tapered rollers 2 1, 1 0, which are rotatably accommodated via cages 20, 8.
  • the tapered roller on the inner side is similar to the above-described embodiment.
  • PCD i is the outer tapered roller 2 1 row pitch diameter P CD o is larger than P CD o (P CD i> P CD o) and the inner cone
  • the roller diameter di of the roller 10 row is set to be larger than the roller diameter do of the outer side roller 2 (di> do).
  • the number of rollers in the tapered roller 2 1 and 1 0 rows is set to be the same.
  • the rigidity and life of the bearing can be improved while achieving light weight and compactness
  • the inner diameter of the tapered roller 10 row on the inner side corresponds to the amount of expansion of the pitch circle diameter PCD i.
  • the shaft diameter d2 of the small-diameter stepped portion 1b 'in the hub ring 1' on one side can be made larger (d2> d1 (Fig. 1)), and the strength and durability of the hub ring 1 ' Can be improved.
  • FIG. 8 is a longitudinal sectional view showing an eighth embodiment of the wheel bearing device according to the invention. Note that this embodiment is basically the same as the above-described sixth embodiment (FIG. 6) except that the configuration of the wheel is different, and that the same parts and parts having the same function or the same function are the same. Reference numerals are assigned and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 13b' of the hub wheel 22 '. And an inner member 25 made of an inner ring 6 '.
  • the hub wheel 22 ' is formed of medium and high carbon steel containing carbon 0.440 to 0.8 ow t%, such as S 53 C, and the inner rolling surface 22a and the small diameter from the seal land 3b where the seal 15 is in sliding contact.
  • the surface hardness of the stepped part 1 3 b ' is in the range of 58 to 64 H RC by induction hardening.
  • this embodiment is similar to the above-described sixth embodiment.
  • Tapered roller 1 Pitch circle diameter of row 0 PCD i is set to a larger diameter (PCD i> PCDo) than the pitch circle diameter P CD o of 21 rows of outer side tapered roller on inner side 1
  • the 0-row roller diameter di is set to a larger diameter (di> do) than the 21-row roller diameter do.
  • the number of rollers in the row is set to be the same.
  • the shaft diameter d2 of the small diameter step 1 3 b 'in the hub ring 22' on the inner side can be made larger (d2> d1), and the strength of the hub ring 22 'is improved. Can be made.
  • FIG. 9 is a longitudinal sectional view showing a ninth embodiment of the wheel bearing device according to the invention.
  • This embodiment is basically different from the above-described fifth embodiment (FIG. 5) only in the configuration of the tapered roller on one inner side, and other parts having the same parts, the same parts, or the same functions.
  • the parts are denoted by the same reference numerals, and detailed description is omitted.
  • This wheel bearing device is for a driven wheel referred to as a second generation, and includes a hub wheel 1 and a wheel bearing 26 fixed to the hub wheel 1.
  • the wheel bearing 26 is press-fitted into the small-diameter step portion 1b through a predetermined squeezing opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this way.
  • the wheel bearing 26 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and a plurality of outer rolling surfaces 4a and 4b formed on the inner periphery, and these on the outer periphery.
  • Two inner races 1 9 and 27 formed with inner rolling surfaces 1 9 a and 27 a opposite to the double row outer rolling surfaces 4 a and 4 b, and both rolling surfaces 4 a, 19 a and 4 b, 27 a Double row tapered rollers 21, which are rotatably accommodated between cages 20, 28, It has 29 columns.
  • the inner rolling surface 27a of the inner ring 27 is formed in a taper shape that makes line contact with the tapered roller 29, and the rear surface where the small-diameter (front) side end surfaces 5d and 6d are abutted in a butted state
  • a double-row tapered roller bearing of the matching type is constructed.
  • the inner ring 27 and the tapered roller 29 are made of high carbon chrome steel such as SJ2 and hardened in the range of 58 to 64 H RC to the core part by quenching.
  • the pitch circle diameter P CD i of 29 inner tapered rollers 29 rows is larger than the pitch circle diameter PCD o of 21 outer tapered rollers 21 rows (PCD i> PCDo)
  • the roller diameter di of 29 rows of tapered rollers on the inner side is set to a larger diameter (di> do) than the roller diameter do of 21 rows of tapered rollers on the outer side.
  • the roller length L i of the inner side tapered roller 29 row is set to be longer than the roller length L o of the outer side tapered roller 21 row (L i> L o).
  • the number of rollers in the 29th row is set to be the same.
  • the basic dynamic load rating of the inner bearing row can be increased to improve the bearing rigidity and life, and the bearings for wheels can be made lightweight by making effective use of the bearing space.
  • a device can be provided.
  • the inner rings 19 and 27 are fitted together by making the inner rings 19 and 27 have the same inner diameter.
  • Small diameter step 1 b can be formed into a straight shaft consisting of shaft diameter d 1, improving workability of hub wheel 1 and pitch circle diameter in 29 rows of tapered rollers on the inner side PC D i
  • the inner wall 27 on the inner side 27 can be made thicker in accordance with the amount of expansion of the inner ring 27, and the inner ring 27 inner rolling surface 27a and outer diameter 6e By suppressing the generated hoop stress, the strength and durability of the inner ring 27 can be improved.
  • FIG. 10 is a longitudinal sectional view showing a tenth embodiment of the wheel bearing device according to the present invention. This embodiment is the same as the ninth embodiment (FIG. 9) described above. Specifically, only the configuration of the hub wheel is different, and other parts and parts having the same parts or functions having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 2 2, and the small-diameter step portion 1 3 b of the hub wheel 2 2.
  • an inner member 30 composed of an inner ring 27.
  • the inner ring 27 has its small-diameter end face 6d abutted against the shoulder 1 3c of the hub ring 2 2 in abutting condition and is press-fitted into the small-diameter step 1 3b via a predetermined shimoshiro. 1 It is fixed in the axial direction by c.
  • the pitch circle diameter PCD i of the inner side tapered roller 29 row is more than the pitch circle diameter PCD o of the outer side tapered roller 21 row. Is also set to a large diameter (PCD i> PCD o), and the roller diameter di of the inner side of the roller 29 is larger than the roller diameter di of the outer side of the tapered roller 21 of the outer side 21 ( di> do). Also, the inner side tapered roller 2 9 row roller length L i is set to be longer than the outer side tapered roller length 2 row roller length L o (L i> L o). Rollers 2 1 and 2 9 The number of rollers is set to be the same.
  • the basic dynamic load rating of the inner bearing row can be increased and the rigidity and life of the bearing can be improved while further reducing weight and compactness.
  • the inner ring 27 on the inner side 27 can be increased in thickness t corresponding to the amount of expansion of the pitch circle diameter PCD i in the 29-row tapered roller on the inner side, and the plasticity of the caulking portion 1 c can be increased. It is possible to improve the strength and durability of the hub wheel 2 2 and the inner ring 2 7 by suppressing the hoop stress generated on the inner raceway surface 2 7 a and the outer diameter 6 e of the inner ring 2 7 due to the deformation.
  • FIG. 11 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • This embodiment is basically different from the ninth embodiment (FIG. 9) described above except that the configuration of the hub wheel and the wheel bearing is partially different. Parts are denoted by the same reference numerals and detailed description thereof is omitted.
  • This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1 ′ and a wheel bearing 31 fixed to the hub wheel 1 ′.
  • the wheel bearing 31 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening while being abutted against the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′ is It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.
  • the wheel bearing 31 has a vehicle body mounting flange 4c integrally formed on the outer periphery, an outer member 4 having a plurality of outer rolling surfaces 4a and 4b formed on the inner periphery, and these on the outer periphery.
  • Two inner races 1 9 'and 27' formed with inner rolling surfaces 1 9a and 27a opposite to the double row outer rolling surfaces 4a and 4b, and both rolling surfaces 4a and 19 A plurality of tapered rollers 2 1 and 29 are provided between a and 4 b and 2 7 a so as to be freely rollable via cages 20 and 28.
  • the pitch circle diameter PCD i of 29 rows of tapered rollers on the inner side is larger than the pitch circle diameter PCDo of 21 rows of tapered rollers on the outer side.
  • PCD i> PCDo the roller diameter di of the inner side tapered roller 29 row is set to a larger diameter (di> do) than the roller diameter do of the outer side tapered roller 21 row .
  • the roller length L i of the inner side tapered roller 29 row is set to be longer than the roller length L o of the outer side tapered roller 21 row (L i> L o), and those tapered rollers
  • the number of rollers in the 21st and 29th rows is set to be the same.
  • the rigidity and life of the bearing can be improved while achieving light weight and compactness, and the inner diameter can be increased in accordance with the amount of expansion of the pitch circle diameter PCD i in the 29 rows of tapered rollers on the inner side.
  • the shaft diameter d2 of the small diameter step 1b 'on the side hub wheel 1' can be made larger (d 2> d 1), and the strength of the hub wheel 1 'can be improved. it can.
  • FIG. 12 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. This embodiment is basically the same as the first embodiment (FIG. 11) described above except that the configuration of the hub wheel is different. Parts and parts having the same function are denoted by the same reference numerals, and detailed description thereof is omitted.
  • This wheel bearing device is for a driven wheel referred to as a third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 13b' of the hub wheel 22 '. And an inner member 32 comprising an inner ring 27 ′.
  • the pitch circle diameter of 29 rows of tapered rollers on the inner side PCD i is the pitch circle diameter P of 21 rows of tapered rollers on the outer side.
  • the diameter is set larger than CD o (PCD i> PCDo)
  • the roller diameter di of the inner side tapered roller 29 row is larger than the roller diameter do of the outer side tapered roller 21 row (di> do ) Is set.
  • the roller length L i of the inner side tapered roller 29 row is set to be longer than the roller length L o of the outer side tapered roller 21 row (L i> L o).
  • 29 rows are set to have the same number of rollers.
  • the shaft diameter d2 of the stepped portion 13b ' can be formed to have a large diameter (d2> d1), and the strength and durability of the hub wheel 22' can be improved.
  • FIG. 13 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. Note that this embodiment is basically different from the ninth embodiment (FIG. 9) described above, except that the configuration of the tapered roller on one side is basically the same. Are denoted by the same reference numerals, and detailed description thereof is omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 33 fixed to the hub wheel 1.
  • the wheel bearing 33 is press-fitted into the small-diameter step portion 1b through a predetermined squeeze opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this way.
  • the wheel bearing 33 has a vehicle body mounting flange 4c integrally on the outer periphery and a plurality of inner periphery flanges.
  • An outer member 4 in which outer rolling surfaces 4 a and 4 b of the row are formed, and inner rolling surfaces 1 9 a and 34 a facing the outer rolling surfaces 4 a and 4 b of these double rows on the outer periphery are provided.
  • Double-row cones accommodated in a freely rolling manner via cages 20 and 35 between two inner rings 1 9 and 34 formed respectively, and both rolling surfaces 4 a and 19 a and 4 b and 34 a It has 21 and 36 rollers.
  • the inner ring 34 and the tapered roller 36 are made of high carbon chrome steel such as SUJ 2 and hardened in the range of 58 to 64 H RC to the core part by quenching.
  • the pitch circle diameter P CD i of 36 rows of tapered rollers on the inner side is larger than the pitch circle diameter PCD o of 21 rows of tapered rollers on the outer side (PCD i> PCDo)
  • the roller length L i of 36 rows of tapered rollers on the inner side is set to be longer than the roller length L o of 21 rows of tapered rollers on the outer side (L i> L o).
  • Z i is set to be larger than the number of rollers Z o on the outer side tapered roller 21 row (Z i> Z o).
  • the inner rings 19 and 34 are fitted together by making the inner diameters of the inner rings 19 and 34 the same.
  • Small diameter step 1 b can be formed into a straight shaft consisting of shaft diameter d 1, improving workability of hub wheel 1 and pitch circle diameter in 36 rows of tapered rollers on one inner side PC D i
  • the inner wall 34 on the inner side 34 can be increased in thickness t corresponding to the amount of expansion of the inner ring 34, and the inner ring 34 inner rolling surface 34a and outer diameter 6e By suppressing the generated hoop stress, the strength and durability of the inner ring 34 can be improved.
  • FIG. 14 is a longitudinal sectional view showing a 14th embodiment of a wheel bearing device according to the present invention.
  • this embodiment is basically the same as the above-described first and third embodiments (Fig. 13) except that the configuration of the hub wheel is different, and the same parts and parts having the same function or the same function. Reference numerals are assigned and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and the inner member is press-fitted into the outer member 4, the hub wheel 22, and the small-diameter step portion 13b of the hub wheel 22. And an inner member 37 composed of a ring 34.
  • the pitch circle diameter PCD i of the inner side tapered roller 36 row is derived from the pitch circle diameter P CDo of the outer side tapered roller 21 row. Is also set to a large diameter (P CD i> P CD o), and the inner side tapered roller roller 36 row length L i is longer than the outer side tapered roller 2 single row roller length L o. It is set (L i> Lo).
  • the wall thickness t of the inner ring 34 on the inner side can be increased.
  • FIG. 15 is a longitudinal sectional view showing a fifteenth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically the same as the above-mentioned first to third embodiments (Fig. 13) except that the configuration of the hub wheel and the wheel bearing is partially different, and has the same parts, the same parts, and the same functions. Parts and parts are denoted by the same reference numerals, and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the second generation.
  • 'And a wheel bearing 38 fixed to the hub wheel 1'.
  • the wheel bearing 38 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined shim opening while abutting against the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′ is It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.
  • the wheel bearing 38 has an outer member 4 having a body mounting flange 4c integrally formed on the outer periphery and a plurality of outer rolling surfaces 4a, 4b formed on the inner periphery, and these on the outer periphery.
  • Inner rolling surfaces 19a and 34a facing the double-row outer rolling surfaces 4a and 4b were formed, respectively, and were set thinner than the inner rings 19 and 34 of the first to third embodiments described above.
  • Two inner rings 1 9 'and 34' and a plurality of tapered rollers 2 1 accommodated in a rolling manner via cages 20 and 35 between both rolling surfaces 4a, 19a and 4b and 34a 2 1 36.
  • the pitch circle diameter PCD i of the inner side tapered roller 36 row is equal to the pitch circle diameter P CD o of the outer side tapered roller 21 row. Is also set to a large diameter (P CD i> P CD o), and the inner side tapered roller roller 36 row length L i is longer than the outer side tapered roller 2 single row roller length L o. It is set (L i> Lo).
  • the shaft diameter d2 of the small diameter step 1b 'at' can be made large (d 2> d 1 (Fig. 1 3)), and the strength of the hub wheel 1 'can be improved. it can.
  • FIG. 16 is a longitudinal sectional view showing a sixteenth embodiment of the wheel bearing device according to the present invention. This embodiment is the same as the above-described 15th embodiment (FIG. 15). Basically, only the configuration of the hub wheel is different, and other parts and parts having the same parts or functions having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 1 3 b' of the hub wheel 22 '. And an inner member 39 made of an inner ring 34 '.
  • the pitch circle diameter PC D i of 36 rows of tapered rollers on the inner side is larger than the pitch circle diameter PCD o of 21 rows of tapered rollers on the outer side (P CD i> PCDo )
  • the length L i of the 36-side tapered roller on the inner side is set longer than the roller length L o of the 21-side tapered roller on the outer side (L i> L o )
  • the number of rollers in 36 rows of tapered rollers Z i is set to be greater than the number of rollers Z in outer rows of tapered rollers 21 (Z i> Z o).
  • the weight and weight of the bearing can be further improved, and the rigidity and life of the bearing can be improved.
  • it corresponds to the expansion diameter of the pitch circle diameter PC D i in the 36 rows of inner cone cones.
  • the shaft diameter d2 of the small-diameter stepped portion 13b 'in the hub wheel 22' can be formed large, and the strength and durability of the hub wheel 22 'can be improved.
  • FIG. 17 is a longitudinal sectional view showing a seventeenth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described first to third embodiments (Fig. 13) except that the configuration of the wheel bearing is basically the same, and other parts and parts having the same parts or the same functions. The same reference numerals are assigned to and detailed descriptions thereof are omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 40 fixed to the hub wheel 1.
  • the wheel bearing 40 is press-fitted into the small-diameter step portion 1b through a predetermined squeeze opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is plastically deformed. Formed It is fixed in the axial direction by the caulking portion 1c.
  • the wheel bearing 40 has a vehicle body mounting flange 4c integrally formed on the outer periphery, an outer member 41 having a plurality of outer rolling surfaces 4a, 41a formed on the inner periphery, and these on the outer periphery.
  • Two inner races 1 9 and 42 formed with inner rolling surfaces 1 9 a and 42 a opposite to the outer rolling surfaces 4 a and 41 a in double rows, and both rolling surfaces 4 a and 19 A double row of conical rollers 21, 36 are accommodated between a and 41a, 42a via rolling cages 20, 43, respectively.
  • the inner ring 42 is made of high carbon chrome steel such as S U J 2 and hardened in the range of 58 to 64 H RC up to the core part by quenching.
  • the pitch circle diameter P CDo of 21 rows of outer side tapered rollers is larger than the pitch circle diameter PCD i of 36 rows of tapered rollers on the inner side (PCDo> PCD i)
  • the roller length L i of 36 rows of tapered rollers on the inner side is set to be longer than the roller length L o of 21 rows of tapered rollers on the outer side (L i> L o).
  • FIG. 18 is a longitudinal sectional view showing a eighteenth embodiment of the wheel bearing device according to the present invention. This embodiment is basically different from the 17th embodiment described above (Fig. 17) except that the configuration of the hub wheel is different, and other parts and parts having the same function or the same function are not used. The same reference numerals are assigned and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and includes an outer member 41, a hub wheel 22, and an inner ring press-fitted into the small-diameter step portion 13b of the hub wheel 22. And an inner member 44 made of 42.
  • the pitch circle diameter PCDo of the outer side tapered roller 21 row is larger than the pitch circle diameter PCDi of the inner side tapered roller roller 36 row, similarly to the embodiment described above.
  • the diameter (PCDo> PCD i) is set, and the roller length L i of the inner side tapered roller row 36 is set to be longer than the roller length L o of the outer side tapered roller row 21 (L i> L o).
  • the roller number Z o in the 21-side tapered roller is set to be larger than the roller number Z i in the 36-side tapered roller 36 on the inner side (Z o> Z i).
  • FIG. 19 is a longitudinal sectional view showing a nineteenth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described first to third embodiments (Fig. 13) except that the configuration of the hub wheel is different, and other parts or parts having the same function or the same function are used. The same reference numerals are assigned and detailed description is omitted.
  • This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 33 ′ fixed to the hub wheel 45.
  • the hub wheel 45 integrally has a wheel mounting flange 3 at one end portion on the outer side, and a cylindrical small-diameter stepped portion 1 b extending in the axial direction from the wheel mounting flange 3 via a shoulder portion 1 a is formed on the outer periphery.
  • a torque transmission selection (or spline) 45 a is formed on the inner periphery.
  • the wheel bearing 33 ' is press-fitted into the small-diameter stepped portion 1b through a predetermined squeeze opening in a state where it abuts against the shoulder portion 1a of the hub wheel 45.
  • the hub wheel 45 is made of medium and high carbon steel containing 0.44 to 0.8 Ow t% of carbon such as S 53 C, and is hardened by induction hardening from the shoulder 1a to the small diameter step 1b. Hardened to a range of 58-64 H RC.
  • the wheel bearing 33 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and formed with double-row outer rolling surfaces 4a, 4b on the inner periphery, and on the outer periphery.
  • Two inner rings 1 9 and 34 formed with inner rolling surfaces 1 9 a and 34 a opposite to these double-row outer rolling surfaces 4 a and 4 b, and both rolling surfaces 4 a and 19 Double row tapered rollers 2 1 and 36 rows are provided between a and 4 b and 34 a so as to be freely rollable via cages 20 and 35 ′.
  • the pitch circle diameter P CD i of the inner side tapered roller 36 row is larger than the pitch circle diameter PCD o of the outer side tapered roller 21 row (PCD i> PCDo).
  • the roller length L i of 36 rows of tapered rollers on the inner side is set to be longer than the roller length L o of 21 rows of tapered rollers on the outer side (L i> L o).
  • the basic load rating of the inner side bearing row is increased while reducing the strength of the cage 35 'due to the increase in the roller diameter di and the number of rollers Z i, while reducing the weight and making it compact. It is possible to provide a wheel bearing device in which the rigidity and life of the bearing are improved.
  • FIG. 20 is a longitudinal sectional view showing a twentieth embodiment of the wheel bearing device according to the invention. This embodiment is different from the above-mentioned 15th embodiment (Fig. 15) except that the number of tapered rollers on the inner side is different, and other parts or parts having the same function or function are the same. The same reference numerals are assigned and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1 'and a wheel bearing 38' fixed to the hub wheel 1 '.
  • the pitch circle diameter PC D i of the inner side tapered roller 36 row is larger than the pitch circle diameter PCD o of the outer side tapered roller 21 row (P CD i> PCDo ) And a 36-row saw roller on the inner side.
  • the filter length L i is set to be longer than the roller length L o of one row of outer tapered rollers 2 (L i> L o).
  • FIG. 21 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. This embodiment is different from the above-mentioned 16th embodiment (Fig. 16) except that the number of tapered rollers on the inner side is different, and other parts or parts having the same function or function are the same. The same reference numerals are assigned and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 13b' of the hub wheel 22 '. And an inner member 39 ′ composed of an inner ring 34 ′.
  • the pitch circle diameter PCD i of the inner side tapered roller 36 row is larger than the pitch circle diameter P CD o of the outer side tapered roller 2 row (P CD i> P CD o), and the length L i of the inner side tapered roller 36 row is set to be longer than the length L o of the outer side tapered roller 21 row (L i> Lo).
  • FIG. 22 is a longitudinal sectional view showing a twenty-second embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described fifth embodiment (Fig. 5) only in the configuration of the hub wheel and the wheel bearing, except that the same parts are the same or have the same functions. Are denoted by the same reference numerals, and detailed description is omitted.
  • This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 46 fixed to the hub wheel 45.
  • the wheel bearing 46 is integrally formed with an outer member 47 having a body mounting flange 4 c on the outer periphery and a plurality of outer rolling surfaces 4 a and 47 a on the inner periphery, and these double rows on the outer periphery.
  • Two inner rings 1 9, 48, and both rolling surfaces 4 a, 19 a and 4 b , 48 a are provided with double row tapered rollers 21, 10 rows accommodated so as to roll freely through cages 20, 49.
  • the outer member 47 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the double-row outer rolling surfaces 4 a and 47 a are represented by induction hardening. Hardened to a surface hardness of 58 to 64 H RC.
  • the inner ring 48 is made of high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 H RC up to the core part by quenching.
  • the roller diameter di of the inner one side tapered roller 10 is set to be larger than the roller diameter do of the outer side tapered roller 21 row (di> do).
  • the basic rated load of the inner-side bearing row can be increased without increasing the pitch circle diameter PCD i of the inner row-side tapered roller 10 row. It is possible to provide a wheel bearing device that can increase the weight, suppress the outer diameter increase of the outer member 47, reduce the weight, and improve the rigidity and life of the bearing while achieving compactness. .
  • FIG. 23 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention.
  • This embodiment is basically the same as the above-described second embodiment (FIG. 2 2) except that the configuration of the wheel bearing is partially different, and other parts having the same parts or the same functions.
  • the same reference numerals are assigned to and detailed descriptions thereof are omitted.
  • This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 50 fixed to the hub wheel 45.
  • the wheel bearing 50 includes an outer member 4 7 having a body mounting flange 4 c integrally formed on the outer periphery and double row outer rolling surfaces 4 a and 4 7 a formed on the inner periphery, and these on the outer periphery.
  • Two inner rings 1 9 and 5 1 formed with inner rolling surfaces 1 9 a and 5 1 a opposite to the outer rolling surfaces 4 a and 4 7 a of the double row, and both rolling surfaces 4 a and 1 9 a and 4 7 a, 5 1 a are provided with double-row tapered rollers 2 1, 2 9 rows that are rotatably accommodated via cages 20, 5 2.
  • the inner rolling surface 5 1 a of the inner ring 5 1 is formed in a taper shape that makes line contact with the tapered roller 2 9, and the small diameter side (front) end face 5 d of the two inner rings 1 9, 5 1 6 d is a back-to-back type double row tapered roller bearing that is abutted in a butted state.
  • the inner ring 51 is made of high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 HRC up to the core part by quenching.
  • the roller diameter di of the inner side tapered roller 29 is set larger than the roller diameter do of the outer side roller 21 (di> do).
  • the roller length L i in the inner row of the inner row 29 is set longer than the roller length L o in the row of the tapered roller 21 in the outer row (L i> L o).
  • this makes it possible to further increase the basic load rating of the inner bearing row without increasing the pitch circle diameter PCD i of 29 inner tapered rollers. It is possible to improve the rigidity and life of the bearing while suppressing the increase in the outer diameter of the side member 47 and making it lighter and more compact.
  • FIG. 24 is a longitudinal sectional view showing a twenty-fourth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the 22nd embodiment described above (Fig. 22) except that the configuration of the wheel bearing is partially different, and other parts and parts having the same parts or the same functions. Are denoted by the same reference numerals, and detailed description thereof is omitted.
  • This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 53 fixed to the hub wheel 45.
  • the wheel bearing 53 includes an outer member 47 having a body mounting flange 4c integrally formed on the outer periphery, and formed with double-row outer rolling surfaces 4a and 47a on the inner periphery, and these double-rows on the outer periphery.
  • Outer raceway surfaces 4 a, 47 a Inner raceway surfaces 5 a, 48 a facing each other 5 a, 48 a formed between the two inner races 5, 48, and both raceways 4 a, 5 a and 47 a, 48 a
  • the pitch circle diameter P C D o of the nine rows of the outer side tapered rollers is the same as the pitch circle diameter P C D i of the ten rows of the inner side tapered rollers (P CD
  • the inner roller roller diameter di is set larger than the roller diameter do of the outer roller roller 9 row (di> do) Yes.
  • the inner side And the tapered roller diameters on the outer and outer rows 10 and 9 can increase the basic load rating of the double row bearing row without increasing the PCD i and PCDo, and prevent the outer member 47 from increasing in outer diameter. And light weight ⁇ The rigidity and life of the bearing can be improved while achieving compactness.
  • FIG. 25 is a longitudinal sectional view showing a 25th embodiment of the wheel bearing device according to the present invention.
  • This embodiment basically differs from the above-described twenty-second embodiment (Fig. 22) only in the configuration of the hub wheel, and the same reference numerals are given to other parts and parts having the same parts or the same functions. Detailed description will be omitted.
  • This wheel bearing device is for a drive wheel referred to as the third generation, and includes an outer member 47, a hub wheel 54, and an inner ring press-fitted into the small-diameter step portion 1 3 b of the hub wheel 54.
  • An inner member 55 consisting of 48 is provided.
  • the hub wheel 54 has a wheel mounting flange 3 integrally at the outer end of the outer ring, and has an outer side inner rolling surface 22 a on the outer periphery and a cylindrical shape extending in the axial direction from the inner rolling surface 22 a.
  • a small diameter step portion 1 3 b is formed.
  • the inner ring 48 has a small-diameter end face 6d abutting against the shoulder part 13c of the hub wheel 54 in abutting condition, and is press-fitted into the small-diameter step part 13b through a predetermined shim. It is fixed in the axial direction by c.
  • the hub wheel 54 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the inner surface of the rolling ring 2 2 a from the seal land 3 b in which the seal 15 is in sliding contact.
  • the surface hardness of the small diameter step portion 1 3 b is hardened by induction hardening to a range of 58 to 64 H RC.
  • the outer diameter up of the outer member 47 can be suppressed, and the rigidity and life of the bearing can be improved while further reducing the size and weight.
  • FIG. 26 is a longitudinal sectional view showing a 26th embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described 24th embodiment (Fig. 24) except that the configuration of the hub wheel and the bearing for the wheel is different. Parts are denoted by the same reference numerals and detailed description thereof is omitted.
  • This wheel bearing device is for a drive wheel called second generation, and includes a hub wheel 56 and a wheel bearing 57 fixed to the hub wheel 56.
  • the hub wheel 56 has a wheel mounting flange 3 integrally at one end on the outer side, and a cylindrical small diameter step 1 b extending in the axial direction from the wheel mounting flange 3 to the outer periphery via a shoulder 1 a.
  • a torque transmission selection (or spline) 45 a is formed on the inner periphery.
  • the hub ring 56 is formed of medium and high carbon steel containing carbon 0.40 to 0.8 O wt%, such as S53C, and is surfaced by induction hardening from the shoulder 1a to the small diameter step 1b. Hardness is hardened in the range of 58-64 HRC.
  • the wheel bearing 5 7 is press-fitted into the small-diameter step portion 1b through a predetermined squeeze opening while being in contact with the shoulder portion 1a of the hub wheel 56, and the end of the small-diameter step portion 1b. It is fixed in the axial direction by a caulking part 1 c formed by plastic deformation of the part.
  • This wheel bearing 5 7 has an outer member 4 7 integrally formed with a vehicle body mounting flange 4 c on the outer periphery and formed with double-row outer rolling surfaces 4 a and 4 7 a on the inner periphery, and on the outer periphery.
  • Inner rolling surfaces 5 8 a and 4 8 a facing the outer rolling surfaces 4 a and 4 7 a of these double rows are formed, respectively.
  • the inner ring 58 and the tapered roller 60 are made of high carbon chrome steel such as SUJ 2 and hardened in the range of 58 to 64 H RC up to the core part by quenching.
  • the roller length L o of the outer side tapered roller 60 row is set to be longer than the roller length L i of the inner side tapered roller 10 row (L o> L i).
  • This increases the basic load rating of the outer bearing row without increasing the pitch circle diameter PCDo of the outer side tapered roller 60 row and without increasing the number of rollers Zo of the tapered roller 60 row. Therefore, it is possible to provide a wheel bearing device that suppresses an increase in the outer diameter of the outer member 47 and is light and compact while improving the rigidity and life of the bearing.
  • FIG. 27 is a longitudinal sectional view showing a twenty-seventh embodiment of the wheel bearing device according to the invention. Note that this embodiment is basically different from the above-described 26th embodiment (Fig. 26) only in the configuration of the hub wheel, and other parts and parts having the same parts or parts having the same functions are designated by the same reference numerals. The detailed description is omitted.
  • This wheel bearing device is for a driven wheel referred to as a second generation, and includes a hub wheel 1 'and a wheel bearing 57 fixed to the hub wheel 1'.
  • the wheel bearing 57 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening in contact with the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′ is Plastic deformation It is fixed in the axial direction by a caulking portion 1 c formed by the above.
  • the roller length L o of the outer side tapered roller 60 row is set to be longer than the roller length L i of the inner side tapered roller 10 row (L o> L i).
  • FIG. 28 is a longitudinal sectional view showing a twenty-eighth embodiment of the wheel bearing device according to the invention. Note that this embodiment is basically different from the above-described twenty-sixth embodiment (Fig. 26) except that the configuration of the hub wheel is basically the same, and other parts and parts having the same parts or the same functions are denoted by the same reference numerals. Detailed description will be omitted.
  • This wheel bearing device is for a drive wheel referred to as the third generation, and includes an outer member 47, a hub wheel 61, and an inner ring press-fitted into the small-diameter step portion 1 3 b of the hub wheel 61.
  • An inner member 62 consisting of 48 is provided.
  • the hub wheel 61 integrally has a wheel mounting flange 3 at the outer end thereof, and has an outer inner rolling surface 61 a on the outer periphery and a cylindrical shape extending in the axial direction from the inner rolling surface 61 a.
  • a small diameter step portion 1 3 b is formed.
  • the hub wheel 61 is made of medium and high carbon steel containing 0.44 to 0.80 wt% of carbon such as S 53 C, and the seal land portion 3 b in sliding contact with the seal 1 5 to the inner rolling surface 6 1 a
  • the surface hardness of the small diameter step portion 1 3 b is hardened by induction hardening to a range of 58 to 64 H RC.
  • the basic load rating of the bearing row on the one side of the counter can be increased, and the outer diameter of the outer member 47 can be suppressed to increase the weight and the rigidity and life of the bearing can be improved while achieving compactness.
  • Fig. 29 is a longitudinal sectional view showing a twenty-ninth embodiment of the wheel bearing device according to the present invention. This embodiment is basically different from the 28th embodiment (FIG. 28) described above except that the configuration of the hub wheel is different, and other parts having the same parts or the same functions are denoted by the same reference numerals. Detailed description is omitted.
  • This wheel bearing device is for a driven wheel referred to as a third generation, and includes an outer member 47, a hub wheel 63, and an inner ring press-fitted into the small-diameter step portion 1 3 b of the hub wheel 63.
  • An inner member 64 consisting of 48 is provided.
  • the hub wheel 63 integrally has a wheel mounting flange 3 at the outer end portion, and has an outer inner rolling surface 61a on the outer periphery and a small diameter extending in the axial direction from the inner rolling surface 61a.
  • a stepped portion 1 3 b is formed.
  • This hub ring 63 is formed of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and from the seal land portion 3 b in which the seal 15 is in sliding contact to the inner rolling surface 6 1 a and The surface hardness is hardened to 58 to 64 H RC by induction hardening over the small diameter step 1 3 b.
  • the strength and rigidity of the hub wheel 63 are increased, and the outer diameter of the tapered roller 60 rows of the 60 rows is increased without increasing the pitch diameter PCDo and without increasing the number of rollers Z o of the tapered roller 60.
  • the basic load rating of the bearing row on one side can be increased, and the outer diameter of the outer member 47 can be prevented from increasing and the rigidity and life of the bearing can be improved while achieving light weight and compactness.
  • Fig. 30 is a longitudinal sectional view showing a thirtieth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the 28th embodiment (Fig. 28) described above, except that the structure of the wheel is only partially different, and other parts having the same parts, the same parts, or the same functions. Parts are denoted by the same reference numerals and detailed description is omitted.
  • This wheel bearing device is for a drive wheel called a third generation, and includes an inner member 64 comprising a hub wheel 63 and an inner ring 48 press-fitted and fixed to the hub wheel 63. And an outer member 47 inserted on the inner member 64.
  • the hub wheel 63 integrally has a wheel mounting flange 3 at one end portion on the outer side, and has a taper-shaped inner rolling surface 63a on the outer side on the outer periphery, and the inner rolling surface 63a.
  • a cylindrical small diameter step portion 13 b extending in the axial direction via the shoulder portion 13 c is formed, and a torque transmission selection (or spline) 45 a is formed on the inner periphery.
  • the hub wheel 63 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the base 3 b on the inner side of the wheel mounting flange 3 to the inner rolling surface 63 a and the shoulder. Inductive firing over small diameter step 1 3 b through part 1 3 c The surface hardness is set in the range of 58 to 64 H RC by putting.
  • the outer member 47 has a vehicle body mounting flange 4c integrally on its outer periphery, and an outer rolling surface 4a on the one side of the hub wheel 63 facing the inner rolling surface 63a of the hub wheel 63 on the inner periphery, An inner side outer raceway surface 47a facing the inner raceway surface 48a of the inner ring 48 is integrally formed. Then, double rows of tapered rollers 66, 10 are accommodated in a freely rolling manner via cages 65, 49 between both rolling surfaces.
  • the tapered roller 66 is made of high carbon chrome steel such as S U J 2 and hardened to the core by a quenching process in the range of 58 to 64 H RC.
  • the outer side tapered roller 66 row roller diameter do is set smaller than the inner roller roller diameter di (do ⁇ di), and the inner side tapered roller
  • the roller length L i of the 10th row is set longer than the roller length L o of the outer side tapered roller 66 row (L i> L o).
  • the number of rollers Zo in the outer side tapered roller 66 row is set to be larger than the number of rollers Zi in the inner row of tapered roller 10 row (Zo> Zi).
  • FIG. 31 is a longitudinal sectional view showing a thirty-first embodiment of the wheel bearing device according to the present invention.
  • This embodiment is for a driven wheel and basically differs from the 30th embodiment (FIG. 30) described above except that the configuration of the hub wheel is different, and other parts and parts having the same parts or the same functions.
  • the same reference numerals are assigned to the same and detailed description thereof is omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 'and a wheel bearing 67 fixed to the hub wheel 1'.
  • the bearing 67 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening while being abutted against the shoulder portion 1 a of the hub wheel 1 ′, and the end of the small-diameter step portion 1 b ′ is plastically deformed It is fixed in the axial direction by the caulking portion 1 c formed in advance.
  • the wheel bearing 67 is composed of an outer member 47 and two inner rings 6 each formed with an inner rolling surface 68a, 48a opposite to the outer circumferential surface 4a, 47a of the double row on the outer circumference. 8, 48, and double-row tapered rollers 66, 10 which are rotatably accommodated via cages 65, 49 between both rolling surfaces 4a, 68a and 47a, 48a.
  • the inner rolling surface 68a of the inner ring 68 on the outer side is formed in a taper shape that makes a line contact with the tapered roller 66. Then, a back-to-back type double-row tapered roller bearing in which the small-diameter side (front) end faces 5 d and 6 d of the pair of inner rings 68 and 48 are abutted in a butted state is configured.
  • the inner diameter of the inner ring 68 is set to be the same as the inner diameter of the inner ring 48 on the inner side.
  • the small-diameter stepped portion 1 b ′ can be integrally processed in a uniform shape, and the number of processing steps can be simplified and the cost can be reduced.
  • the inner ring 68 is formed of a high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 HRC to the core portion by quenching, like the inner ring 48 on the inner side.
  • the roller diameter dough of the outer roller row 66 is smaller than the roller diameter di of the 10 row tapered roller di ( do ⁇ di)
  • the roller length L i of the inner one side roller is set to be longer than the roller length L o of the outer side tapered roller row 66 (L i> L o )
  • the outer roller side tapered roller 66 row roller count Z o Tapered roller on the side 10 Rollers in row 0 are accommodated more than Z i (Z o> Z i).
  • the wheel bearing device according to the present invention can be applied to a wheel bearing device of a second or third generation structure regardless of whether it is for a driving wheel or a driven wheel.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • FIG. 2 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention.
  • FIG. 3 is a longitudinal sectional view showing a third embodiment of a wheel bearing device according to the present invention.
  • FIG. 4 is a longitudinal sectional view showing a fourth embodiment of a wheel bearing device according to the present invention.
  • FIG. 5 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing device according to the invention.
  • FIG. 6 is a longitudinal sectional view showing a sixth embodiment of the wheel bearing device according to the invention.
  • FIG. 7 is a longitudinal sectional view showing a seventh embodiment of the wheel bearing device according to the invention.
  • FIG. 8 is a longitudinal sectional view showing an eighth embodiment of the wheel bearing device according to the invention.
  • FIG. 9 is a longitudinal sectional view showing a ninth embodiment of the wheel bearing device according to the invention.
  • FIG. 10 is a longitudinal sectional view showing a tenth embodiment of the wheel bearing device according to the present invention.
  • FIG. 11 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • FIG. 12 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • FIG. 13 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention ⁇ ::.
  • FIG. 14 is a longitudinal sectional view showing a fourteenth embodiment of the wheel bearing device according to the present invention ⁇ ::.
  • FIG. 15 is a longitudinal sectional view showing the fifteenth embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 16 is a longitudinal sectional view showing the sixteenth embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 17 is a longitudinal sectional view showing the seventeenth embodiment of the present invention I :: wheel bearing device according to the present invention.
  • FIG. 18 is a longitudinal sectional view showing the eighteenth embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 19 is a longitudinal sectional view showing the nineteenth embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 20 is a longitudinal sectional view showing the 20th embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 21 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 22 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 23 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 24 is a longitudinal sectional view showing a 24th embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 25 is a longitudinal sectional view showing a 25th embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 26 is a longitudinal sectional view showing a 26th embodiment of the wheel bearing device according to the present invention I :.
  • FIG. 27 is a longitudinal sectional view showing a twenty-seventh embodiment of a wheel bearing device according to the invention.
  • FIG. 28 is a longitudinal sectional view showing a twenty-eighth embodiment of the wheel bearing device according to the invention.
  • FIG. 29 is a longitudinal sectional view showing a twenty-ninth embodiment of the wheel bearing device according to the present invention.
  • FIG. 30 is a longitudinal sectional view showing a thirtieth embodiment of the wheel bearing device according to the invention.
  • FIG. 31 is a longitudinal sectional view showing a 31st embodiment of a wheel bearing device according to the present invention.
  • FIG. 32 is a longitudinal sectional view showing a conventional wheel bearing device.
  • FIG. 33 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, in which contradictory problems of reduction in weight and size and increase in rigidity are solved at the same time and which has increased strength and durability. [MEANS FOR SOLVING PROBLEMS] The bearing device for a wheel has double-row (9, 10) tapered rollers, and in the bearing device, an inner ring (6) is fixed by subjecting an end of a small-diameter step section (13b) of a hub ring (13) to rocking die swaging. The pitch circle diameter PCDi of the tapered-roller row (10) on the inner side is set greater than the pitch circle diameter PCDo of the tapered-roller row (9) on the outer side. Further, the number of the tapered rollers in the double rows is set to be the same, the diameter di of the tapered rollers (10) on the inner side is set greater than the diameter do of the tapered rollers (9) on the outer side, and the length Lo of the tapered rollers (9) on the outer side is set more than the length Li of the tapered rollers (10) on the inner side. The construction increases the rigidity and life of the bearing and enables effective use of a bearing space to make the bearing device light-weight and compact.

Description

明 細 書  Specification
車輪用軸受装置  Wheel bearing device
技術分野  Technical field
[0001 ] 本発明は、 自動車等の車輪を回転自在に支承する車輪用軸受装置、 特に、 軽量化と高剛性化を図った車輪用軸受装置に関するものである。  TECHNICAL FIELD [0001] The present invention relates to a wheel bearing device that rotatably supports a wheel of an automobile or the like, and more particularly to a wheel bearing device that is reduced in weight and increased in rigidity.
背景技術  Background art
[0002] 従来から自動車等の車輪を支持する車輪用軸受装置は、 車輪を取り付ける ためのハブ輪を転がり軸受を介して回転自在に支承するもので、 駆動輪用と 従動輪用とがある。 構造上の理由から、 駆動輪用では内輪回転方式が、 従動 輪用では内輪回転と外輪回転の両方式が一般的に採用されている。 この車輪 用軸受装置には、 所望の軸受剛性を有し、 ミスァライメントに対しても耐久 性を発揮すると共に、 燃費向上の観点から回転トルクが小さい複列アンギュ ラ玉軸受が多用されている。 一方、 オフロード力一やトラック等、 車体重量 が嵩む車両には複列円錐ころ軸受が使用されている。  [0002] Conventionally, wheel bearing devices for supporting wheels of automobiles and the like support a hub wheel for mounting a wheel rotatably via a rolling bearing, and there are a drive wheel and a driven wheel. For structural reasons, the inner ring rotation method is generally used for driving wheels, and both the inner ring rotation method and outer ring rotation method are used for driven wheels. In this wheel bearing device, a double-row angular contact ball bearing that has a desired bearing rigidity, exhibits durability against misalignment, and has a low rotational torque from the viewpoint of improving fuel efficiency is often used. . On the other hand, double row tapered roller bearings are used in vehicles with heavy vehicle body weight such as off-road force and trucks.
[0003] また、 車輪用軸受装置には、 懸架装置を構成するナックルとハブ輪との間 に複列アンギユラ玉軸受等からなる車輪用軸受を嵌合させた第 1世代と称さ れる構造から、 外方部材の外周に直接車体取付フランジまたは車輪取付フラ ンジが形成された第 2世代構造、 また、 ハブ輪の外周に一方の内側転走面が 直接形成された第 3世代構造、 あるいは、 ハブ輪と等速自在継手の外側継手 部材の外周にそれぞれ内側転走面が直接形成された第 4世代構造とに大別さ れている。  [0003] In addition, the wheel bearing device has a structure called a first generation in which a wheel bearing composed of a double-row anguilla ball bearing or the like is fitted between a knuckle and a hub wheel constituting a suspension device. Second generation structure with body mounting flange or wheel mounting flange formed directly on the outer periphery of the outer member, or third generation structure with one inner raceway formed directly on the outer periphery of the hub wheel, or hub It is roughly divided into the 4th generation structure in which the inner rolling surface is directly formed on the outer circumference of the outer joint member of the wheel and constant velocity universal joint.
[0004] 図 3 2に示す車輪用軸受装置は、 軽量■ コンパク ト化を図った第 4世代構 造で、 ハブ輪 1 0 0と複列の転がり軸受 1 0 1および等速自在継手 1 0 2と がュニット化して構成されている。 複列の転がり軸受 1 0 1は、 外方部材 1 0 3と内方部材 1 0 4と、 両部材間に収容された複数のポール 1 0 5および 円錐ころ 1 0 6とを備えている。 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) 、 中央寄り側をィ ンナー側 (図面右側) という。 [0004] The wheel bearing device shown in Fig. 3 2 is a lightweight, compact, 4th generation structure with a hub wheel 1 0 0 and double row rolling bearing 1 0 1 and constant velocity universal joint 1 0 2 and are united. The double row rolling bearing 100 includes an outer member 10 3, an inner member 10 4, and a plurality of poles 10 5 and tapered rollers 10 6 accommodated between the two members. In the following description, the side closer to the outer side of the vehicle in the assembled state is the outer side (left side of the drawing), and the side closer to the center is It is called the inner side (right side of the drawing).
[0005] 外方部材 1 0 3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 1 0 3 cを一体に有し、 内周に複列の外側転走 面 1 0 3 a、 1 0 3 bが形成されている。 ここで、 アウター側の外側転走面 1 0 3 aの直径は、 ィンナ一側の外側転走面 1 0 3 bの直径よりも小径に設 定されている。 一方、 内方部材 1 0 4は、 ハブ輪 1 0 0と、 このハブ輪 1 0 0と一体に構成された後述する外側継手部材 1 0 8と、 この外側継手部材 1 0 8に圧入された別体の内輪 1 0 7とを有している。  [0005] The outer member 10 3 integrally has a vehicle body mounting flange 10 3 c attached to a knuckle constituting a suspension device (not shown) on the outer periphery, and a double row outer rolling surface 10 on the inner periphery. 3 a and 1 0 3 b are formed. Here, the diameter of the outer rolling surface 10 3 a on the outer side is set to be smaller than the diameter of the outer rolling surface 10 3 b on the inner side. On the other hand, the inner member 10 04 is press-fitted into the hub wheel 100, an outer joint member 10 8, which will be described later, integrally formed with the hub wheel 100, and the outer joint member 10 8. And a separate inner ring 1 0 7.
[0006] ハブ輪 1 0 0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 1 O O bを一体に有し、 外周に複列の外側転走面 1 0 3 a、 1 0 3 bのうちァウタ一側の外側転走面 1 0 3 aに対向する内側転走面 1 0 0 aが 直接形成されると共に、 内輪 1 0 7の外周には複列の外側転走面 1 0 3 a、 1 0 3 bのうちインナ一側の外側転走面 1 0 3 bに対向する内側転走面 1 0 7 aが形成されている。  [0006] The hub wheel 1 0 0 has a wheel mounting flange 1 OO b for mounting a wheel (not shown) at one end, and a double row outer rolling surface 1 0 3 a, 1 on the outer periphery. 0 3 b Outer rolling surface on one side of outer side 1 0 3 a Inner rolling surface facing 1 0 3 a is directly formed, and the outer ring of inner ring 1 0 7 has double row outer rolling surface An inner rolling surface 1 0 7 a facing the outer rolling surface 1 0 3 b on the inner side of 1 0 3 a and 1 0 3 b is formed.
[0007] 等速自在継手 1 0 2は、 カップ状のマウス部 1 0 9と、 このマウス部 1 0 9の底部をなす肩部 1 1 0とからなる外側継手部材 1 0 8を有し、 この外側 継手部材 1 0 8の内周には曲線状のトラック溝 1 0 8 aが形成されている。 内輪 1 0 7はマウス部 1 0 9の外径に圧入され、 止め輪 1 1 1によって軸方 向に固定されている。  [0007] The constant velocity universal joint 1 0 2 has an outer joint member 1 0 8 composed of a cup-shaped mouth portion 1 0 9 and a shoulder portion 1 1 0 which forms the bottom of the mouth portion 1 0 9, A curved track groove 10 8 a is formed on the inner periphery of the outer joint member 10 8. The inner ring 10 07 is press-fitted into the outer diameter of the mouse portion 10 9 and is fixed in the axial direction by a retaining ring 1 1 1.
[0008] 外方部材 1 0 3と内方部材 1 0 4のァウタ一側の転走面 1 0 3 a、 1 0 0 a間には複数のポール 1 0 5が、 ィンナ一側の転走面 1 0 3 b、 1 0 7 a間 には複数の円錐ころ 1 0 6がそれぞれ転動自在に収容され、 これらポール 1 0 5列および円錐ころ 1 0 6列のうちァウタ一側のポール 1 0 5列のピッチ 円直径は、 インナ一側の円錐ころ 1 0 6列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、 アウター側の軸受列部分に比べ大きな荷重が加わ るインナ一側の軸受列部分の基本定格荷重を、 アウター側の軸受列部分の基 本定格荷重よりも大きくして、 これら両軸受列部分の寿命をほぼ同じにする ことができ、 無駄のない設計を可能にすることができる (例えば、 特許文献 1参照。 ) 。 [0008] A rolling surface on the outer side of the outer member 1 0 3 and the inner member 1 0 4 on the outer side 1 0 3 a, a plurality of poles 1 0 5 between the 1 0 0 a and rolling on the inner side A plurality of tapered rollers 1 0 6 are rotatably accommodated between the faces 1 0 3 b and 1 0 7 a, respectively, and the pole 1 on the outer side of the rows 1 0 5 and 1 0 6 The pitch circle diameter of the fifth row is set smaller than the pitch circle diameter of the inner row of tapered rollers. As a result, the basic rated load of the inner-side bearing row portion to which a larger load is applied than the outer-side bearing row portion is made larger than the basic rated load of the outer-side bearing row portion, and both of these bearing rows are The life of the parts can be made almost the same, and a design without waste can be made possible (for example, patent literature) See 1. )
[0009] 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 1 0 8の マウス部 1 0 9に内輪 1 0 7が固定される構造のため、 軸方向には確かにコ ンパク ト化されるが、 外方部材 1 0 3の外径自体が大きくなり、 軽量化を阻 害するだけでなく、 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 3 3に示すような車輪用 軸受装置が知られている。  However, in such a wheel bearing device, since the inner ring 1 0 7 is fixed to the mouse portion 1 0 9 of the outer joint member 1 0 8, it is certainly compact in the axial direction. However, not only does the outer diameter of the outer member 10 3 itself increase, which not only obstructs weight reduction but also changes in the design of peripheral parts such as knuckles. As a solution to these problems, a wheel bearing device as shown in Fig. 33 is known.
[0010] この車輪用軸受装置は、 外周にナックル (図示せず) に取り付けられるた めの車体取付フランジ 1 1 2 cを一体に有し、 内周に複列の外側転走面 1 1 2 a、 1 1 2 bが形成された外方部材 1 1 2と、 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 1 1 3を一体に有し、 外周に複列の外 側転走面 1 1 2 a、 1 1 2 bのうちアウター側の外側転走面 1 1 2 aに対向 する内側転走面 1 1 4 aと、 この内側転走面 1 1 4 aから軸方向に延びる小 径段部 1 1 4 bが形成されたハブ輪 1 1 4、 およびこのハブ輪 1 1 4の小径 段部 1 1 4 bに外嵌され、 複列の外側転走面 1 1 2 a、 1 1 2 bのうちイン ナ一側の外側転走面 1 1 2 bに対向する内側転走面 1 1 5 aが形成された内 輪 1 1 5からなる内方部材 1 1 6と、 これら両転走面間に収容された複列の ポール 1 1 7、 1 1 8と、 これら複列のポール 1 1 7、 1 1 8を転動自在に 保持する保持器 1 1 9、 1 2 0とを備えた複列アンギユラ玉軸受で構成され ている。  [0010] This wheel bearing device has a vehicle body mounting flange 1 1 2 c integrally attached to a knuckle (not shown) on the outer periphery, and a double row outer rolling surface 1 1 2 on the inner periphery. a, 1 1 2 b formed outer member 1 1 2 and wheel mounting flange 1 1 3 for mounting a wheel (not shown) at one end, and double row outside on the outer circumference Rolling surface 1 1 2 a, 1 1 2 b Outer rolling surface 1 1 2 b Inner rolling surface facing 1 1 2 a 1 1 4 a and axial direction from this inner rolling surface 1 1 4 a The hub wheel 1 1 4 formed with a small-diameter step 1 1 4 b extending to the outer ring 1 and the small-diameter step 1 1 4 b of this hub wheel 1 1 4 a, 1 1 2 b Outer rolling surface on one side of inner side 1 1 2 b Inner rolling surface facing 1 1 2 b 1 1 5 Inner member 1 1 6 formed of inner ring 1 1 5 A double row of poles 1 1 7 and 1 1 8 accommodated between these rolling surfaces, These double-row poles 1 1 7 and 1 1 8 are constituted by double-row anguillar ball bearings equipped with cages 1 1 9 and 1 2 0 which hold the rolls freely.
[001 1 ] 内輪 1 1 5は、 ハブ輪 1 1 4の小径段部 1 1 4 bを径方向外方に塑性変形 させて形成した加締部 1 1 4 cによって軸方向に固定されている。 そして、 外方部材 1 1 2と内方部材 1 1 6との間に形成される環状空間の開口部にシ —ル 1 2 1、 1 2 2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、 外部から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。  [001 1] The inner ring 1 1 5 is fixed in the axial direction by a caulking portion 1 1 4 c formed by plastically deforming the small diameter step portion 1 1 4 b of the hub wheel 1 1 4 radially outward. . The seal 1 2 1 and 1 2 2 are installed in the opening of the annular space formed between the outer member 1 1 2 and the inner member 1 1 6, and the lubricating grease sealed inside the bearing And prevents rainwater and dust from entering the bearings from the outside.
[0012] ここで、 ァウタ一側のポール 1 1 7列のピッチ円直径 D 1が、 ィンナ一側 のポール 1 1 8列のピッチ円直径 D 2よりも大径に設定されている。 これに 伴い、 ハブ輪 1 1 4の内側転走面 1 1 4 aが内輪 1 1 5の内側転走面 1 1 5 aよりも拡径され、 あわせて外方部材 1 1 2のアウター側の外側転走面 1 1 2 aがインナ一側の外側転走面 1 1 2 bよりも拡径されている。 そして、 ァ ウタ一側のポール 1 1 7がインナ一側のポール 1 1 8よりも多数収容されて いる。 このように、 各ピッチ円直径 D 1、 D 2を D 1 > D 2に設定すること により、 車両の静止時だけでなく旋回時においても剛性が向上し、 車輪用軸 受装置の長寿命化を図ることができる (例えば、 特許文献 2参照。 ) 。 特許文献 1 :特開平 1 1—9 1 3 0 8号公報 [0012] Here, the pitch circle diameter D1 of the pole 1 17 row on the one side of the counter is set larger than the pitch circle diameter D2 of the pole 1 1 8 row on the inner side. Along with this, the inner raceway 1 1 4 a of the hub wheel 1 1 4 is the inner raceway 1 1 5 of the inner race 1 1 5 The outer side rolling surface 1 1 2 a on the outer side of the outer member 1 1 2 has a larger diameter than the outer rolling surface 1 1 2 b on the inner side. And more poles 1 1 7 on the outer side are accommodated than poles 1 1 8 on the inner side. In this way, by setting each pitch circle diameter D1, D2 to D1> D2, the rigidity is improved not only when the vehicle is stationary but also when turning, and the service life of the wheel bearing device is extended. (For example, see Patent Document 2). Patent Document 1: Japanese Patent Laid-Open No. 1-9-9 30 8
特許文献 2:特開 2 0 0 4 _ 1 0 8 4 4 9号公報  Patent Document 2: Japanese Patent Laid-Open No. 2 0 0 4 _ 1 0 8 4 4 9
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
[0013] こうした従来の車輪用軸受装置では、 アウター側のポール 1 1 7列のピッ チ円直径 D 1がィンナ一側のポール 1 1 8列のピッチ円直径 D 2よりも大径 に設定され、 これに伴い、 ハブ輪 1 1 4の内側転走面 1 1 4 aが内輪 1 1 5 の内側転走面 1 1 5 aよりも拡径されている。 これにより装置の大型化を避 けつつアウター側の軸受列の剛性が向上し、 車輪用軸受装置の長寿命化を図 ることができる。 然しながら、 インナ _側■アウター側の各軸受列に加わる 荷重は互いに異なり、 アウター側の軸受列に加わる荷重よりも、 インナー側 の軸受列に加わる荷重の方が大きくなるのが一般的である。 こうした場合、 この従来の車輪用軸受装置では、 インナ一側の軸受列の基本定格荷重が、 ァ ウタ一側の軸受列の基本定格荷重よりも小さくなって短寿命になる。  In such a conventional wheel bearing device, the pitch circle diameter D 1 of the outer pole 1 117 row is set larger than the pitch circle diameter D 2 of the inner pole 1 1 8 row. Accordingly, the inner raceway surface 1 1 4 a of the hub wheel 1 1 4 has a larger diameter than the inner raceway surface 1 1 5 a of the inner race 1 1 5. As a result, the rigidity of the outer bearing row can be improved while avoiding an increase in the size of the device, and the service life of the wheel bearing device can be extended. However, the loads applied to the inner and outer bearing rows are different from each other, and the load applied to the inner bearing row is generally larger than the load applied to the outer bearing row. In such a case, in this conventional wheel bearing device, the basic load rating of the inner side bearing row is smaller than the basic load rating of the outer side bearing row, resulting in a shorter life.
[0014] 本発明は、 このような事情に鑑みてなされたもので、 装置の軽量■ コンパ ク ト化と高剛性化という相反する課題を同時に解決すると共に、 強度 "耐久 性を向上させた車輪用軸受装置を提供することを目的としている。  [0014] The present invention has been made in view of such circumstances, and simultaneously solves the conflicting problems of light weight and compactness and high rigidity of the device, and at the same time, has improved strength and durability. An object of the present invention is to provide a bearing device for a vehicle.
課題を解決するための手段  Means for solving the problem
[0015] 係る目的を達成すべく、 本発明は、 外周にナックルに取り付けられるため の車体取付フランジを一体に有し、 内周に複列の外側転走面が形成された外 方部材と、 一端部に車輪を取り付けるための車輪取付フランジを一体に有し 、 外周に小径段部が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入 され、 外周に前記複列の外側転走面に対向する内側転走面が形成された少な くとも一つの内輪からなる内方部材と、 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円錐ころ列とを備えた車輪用軸受装置 において、 前記複列の円錐ころ列のうちインナ一側の円錐ころ列のピッチ円 直径がアウター側の円錐ころ列のピッチ円直径よりも大径に設定され、 さら に、 前記インナ一側の円錐ころ列のころ径が前記ァウタ一側の円錐ころ列の ころ径よりも大径に設定されると共に、 前記アウター側の円錐ころ列のころ 長さが前記インナ一側の円錐ころ列のころ長さよりも長く設定されている。 ■ ■ ■請求項 1 [0015] In order to achieve the object, the present invention includes an outer member integrally having a vehicle body mounting flange to be attached to a knuckle on the outer periphery, and a double row outer rolling surface formed on the inner periphery. A hub wheel having a wheel mounting flange for mounting a wheel on one end and a small diameter step portion formed on the outer periphery, and press fitting into the small diameter step portion of this hub ring An inner member comprising at least one inner ring formed on the outer periphery with an inner rolling surface facing the double row outer rolling surface, and both rolling surfaces of the inner member and the outer member. A wheel bearing device having a double row tapered roller row accommodated in a freely rolling manner between the pitch roller diameters of the inner side conical roller row of the double row conical roller row and having a conical shape on the outer side. The roller diameter is set to be larger than the pitch circle diameter of the roller row, and further, the roller diameter of the inner side tapered roller row is set to be larger than the roller diameter of the outer side tapered roller row, The roller length of the outer side tapered roller row is set to be longer than the roller length of the inner side tapered roller row. ■ ■ ■ Claim 1
[001 6] このように、 複列の円錐ころ列を備えた第 2または第 3世代構造の車輪用 軸受装置において、 複列の円錐ころ列のうちインナ一側の円錐ころ列のピッ チ円直径がァゥタ一側の円錐ころ列のピッチ円直径よりも大径に設定され、 さらに、 ィンナ一側の円錐ころ列のころ径がァウタ一側の円錐ころ列のころ 径よりも大径に設定されると共に、 アウター側の円錐ころ列のころ長さがィ ンナ一側の円錐ころ列のころ長さよりも長く設定されているので、 軸受の剛 性と寿命を向上させることができると共に、 軸受スペースを有効に活用して 軽量 . コンパク ト化を図ることができる。 したがって、 装置の軽量■ コンパ ク ト化と高剛性化という相反する課題を同時に解決すると共に、 強度 "耐久 性を向上させた車輪用軸受装置を提供することができる。  [001 6] As described above, in the second or third generation wheel bearing device having double row tapered roller rows, the pitch circle of the tapered roller row on the inner side of the double row tapered roller row is provided. The diameter is set larger than the pitch circle diameter of the tapered roller row on the outer side, and the roller diameter of the tapered roller row on the inner side is set larger than the roller diameter of the tapered roller row on the outer side. In addition, the roller length of the outer tapered roller train is set to be longer than the roller length of the inner tapered roller train, so that the rigidity and life of the bearing can be improved, and the bearing The space can be used effectively to make it lighter and more compact. Therefore, it is possible to provide a wheel bearing device that can simultaneously solve the conflicting problems of light weight and compactness and high rigidity of the device, and that has improved strength and durability.
[001 7] また、 本発明は、 外周にナックルに取り付けられるための車体取付フラン ジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 一端部 に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に小径段部 が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外周に前記 複列の外側転走面に対向する内側転走面が形成された少なくとも一つの内輪 からなる内方部材と、 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円錐ころ列とを備えた車輪用軸受装置において、 前記複 列の円錐ころ列のうちインナ一側の円錐ころ列のピッチ円直径がアウター側 の円錐ころ列のピッチ円直径よりも大径に設定されると共に、 前記インナ一 側の円錐ころ列のころ径が前記アウター側の円錐ころ列のころ径ょりも大径 に設定されている。 ■ ■ ■請求項 2 [001 7] The present invention also includes an outer member integrally having a vehicle body mounting flange to be attached to a knuckle on the outer periphery, and a double-row outer rolling surface formed on the inner periphery; A hub wheel that has a wheel mounting flange for mounting the wheel and has a small-diameter step formed on the outer periphery, and is press-fitted into the small-diameter step portion of the hub wheel, and faces the outer surface of the double row on the outer periphery. An inner member formed of at least one inner ring formed with an inner raceway, and a double row conical roller row accommodated between the inner member and the outer member so as to roll freely. The pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row, The inner The roller diameter of the tapered roller row on the side is set to a large diameter as well. ■ ■ ■ Claim 2
[0018] このように、 複列の円錐ころ列を備えた第 2または第 3世代構造の車輪用 軸受装置において、 複列の円錐ころ列のうちインナ一側の円錐ころ列のピッ チ円直径がアウター側の円錐ころ列のピッチ円直径よりも大径に設定される と共に、 インナ一側の円錐ころ列のころ径がアウター側の円錐ころ列のころ 径よりも大径に設定されているので、 軸受の剛性と寿命を向上させることが できると共に、 軸受スペースを有効に活用して軽量■ コンパク ト化を図るこ とができる。 したがって、 装置の軽量■ コンパク ト化と高剛性化という相反 する課題を同時に解決すると共に、 強度■耐久性を向上させた車輪用軸受装 置を提供することができる。  [0018] Thus, in the wheel bearing device of the second or third generation structure provided with the double row tapered roller row, the pitch circle diameter of the tapered roller row on the inner side of the double row tapered roller row is provided. Is set to be larger than the pitch circle diameter of the outer tapered roller train, and the roller diameter of the inner tapered roller train is set to be larger than the roller diameter of the outer tapered roller train. As a result, the rigidity and life of the bearing can be improved, and the bearing space can be effectively utilized to achieve light weight and compactness. Therefore, it is possible to provide a wheel bearing device that can simultaneously solve the conflicting problems of light weight and compactness and high rigidity of the device, and that has improved strength and durability.
[001 9] また、 発明のように、 前記インナ一側の円錐ころ列のころ長さが前記ァゥ タ一側の円錐ころ列のころ長さよりも長く設定されていれば、 ィンナ一側の 軸受列の基本動定格荷重が増大して軸受の剛性と寿命をさらに向上させるこ とができる。 ■ ■ ■請求項 3  [001 9] Further, as in the invention, if the roller length of the inner side tapered roller train is set longer than the roller length of the outer side tapered roller train, The basic dynamic load rating of the bearing row can be increased, further improving the rigidity and life of the bearing. ■ ■ ■ Claim 3
[0020] また、 本発明のように、 前記複列の円錐ころ列のころ個数が同一に設定さ れていても良い。 ■ ■ ■請求項 4  [0020] Further, as in the present invention, the number of rollers of the double row tapered roller row may be set to be the same. ■ ■ ■ Claim 4
[0021 ] また、 本発明は、 外周にナックルに取り付けられるための車体取付フラン ジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 一端部 に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に小径段部 が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外周に前記 複列の外側転走面に対向する内側転走面が形成された少なくとも一つの内輪 からなる内方部材と、 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円錐ころ列とを備えた車輪用軸受装置において、 前記複 列の円錐ころ列のうちインナ一側の円錐ころ列のピッチ円直径がアウター側 の円錐ころ列のピッチ円直径よりも大径に設定されると共に、 前記インナ一 側の円錐ころ列のころ長さが前記アウター側の円錐ころ列のころ長さよりも 長く設定され、 力、つ、 前記インナ一側の円錐ころ列のころ個数が前記ァウタ —側の円錐ころ列のころ個数よりも多く設定されている。 ■ ■ ■請求項 5 [0022] このように、 複列の円錐ころ列を備えた第 2または第 3世代構造の車輪用 軸受装置において、 複列の円錐ころ列のうちインナ一側の円錐ころ列のピッ チ円直径がアウター側の円錐ころ列のピッチ円直径よりも大径に設定される と共に、 インナ一側の円錐ころ列のころ長さがアウター側の円錐ころ列のこ ろ長さよりも長く設定され、 かつ、 インナ一側の円錐ころ列のころ個数がァ ウタ一側の円錐ころ列のころ個数よりも多く設定されているので、 装置の軽 量■ コンパク ト化と高剛性化という相反する課題を同時に解決すると共に、 インナ一側の軸受列の基本定格荷重が高くなり軸受の剛性と寿命を向上させ た車輪用軸受装置を提供することができる。 [0021] The present invention also includes an outer member integrally including a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end. A hub wheel having a wheel mounting flange for mounting the outer ring, and a small-diameter step portion formed on the outer periphery, and a small-diameter step portion of the hub wheel, and press-fitted into the outer periphery of the double row on the outer periphery. An inner member composed of at least one inner ring formed with an inner rolling surface, and a double row tapered roller row accommodated so as to roll between the inner member and both rolling surfaces of the outer member. In the wheel bearing device provided, the pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row, and The roller length of the inner side tapered roller row is the outer It is set to be longer than the roller length of the tapered roller rows of the force, one, number rollers of the tapered roller rows of the inner one side the Auta -More than the number of rollers in the tapered roller row on the side. ■ ■ ■ Claim 5 [0022] Thus, in the second or third generation wheel bearing device having double row tapered roller rows, the inner side tapered roller of the double row tapered roller rows. The pitch circle diameter of the row is set to be larger than the pitch circle diameter of the outer side tapered roller row, and the roller length of the inner side tapered roller row is larger than the length of the outer side tapered roller row. The number of rollers in the tapered roller train on the inner side is set to be larger than the number of rollers in the tapered roller row on the outer side, so the weight of the device is compact and the rigidity is increased. Thus, it is possible to provide a wheel bearing device in which the basic rated load of the bearing row on the inner side is increased and the rigidity and life of the bearing are improved.
[0023] また、 本発明は、 外周にナックルに取り付けられるための車体取付フラン ジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 一端部 に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に小径段部 が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外周に前記 複列の外側転走面に対向する内側転走面が形成された少なくとも一つの内輪 からなる内方部材と、 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円錐ころ列とを備えた車輪用軸受装置において、 前記複 列の円錐ころ列のうちアウター側の円錐ころ列のピッチ円直径がィンナ一側 の円錐ころ列のピッチ円直径よりも大径に設定されると共に、 前記インナ一 側の円錐ころ列のころ長さが前記アウター側の円錐ころ列のころ長さよりも 長く設定され、 力、つ、 前記アウター側の円錐ころ列のころ個数が前記インナ —側の円錐ころ列のころ個数よりも多く設定されている。 ■ ■ ■請求項 6 [0024] このように、 複列の円錐ころ列を備えた第 2または第 3世代構造の車輪用 軸受装置において、 複列の円錐ころ列のうちアウター側の円錐ころ列のピッ チ円直径がインナ一側の円錐ころ列のピッチ円直径よりも大径に設定される と共に、 インナ一側の円錐ころ列のころ長さがアウター側の円錐ころ列のこ ろ長さよりも長く設定され、 かつ、 アウター側の円錐ころ列のころ個数がィ ンナ一側の円錐ころ列のころ個数よりも多く設定されているので、 軽量 - コ ンパク ト化を図ると共に、 インナ一側の軸受列の基本定格荷重が高くなり、 外方部材の外径をアツプすることなく軸受の剛性と寿命を向上させた車輪用 軸受装置を提供することができる。 [0023] The present invention also includes an outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end. A hub wheel having a wheel mounting flange for mounting the outer ring, and a small-diameter step portion formed on the outer periphery, and a small-diameter step portion of the hub wheel, and press-fitted into the outer periphery of the double row on the outer periphery. An inner member composed of at least one inner ring formed with an inner rolling surface, and a double row tapered roller row accommodated so as to roll between the inner member and both rolling surfaces of the outer member. In the wheel bearing device provided, a pitch circle diameter of an outer side tapered roller row of the double row tapered roller rows is set larger than a pitch circle diameter of an inner side tapered roller row, and The roller length of the inner side tapered roller row is the outer Is set to be longer than the roller length of the tapered roller rows of the force, one, number rollers of the tapered roller rows of the outer side the inner - is set larger than the number roller on the side of the tapered roller rows. ■ ■ ■ Claim 6 [0024] In this way, in the second or third generation wheel bearing device having double-row tapered roller rows, the outer-side tapered roller row of the double-row tapered roller rows. The pitch circle diameter of the inner roller is set to be larger than the pitch circle diameter of the inner side tapered roller train, and the roller length of the inner side tapered roller train is larger than the length of the outer tapered roller train. Is set longer and the number of rollers in the outer tapered roller row is set to be larger than the number of rollers in the inner tapered roller row. It is possible to provide a wheel bearing device that improves the rigidity and life of the bearing without increasing the outer diameter of the outer member, and the basic rated load of the bearing row on the inner side is increased. it can.
[0025] また、 本発明のように、 前記インナ一側の円錐ころ列のころ径と前記ァゥ ター側の円錐ころ列のころ径が同一に設定されていても良い。 ■ ■ ■請求項  [0025] Further, as in the present invention, a roller diameter of the inner side tapered roller train and a roller diameter of the outer tapered roller train may be set to be the same. ■ ■ ■ Claims
[0026] また、 本発明は、 外周にナックルに取り付けられるための車体取付フラン ジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 一端部 に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に小径段部 が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外周に前記 複列の外側転走面に対向する内側転走面が形成された少なくとも一つの内輪 からなる内方部材と、 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円錐ころ列とを備えた車輪用軸受装置において、 前記複 列の円錐ころ列のうちインナ一側の円錐ころ列のピッチ円直径がアウター側 の円錐ころ列のピッチ円直径よりも大径に設定されると共に、 前記インナ一 側の円錐ころ列のころ長さが前記アウター側の円錐ころ列のころ長さよりも 長く設定され、 かつ、 これらの円錐ころのころ径ぉよびころ個数が同一に設 定されている。 ■ ■ ■請求項 8 [0026] Further, according to the present invention, an outer member having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end A hub wheel having a wheel mounting flange for mounting the outer ring, and a small-diameter step portion formed on the outer periphery, and a small-diameter step portion of the hub wheel, and press-fitted into the outer periphery of the double row on the outer periphery. An inner member composed of at least one inner ring formed with an inner rolling surface, and a double row tapered roller row accommodated so as to roll between the inner member and both rolling surfaces of the outer member. In the wheel bearing device provided, the pitch circle diameter of the inner side tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row, and The roller length of the inner side tapered roller row is the outer It is set to be longer than the roller length of the tapered roller row of and the number roller diameter Oyobi rollers of these tapered rollers is set to the same. ■ ■ ■ Claim 8
[0027] このように、 複列の円錐ころ列を備えた第 2または第 3世代構造の車輪用 軸受装置において、 複列の円錐ころ列のうちインナ一側の円錐ころ列のピッ チ円直径がアウター側の円錐ころ列のピッチ円直径よりも大径に設定される と共に、 インナ一側の円錐ころ列のころ長さがアウター側の円錐ころ列のこ ろ長さよりも長く設定され、 かつ、 これらの円錐ころのころ径ぉよびころ個 数が同一に設定されているので、 軽量 ' コンパク ト化を図ると共に、 ころ径 およびころ個数の増加による保持器の強度ダウンを防止しつつインナ一側の 軸受列の基本定格荷重が増大され、 軸受の剛性と寿命を向上させた車輪用軸 受装置を提供することができる。  [0027] Thus, in the wheel bearing device of the second or third generation structure provided with the double row tapered roller row, the pitch circle diameter of the tapered roller row on the inner side of the double row tapered roller row is provided. Is set to be larger than the pitch circle diameter of the outer side tapered roller row, the roller length of the inner side tapered roller row is set to be longer than the outer length of the tapered roller row of the outer side, and Since these tapered rollers have the same roller diameter and the same number of rollers, they can be made lighter and more compact, and the inner diameter can be reduced while preventing the cage strength from being reduced by increasing the roller diameter and number of rollers. It is possible to provide a wheel bearing device in which the basic load rating of the side bearing row is increased and the rigidity and life of the bearing are improved.
[0028] また、 本発明は、 外周にナックルに取り付けられるための車体取付フラン ジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 一端部 に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に小径段部 が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外周に前記 複列の外側転走面に対向する内側転走面が形成された少なくとも一つの内輪 からなる内方部材と、 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円錐ころ列とを備えた車輪用軸受装置において、 前記複 列の円錐ころ列のピッチ円直径が同一に設定されると共に、 前記複列の円錐 ころ列のうちインナ一側の円錐ころ列のころ径がアウター側の円錐ころ列の ころ径よりも大径に設定され、 かつ、 これらの円錐ころ列のころ個数が同一 に設定されている。 ■ ■ ■請求項 9 [0028] Further, the present invention provides a vehicle body mounting flange for mounting to a knuckle on the outer periphery. The outer member with a double row outer raceway formed on the inner periphery and the wheel mounting flange for mounting the wheel on one end are integrated, and the small diameter step is formed on the outer periphery. And an inner member comprising at least one inner ring that is press-fitted into a small-diameter step portion of the hub ring and has an inner rolling surface facing the outer rolling surface of the double row on the outer periphery. In a wheel bearing device including an inner member and a double-row tapered roller row rotatably accommodated between both rolling surfaces of the outer member, a pitch circle diameter of the double-row tapered roller row is The roller diameter of the inner side tapered roller row of the double row tapered roller rows is set to be larger than the roller diameter of the outer side tapered roller row, and these tapered rollers The number of rollers in the row is set to be the same. ■ ■ ■ Claim 9
[0029] このように、 複列の円錐ころ列を備えた第 2または第 3世代構造の車輪用 軸受装置において、 複列の円錐ころ列のピッチ円直径が同一に設定されると 共に、 複列の円錐ころ列のうちインナ一側の円錐ころ列のころ径がアウター 側の円錐ころ列のころ径よりも大径に設定され、 かつ、 これらの円錐ころ列 のころ個数が同一に設定されているので、 インナ一側の円錐ころ列のピッチ 円直径を大きくすることなくィンナー側の軸受列の基本定格荷重を高くする ことができ、 外方部材の外径アップを抑制し、 軽量■ コンパク ト化を図りつ つ軸受の剛性と寿命を向上させた車輪用軸受装置を提供することができる。  [0029] Thus, in the second or third generation wheel bearing device having double row tapered roller rows, the pitch circle diameters of the double row tapered roller rows are set to be the same, and The roller diameter of the tapered roller row on the inner side of the row of tapered roller rows is set larger than the roller diameter of the tapered roller row on the outer side, and the number of rollers in these tapered roller rows is set to be the same. Therefore, it is possible to increase the basic rated load of the inner side bearing row without increasing the pitch circle diameter of the inner one side, and to prevent the outer member from increasing its outer diameter. Thus, it is possible to provide a wheel bearing device in which the rigidity and life of the bearing are improved.
[0030] 好ましくは、 発明のように、 前記インナ一側の円錐ころ列のころ長さが前 記アウター側の円錐ころ列のころ長さよりも長く設定されていれば、 インナ 一側の円錐ころ列のピッチ円直径を大きくすることなくィンナー側の軸受列 の基本定格荷重をさらに高くすることができ、 外方部材の外径ァップを抑制 し、 軽量 ' コンパク ト化を図りつつ軸受の剛性と寿命を向上させることがで きる。 ■ ■ ■請求項 1 0  [0030] Preferably, as in the invention, if the roller length of the inner side tapered roller row is set to be longer than the roller length of the outer side tapered roller row, the inner one side tapered roller It is possible to further increase the basic load rating of the inner side bearing row without increasing the pitch circle diameter of the row, to suppress the outer diameter of the outer member, and to reduce the outer diameter of the outer member, while reducing the weight and reducing the rigidity of the bearing. The service life can be improved. ■ ■ ■ Claim 1 0
[0031 ] また、 本発明のように、 前記アウター側の円錐ころ列のころ長さが前記ィ ンナー側の円錐ころ列のころ長さよりも長く設定されていれば、 複列の円錐 ころ列のピツチ円直径を大きくすることなく複列の軸受列の基本定格荷重を 高くすることができ、 外方部材の外径アップを抑制し、 軽量■ コンパク ト化 を図りつつ軸受の剛性と寿命を向上させることができる。 ■ ■ ■請求項 1 1 [0032] また、 本発明は、 外周にナックルに取り付けられるための車体取付フラン ジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 一端部 に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に小径段部 が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外周に前記 複列の外側転走面に対向する内側転走面が形成された少なくとも一つの内輪 からなる内方部材と、 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円錐ころ列とを備えた車輪用軸受装置において、 前記複 列の円錐ころ列のピッチ円直径が同一に設定されると共に、 前記複列の円錐 ころ列のうちアウター側の円錐ころ列のころ長さがインナ一側の円錐ころ列 のころ長さよりも長く設定され、 かつ、 これらの円錐ころ列のころ個数が同 —に設定されている。 ■ ■ ■請求項 1 2 [0031] Further, as in the present invention, if the roller length of the outer tapered roller train is set longer than the roller length of the inner tapered roller train, The basic load rating of double row bearing rows can be increased without increasing the diameter of the pitch circle, and the outer diameter of the outer member can be prevented from increasing, making it light and compact. Thus, the rigidity and life of the bearing can be improved. ■ ■ ■ Claim 1 1 [0032] Further, the present invention has a vehicle body mounting flange integrally attached to a knuckle on the outer periphery, and an outer side in which a double row outer rolling surface is formed on the inner periphery. And a hub wheel having a wheel mounting flange for mounting a wheel at one end, a small-diameter step portion formed on the outer periphery, and press-fitted into the small-diameter step portion of the hub wheel. An inner member composed of at least one inner ring formed with an inner rolling surface opposite to the outer rolling surface, and a composite member housed in a freely rolling manner between the inner and the outer member. In the wheel bearing device provided with a row of tapered roller rows, the pitch circle diameter of the double row tapered roller rows is set to be the same, and the outer side tapered roller row of the double row tapered roller rows is arranged. Set the roller length longer than the roller length of the tapered roller row on the inner side. It is, and the number rollers of these tapered rollers column same - is set to. ■ ■ ■ Claim 1 2
[0033] このように、 複列の円錐ころ列を備えた第 2または第 3世代構造の車輪用 軸受装置において、 複列の円錐ころ列のピッチ円直径が同一に設定されると 共に、 複列の円錐ころ列のうちアウター側の円錐ころ列のころ長さがインナ —側の円錐ころ列のころ長さよりも長く設定され、 かつ、 これらの円錐ころ 列のころ個数が同一に設定されているので、 アウター側の円錐ころ列のピッ チ円直径を大きくすることなく、 また、 その円錐ころのころ個数を増やすこ となくアウター側の軸受列の基本定格荷重を高くすることができ、 軽量 - コ ンパク ト化を図りつつ軸受の剛性と寿命を向上させた車輪用軸受装置を提供 することができる。 [0033] Thus, in the second or third generation wheel bearing device having a double row tapered roller row, the pitch circle diameter of the double row tapered roller row is set to be the same, and The roller length of the outer tapered roller row in the row is set to be longer than the roller length of the inner tapered roller row, and the number of rollers in these tapered roller rows is set to be the same. Therefore, the basic load rating of the outer side bearing row can be increased without increasing the pitch circle diameter of the outer side tapered roller row and without increasing the number of rollers of the tapered roller. -It is possible to provide a wheel bearing device in which the rigidity and life of the bearing are improved while achieving compactness.
[0034] また、 本発明のように、 前記アウター側の円錐ころ列のころ径と前記イン ナ一側の円錐ころ列のころ径が同一に設定されていれば、 外方部材のァウタ 一側の外径アップを抑制することができる。 ■ ■ ■請求項 1 3  [0034] Further, as in the present invention, if the roller diameter of the outer tapered roller row and the roller diameter of the inner tapered roller row are set to be the same, the outer side of the outer member An increase in the outer diameter can be suppressed. ■ ■ ■ Claim 1 3
[0035] また、 本発明は、 外周にナックルに取り付けられるための車体取付フラン ジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 一端部 に車輪を取り付けるための車輪取付フランジを一体に有し、 外周にこの車輪 取付フランジから軸方向に延びる小径段部が形成されたハブ輪、 およびこの / \ブ輪の小径段部に圧入され、 外周に前記複列の外側転走面に対向する内側 転走面が形成された少なくとも一つの内輪からなる内方部材と、 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円錐ころ列と を備えた車輪用軸受装置において、 前記複列の円錐ころ列のピッチ円直径が 同一に設定され、 前記複列の円錐ころ列のうちアウター側の円錐ころ列のこ ろ径がインナ一側の円錐ころ列のころ径よりも小径に設定されると共に、 前 記ァウタ一側の円錐ころ列のころ個数が前記ィンナー側の円錐ころ列のころ 個数よりも多く設定され、 かつ、 前記インナ一側の円錐ころ列のころ長さが 前記アウター側の円錐ころ列のころ長さよりも長く設定されている。 ■ ■ ■ ■請求項 1 4 [0035] The present invention also includes an outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel on one end. A hub wheel integrally having a wheel mounting flange for mounting, and having a small-diameter step portion extending in the axial direction from the wheel mounting flange on the outer periphery, and An inner member composed of at least one inner ring press-fitted into the small-diameter step portion of the ring and formed with an inner rolling surface facing the outer rolling surface of the double row on the outer circumference, and the inner member In the wheel bearing device comprising a double row tapered roller row that is rotatably accommodated between both rolling surfaces of the outer member, the pitch circle diameter of the double row tapered roller row is set to be the same. The diameter of the outer tapered roller row of the double row tapered roller rows is set to be smaller than the roller diameter of the inner side tapered roller row, and the outer roller side tapered roller row The number of rollers is set to be greater than the number of rollers in the inner side tapered roller row, and the roller length of the inner side tapered roller row is set to be longer than the roller length of the outer side tapered roller row. Yes. ■ ■ ■ ■ Claim 1 4
[0036] このように、 複列の円錐ころ列を備えた第 2または第 3世代構造の車輪用 軸受装置において、 複列の円錐ころ列のピッチ円直径が同一に設定され、 複 列の円錐ころ列のうちアウター側の円錐ころ列のころ径がインナ一側の円錐 ころ列のころ径よりも小径に設定されると共に、 アウター側の円錐ころ列の ころ個数がィンナ一側の円錐ころ列のころ個数よりも多く設定され、 かつ、 インナ一側の円錐ころ列のころ長さがアウター側の円錐ころ列のころ長さよ りも長く設定されているので、 アウター側の円錐ころ列のピッチ円直径を大 きくすることなく、 両軸受列の基本定格荷重を高くすることができ、 軽量 - コンパク ト化を図りつつ軸受の剛性と寿命を向上させた車輪用軸受装置を提 供することができる。  [0036] In this way, in the second or third generation wheel bearing device having double-row tapered roller rows, the pitch circle diameters of the double-row tapered roller rows are set to be the same, and the double-row cone rollers The roller diameter of the outer tapered roller train is set to be smaller than the roller diameter of the inner one, and the number of rollers in the outer tapered roller train is the inner one. Since the roller length of the inner tapered roller row is set to be longer than the roller length of the outer tapered roller row, the pitch of the outer tapered roller row is set. It is possible to increase the basic load rating of both bearing rows without increasing the diameter of the circle, and to provide a wheel bearing device that is lightweight and compact, while improving the rigidity and life of the bearing. .
[0037] また、 本発明のように、 前記小径段部の端部を径方向外方に塑性変形させ て形成した加締部により前記内輪が軸方向に固定されていれば、 軽量■ コン パク ト化を図ることができる。 ■ ■ ■請求項 1 5  [0037] Further, as in the present invention, if the inner ring is fixed in the axial direction by a caulking portion formed by plastically deforming the end portion of the small diameter step portion radially outward, Can be achieved. ■ ■ ■ Claim 1 5
[0038] また、 本発明のように、 前記ハブ輪の外周にアウター側の内側転走面が直 接形成されると共に、 この内側転走面から軸方向に延びる前記小径段部が形 成され、 この小径段部に所定のシメシ口を介して前記インナ一側の内輪が圧 入されていれば、 一層装置の軽量■ コンパク ト化ができると共に、 インナ一 側の円錐ころ列におけるピッチ円直径の拡径量に対応してィンナー側の内輪 の肉厚を厚くすることができ、 加締部の塑性変形に伴い内輪の内側転走面や 外径に発生するフープ応力を抑制してハブ輪および内輪の強度■耐久性を向 上させることができる。 ■ ■ ■請求項 1 6 [0038] Further, as in the present invention, an outer-side inner rolling surface is directly formed on the outer periphery of the hub wheel, and the small-diameter step portion extending in the axial direction from the inner-rolling surface is formed. If the inner ring on the inner side is press-fitted into the small diameter step portion through a predetermined opening, the device can be made lighter and more compact, and the pitch circle diameter in the tapered roller array on the inner side can be reduced. The inner ring on the inner side corresponding to the amount of diameter expansion The hoop stress generated on the inner raceway surface and the outer diameter of the inner ring due to plastic deformation of the caulking part can be suppressed to improve the strength of the hub ring and inner ring. Can do. ■ ■ ■ Claim 1 6
[0039] また、 本発明のように、 前記ハブ輪の小径段部に一対の内輪が圧入され、 これらの内輪の内径が同一に設定されていれば、 ハブ輪の小径段部をストレ -卜な形状に形成することができ、 加工性を向上させることができると共に 、 ィンナ一側の円錐ころ列におけるピッチ円直径の拡径量に対応してインナ 一側の内輪の肉厚を厚くすることができ、 加締部の塑性変形に伴い内輪の内 側転走面や外径に発生するフープ応力を抑制して内輪の強度■耐久性を向上 させることができる。 ■ ■ ■請求項 1 7 [0039] Further, as in the present invention, if a pair of inner rings are press-fitted into the small-diameter step portion of the hub wheel and the inner diameters of these inner rings are set to be the same, the small-diameter step portion of the hub wheel is It can be formed into any shape, and the workability can be improved, and the inner ring inner wall thickness can be increased corresponding to the amount of pitch circle diameter expansion in the inner roller taper row. It is possible to improve the strength and durability of the inner ring by suppressing the hoop stress generated on the inner raceway surface and outer diameter of the inner ring due to plastic deformation of the caulking portion. ■ ■ ■ Claim 1 7
発明を実施するための最良の形態  BEST MODE FOR CARRYING OUT THE INVENTION
[0040] 外周にナックルに取り付けられるための車体取付フランジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 一端部に車輪を取り付け るための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の一 方に対向する内側転走面と、 この内側転走面から軸方向に延びる小径段部が 形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外周に前記複 列の外側転走面の他方に対向する内側転走面が形成された内輪からなる内方 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 複列の円錐ころ列とを備え、 前記小径段部の端部を径方向外方に塑性変形さ せて形成した加締部により前記内輪がハブ輪に対して軸方向に固定された車 輪用軸受装置において、 前記複列の円錐ころ列のうちインナ一側の円錐ころ 列のピッチ円直径がアウター側の円錐ころ列のピッチ円直径よりも大径に設 定され、 さらに、 前記複列の円錐ころ列のころ個数が同一に設定され、 前記 ィンナー側の円錐ころ列のころ径が前記ァウタ一側の円錐ころ列のころ径ょ りも大径に設定されると共に、 前記アウター側の円錐ころ列のころ長さが前 記インナ一側の円錐ころ列のころ長さよりも長く設定されている。  [0040] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, a double row outer rolling surface formed on the inner periphery, and a wheel attachment for attaching the wheel to one end A hub wheel having a flange integrally formed and formed on the outer periphery thereof with an inner rolling surface facing one of the outer rolling surfaces of the double row, and a small-diameter step portion extending in an axial direction from the inner rolling surface; and An inner member comprising an inner ring that is press-fitted into a small-diameter step portion of the hub wheel and has an inner rolling surface facing the other of the outer rolling surfaces of the double row on the outer periphery; and the inner member and the outer A double row tapered roller row that is rotatably accommodated between both rolling surfaces of the member, and is formed by a caulking portion that is formed by plastically deforming an end portion of the small diameter step portion radially outward. In a bearing device for a wheel in which an inner ring is fixed in an axial direction with respect to a hub wheel, the double-row tapered roller The pitch circle diameter of the inner side tapered roller train is set to be larger than the pitch circle diameter of the outer tapered roller train, and the number of rollers of the double row tapered roller train is set to be the same. The roller diameter of the inner tapered roller train is set to be larger than the roller diameter of the outer tapered roller train, and the roller length of the outer tapered roller train is It is set longer than the roller length of the tapered roller row on the side.
実施例 1  Example 1
[0041 ] 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。 図 1は、 本発明に係る車輪用軸受装置の第 1の実施形態を示す縦断面図で この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 と、 このハブ輪 1に固定された車輪用軸受 2とを備えている。 ハブ輪 1は、 アウター側の一端部に車輪 (図示せず) を取り付けるための車輪取付フラン ジ 3を一体に有し、 この車輪取付フランジ 3から肩部 1 aを介して軸方向に 延びる小径段部 1 bが形成されている。 車輪取付フランジ 3にはハブポルト 3 aが周方向等配に植設されている。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1, A wheel bearing 2 fixed to the hub wheel 1 is provided. The hub wheel 1 integrally has a wheel mounting flange 3 for mounting a wheel (not shown) at one end portion on the outer side, and has a small diameter extending in an axial direction from the wheel mounting flange 3 through a shoulder portion 1a. A step 1b is formed. Hub ports 3 a are planted on the wheel mounting flange 3 at equal intervals in the circumferential direction.
[0042] 車輪用軸受 2は、 ハブ輪 1の肩部 1 aに衝合した状態で小径段部 1 bに所 定のシメシロを介して圧入されると共に、 小径段部 1 bの端部を塑性変形さ せて形成した加締部 1 cによって軸方向に固定されている。 ハブ輪 1は S 5 3 C等の炭素 0 . 4 0〜0 . 8 O w t %を含む中高炭素鋼で形成され、 肩部 1 aから小径段部 1 bに亙って高周波焼入れによって表面硬さを 5 8〜6 4 H R Cの範囲に硬化処理されている。 なお、 加締部 1 cは鍛造加工後の表面 硬さのままとされている。 これにより、 車輪取付フランジ 3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、 車輪用軸受 2の嵌合部となる 小径段部 1 bの耐フレツティング性が向上すると共に、 加締部 1 cの塑性加 ェを微小なクラック等の発生を防止してスムーズに行うことができる。  [0042] The wheel bearing 2 is press-fitted into the small-diameter step portion 1b through a predetermined shimiro while being in contact with the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation. The hub ring 1 is formed of medium and high carbon steel containing carbon 0.40 to 0.8 O wt% such as S 53 C, and is hardened by induction hardening from the shoulder 1a to the small diameter step 1b. Has been cured to a range of 5 8 to 6 4 HRC. Note that the caulking portion 1c remains the surface hardness after forging. This has sufficient mechanical strength against the rotational bending load applied to the wheel mounting flange 3, and improves the fretting resistance of the small-diameter stepped portion 1b that becomes the fitting portion of the wheel bearing 2. At the same time, the plastic application of the crimped portion 1c can be smoothly performed while preventing the occurrence of minute cracks and the like.
[0043] 車輪用軸受 2は、 外周に懸架装置を構成するナックル (図示せず) に取り 付けられるための車体取付フランジ 4 cを一体に有し、 内周に複列の外側転 走面 4 a、 4 bが形成された外方部材 4と、 外周にこれら複列の外側転走面 4 a、 4 bに対向する内側転走面 5 a、 6 aがそれぞれ形成された 2つの内 輪 5、 6と、 両転走面 4 a、 5 aおよび 4 b、 6 a間に保持器 7、 8を介し て転動自在に収容された複列の円錐ころ 9、 1 0列を備えている。 外方部材 4と 2つの内輪 5、 6との間に形成された環状空間の開口部にはシール 1 1 、 1 2が装着され、 軸受内部に封入されたグリースの外部への漏洩と、 外部 から雨水やダスト等が軸受内部に侵入するのを防止している。  [0043] The wheel bearing 2 is integrally provided with a vehicle body mounting flange 4c to be attached to a knuckle (not shown) constituting a suspension device on the outer periphery, and a double row outer rolling surface 4 on the inner periphery. Two outer rings with outer members 4 with a and 4 b and inner rolling surfaces 5 a and 6 a facing the outer circumferential surfaces 4 a and 4 b of the double row on the outer circumference. 5, 6 and double rolling tapered rollers 9, 10 which are accommodated in a rolling manner via cages 7, 8 between both rolling surfaces 4a, 5a and 4b, 6a. Yes. Seals 1 1 and 1 2 are attached to the opening of the annular space formed between the outer member 4 and the two inner rings 5 and 6, and leakage of grease sealed inside the bearing Prevents rainwater and dust from entering the bearing.
[0044] 内輪 5、 6の内側転走面 5 a、 6 aは、 円錐ころ 9、 1 0にラインコンタ ク トするテーパ状に形成され、 小径側 (正面) 端面 5 d、 6 dが突合せ状態 で衝合された、 所謂背面合せタイプの複列円錐ころ軸受を構成している。 そ して、 内側転走面 5 a、 6 aの大径側に円錐ころ 9、 1 0を案内するための 大鍔 5 b、 6 bと、 小径側に円錐ころ 9、 1 0の脱落を防止するための小鍔 5 c、 6 cがそれぞれ形成されている。 [0044] Inner raceway surfaces 5a and 6a of inner rings 5 and 6 are line contoured to tapered rollers 9 and 10 This is a so-called back-to-back type double-row tapered roller bearing that is formed in a tapered shape with a small diameter side (front) end face 5d and 6d abutting in a butted state. Then, the large rollers 5 b and 6 b for guiding the tapered rollers 9 and 10 to the large diameter side of the inner rolling surfaces 5 a and 6 a and the tapered rollers 9 and 10 to drop off on the small diameter side are provided. Gavels 5 c and 6 c are formed for prevention.
[0045] 外方部材 4は S 53 C等の炭素 0. 40〜0. 80w t %を含む中高炭素 鋼で形成され、 複列の外側転走面 4 a、 4 bが高周波焼入れによって表面硬 さを 58〜64 H RCの範囲に硬化処理されている。 また、 内輪 5、 6およ び円錐ころ 9、 1 0は S U J 2等の高炭素クロム鋼で形成され、 ズブ焼入れ によって芯部まで 58〜64 H RCの範囲に硬化処理されている。  [0045] The outer member 4 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the double row outer rolling surfaces 4 a and 4 b are hardened by induction hardening. Hardened to a range of 58-64 H RC. The inner rings 5 and 6 and the tapered rollers 9 and 10 are made of high carbon chrome steel such as SU 2 and hardened in the range of 58 to 64 H RC to the core part by quenching.
[0046] ここで、 本実施形態では、 インナ一側の円錐ころ 1 0列のピッチ円直径 P CD iがアウター側の円錐ころ 9列のピッチ円直径 PCD oよりも大径 (P CD i >PCDo) に設定されている。 また、 インナ一側の円錐ころ 1 0列 のころ径 d iがアウター側の円錐ころ 9列のころ径 d oよりも大径 (d i > d o) に設定されると共に、 ころ長さに関しては、 アウター側の円錐ころ 9 列のころ長さ L oがインナ一側の円錐ころ 1 0列のころ長さ L i よりも長く 設定されている ( L o > L i ) 。 なお、 それらの円錐ころ 9、 1 0列のころ 個数は同一になるように設定されている。 これにより、 軸受の剛性と寿命を 向上させることができると共に、 軸受スペースを有効に活用して軽量■ コン パク ト化を図った車輪用軸受装置を提供することができる。  Here, in the present embodiment, the pitch circle diameter P CD i of the inner row of tapered rollers 10 on the inner side is larger than the pitch circle diameter PCD o of the row of 9 tapered rollers on the outer side (P CD i> PCDo). In addition, the roller diameter di of the 10-row tapered roller on the inner side is set to a larger diameter (di> do) than the roller diameter do of the 9-side tapered roller on the outer side, and the roller length is The roller length L o of the 9-row tapered roller is set to be longer than the roller length L i of the 10-side tapered roller 10 (L o> L i). Note that the number of rollers in the tapered rollers 9 and 10 row is set to be the same. As a result, it is possible to improve the rigidity and life of the bearing, and to provide a wheel bearing device that is lightweight and compact by effectively utilizing the bearing space.
[0047] また、 設計自由度が増すため、 ピッチ円直径 PCDo、 PCD i に違いが あってもそれぞれの内輪 5、 6の内径を同一にすることにより、 内輪 5、 6 が嵌合する小径段部 1 bが軸径 d 1からなるストレー卜な軸状に形成でき、 ハブ輪 1の加工性を向上させることができると共に、 インナ一側の円錐ころ 1 0列におけるピッチ円直径 PC D iの拡径量に対応してインナ一側の内輪 6の肉厚 tを厚くすることができ、 加締部 1 cの塑性変形に伴い内輪 6の内 側転走面 6 aや外径 6 eに発生するフープ応力を抑制して内輪 6の強度■耐 久性を向上させることができる。 実施例 1 [0047] Further, since the degree of freedom in design increases, even if there is a difference in pitch circle diameters PCDo and PCD i, the inner diameters of the inner rings 5 and 6 are made the same so that the inner diameters 5 and 6 are fitted to each other. The part 1 b can be formed into a straight shaft shape with the shaft diameter d 1, which can improve the workability of the hub wheel 1, and the pitch circle diameter PC D i in the row of tapered rollers 10 on the inner side The wall thickness t of the inner ring 6 on the inner side can be increased corresponding to the amount of diameter expansion, and the inner raceway surface 6a and the outer diameter 6e of the inner ring 6 can be increased with plastic deformation of the caulking portion 1c. The hoop stress generated can be suppressed and the strength and durability of the inner ring 6 can be improved. Example 1
[0048] 図 2は、 本発明に係る車輪用軸受装置の第 2の実施形態を示す縦断面図で ある。 なお、 この実施形態は、 前述した実施形態と基本的にはハブ輪の構成 が異なるだけで、 その他同一部品同一部位あるいは同一機能を有する部品や 部位には同じ符号を付して詳細な説明を省略する。  FIG. 2 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described embodiment only in the configuration of the hub wheel, and other parts and parts having the same parts or the same functions are denoted by the same reference numerals for detailed description. Omitted.
[0049] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 4と、 ハブ輪 1 3、 およびこのハブ輪 1 3の小径段部 1 3 bに圧入された内 輪 6からなる内方部材 1 4とを備えている。 ハブ輪 1 3は、 外周にアウター 側の外側転走面 4 aに対向するアウター側の内側転走面 1 3 aと、 この内側 転走面 1 3 aから軸方向に延びる小径段部 1 3 bが形成されている。 内輪 6 はハブ輪 1 3の肩部 1 3 cに突合せ状態で衝合し、 小径段部 1 3 bに所定の シメシロを介して圧入されて加締部 1 cによって軸方向に固定されている。  [0049] This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 1 3 and the small diameter step portion 1 3 b of the hub wheel 13. And an inner member 14 composed of an inner ring 6. The hub wheel 1 3 has an outer outer rolling surface 4 a that faces the outer outer rolling surface 4 a on the outer periphery, and a small-diameter step portion 1 3 that extends in the axial direction from the inner rolling surface 1 3 a. b is formed. The inner ring 6 is abutted against the shoulder 1 3 c of the hub ring 1 3 in abutting condition, is press-fitted into the small-diameter stepped portion 1 3 b through a predetermined shimiro, and is fixed in the axial direction by the crimping portion 1 c. .
[0050] 外方部材 4とハブ輪 1 3および内輪 6との間に形成された環状空間の開口 部にはシール 1 5、 1 2が装着され、 軸受内部に封入されたグリースの外部 への漏洩と、 外部から雨水やダスト等が軸受内部に侵入するのを防止してい る。 また、 ハブ輪 1 3は S 5 3 C等の炭素 0 . 4 0〜0 . 8 0 w t %を含む 中高炭素鋼で形成され、 シール 1 5が摺接するシールランド部 3 bから内側 転走面 1 3 aおよび小径段部 1 3 bに亙って高周波焼入れによって表面硬さ を 5 8〜6 4 H R Cの範囲に硬化処理されている。  [0050] Seals 15 and 1 2 are attached to the openings of the annular space formed between the outer member 4 and the hub ring 13 and the inner ring 6, and the grease sealed inside the bearing is exposed to the outside. It prevents leakage and rainwater and dust from entering the bearing. The hub wheel 13 is made of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and the inner rolling surface from the seal land portion 3 b in which the seal 15 is in sliding contact. The surface hardness is hardened to a range of 58 to 64 HRC by induction hardening over 1 3 a and small diameter step 1 3 b.
[0051 ] ここで、 本実施形態は、 前述した実施形態と同様、 インナ一側の円錐ころ  [0051] Here, in the present embodiment, the tapered roller on the inner side is similar to the above-described embodiment.
1 0列のピッチ円直径 P C D iがァウタ一側の円錐ころ 9列のピッチ円直径 P C D oよりも大径 (P C D i > P C D o ) に設定され、 さらに、 インナ一 側の円錐ころ 1 0列のころ径 d iがアウター側の円錐ころ 9列のころ径 d o よりも大径 (d i > d o ) に設定されると共に、 アウター側の円錐ころ 9列 のころ長さ L oがインナ一側の円錐ころ 1 0列のころ長さ L i よりも長く設 定されている (L o > L i ) 。 これにより、 軽量■ コンパク ト化を図りつつ 軸受の剛性と寿命を向上させることができると共に、 インナ一側の円錐ころ 1 0列におけるピッチ円直径 P C D iの拡径量に対応してインナ一側の内輪 6の肉厚 tを厚くすることができ、 加締部 1 cの塑性変形に伴い内輪 6の内 側転走面 6 aや外径 6 eに発生するフープ応力を抑制してハブ輪 1 3および 内輪 6の強度■耐久性を向上させることができる。 10 pitch circle diameter PCD i is set larger than pitch circle diameter PCD o of 9 rows of pitch rollers (PCD i> PCD o), and inner side of tapered rollers 10 rows The roller diameter di is set to a larger diameter (di> do) than the roller diameter do of the outer side tapered roller 9 rows, and the roller length L o of the outer side tapered roller 9 rows is the inner side cone. The roller length is set to be longer than the roller length L i of row 10 (L o> L i). This makes it possible to improve the rigidity and life of the bearing while achieving light weight and compactness, and also to increase the pitch circle diameter PCD i in the inner row of tapered rollers 10 on the inner side. Inner ring The hub ring 1 3 can be made thicker, and the hoop stress generated on the inner raceway surface 6a and outer diameter 6e of the inner ring 6 due to plastic deformation of the caulking portion 1c can be suppressed. And Strength of inner ring 6 ■ Durability can be improved.
実施例 3  Example 3
[0052] 図 3は、 本発明に係る車輪用軸受装置の第 3の実施形態を示す縦断面図で ある。 なお、 この実施形態は、 前述した第 1の実施形態 (図 1 ) と基本的に は車輪用軸受の構成が異なるだけで、 その他同一部品同一部位あるいは同一 機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。  FIG. 3 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention. This embodiment is basically the same as the first embodiment (FIG. 1) described above except that the configuration of the wheel bearing is different, and other parts and parts having the same parts or functions having the same parts have the same reference numerals. The detailed description is omitted.
[0053] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 ' と、 このハブ輪 1 ' に固定された車輪用軸受 1 6とを備えている。 車輪用 軸受 1 6は、 ハブ輪 1 ' の肩部 1 aに衝合した状態で小径段部 1 b ' に所定 のシメシ口を介して圧入されると共に、 小径段部 1 b ' の端部を塑性変形さ せて形成した加締部 1 cによって軸方向に固定されている。  This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 ′ and a wheel bearing 16 fixed to the hub wheel 1 ′. The wheel bearing 16 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening in contact with the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′. It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.
[0054] 車輪用軸受 1 6は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複 列の外側転走面 4 a、 4 bが形成された外方部材 4と、 外周にこれら複列の 外側転走面 4 a、 4 bに対向する内側転走面 5 a、 6 aがそれぞれ形成され た 2つの内輪 5 ' 、 6 ' と、 両転走面 4 a、 5 aおよび 4 b、 6 a間に保持 器 7、 8を介して転動自在に収容された複数の円錐ころ 9、 1 0とを備えて いる。  [0054] The wheel bearing 16 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and formed with a plurality of outer rolling surfaces 4a and 4b on the inner periphery, and on the outer periphery. Two inner rings 5 ′, 6 ′ formed with inner rolling surfaces 5 a, 6 a facing the outer rolling surfaces 4 a, 4 b of the double row, and both rolling surfaces 4 a, 5 a and A plurality of tapered rollers 9 and 10 are provided between 4 b and 6 a so as to roll freely through cages 7 and 8.
[0055] ここで、 本実施形態は、 前述した実施形態と同様、 インナ一側の円錐ころ  [0055] Here, in the present embodiment, the tapered roller on the inner side is similar to the above-described embodiment.
1 0列のピッチ円直径 P C D iがァウタ一側の円錐ころ 9列のピッチ円直径 P C D oよりも大径 (P C D i > P C D o ) に設定され、 さらに、 インナ一 側の円錐ころ 1 0列のころ径 d iがアウター側の円錐ころ 9列のころ径 d o よりも大径 (d i > d o ) に設定されると共に、 アウター側の円錐ころ 9列 のころ長さ L oがインナ一側の円錐ころ 1 0列のころ長さ L i よりも長く設 定されている (L o > L i ) 。 これにより、 軽量■ コンパク ト化を図りつつ 軸受の剛性と寿命を向上させることができると共に、 インナ一側の円錐ころ 1 0列におけるピッチ円直径 P C D iの拡径量に対応してインナ一側のハブ 輪 1 ' における小径段部 1 b ' の軸径 d 2を大径 ( d 2 > d 1 (図 1 ) ) に 形成することができ、 ハブ輪 1 ' の強度■耐久性を向上させることができる 実施例 4 10 pitch circle diameter PCD i is set larger than pitch circle diameter PCD o of 9 rows of pitch rollers (PCD i> PCD o), and inner side of tapered rollers 10 rows The roller diameter di is set to a larger diameter (di> do) than the roller diameter do of the outer side tapered roller 9 rows, and the roller length L o of the outer side tapered roller 9 rows is the inner side cone. The roller length is set to be longer than the roller length L i of row 10 (L o> L i). This makes it possible to improve the rigidity and life of the bearing while achieving light weight and compactness, and also to increase the pitch circle diameter PCD i in the inner row of tapered rollers 10 on the inner side. Hub of The shaft diameter d2 of the small-diameter step 1b 'in the wheel 1' can be formed as a large diameter (d2> d1 (Fig. 1)), and the strength of the hub wheel 1 'can be improved. Yes Example 4
[0056] 図 4は、 本発明に係る車輪用軸受装置の第 4の実施形態を示す縦断面図で ある。 なお、 この実施形態は、 前述した第 3の実施形態 (図 3) と基本的に は/ \ブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは同一機能 を有する部品や部位には同じ符号を付して詳細な説明を省略する。  FIG. 4 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing device according to the present invention. This embodiment is basically the same as the third embodiment described above (Fig. 3) except that the structure of the wheel is different, and that the same parts and parts having the same function or the same function are the same. Reference numerals are assigned and detailed description is omitted.
[0057] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 4と、 ハブ輪 1 3' 、 およびこのハブ輪 1 3' の小径段部 1 3 b' に圧入さ れた内輪 6' からなる内方部材 1 7とを備えている。  [0057] This wheel bearing device is for a driven wheel referred to as a third generation, and includes an outer member 4, a hub wheel 1 3 ', and a small-diameter step portion 1 3 b' of the hub wheel 1 3 '. And an inner member 17 made of an inner ring 6 'press-fitted into the inner ring.
[0058] ハブ輪 1 3' は S 53 C等の炭素 0. 40〜0. 80w t %を含む中高炭 素鋼で形成され、 シール 1 5が摺接するシールランド部 3 bから内側転走面 1 3 aおよび小径段部 1 3 b' に亙って高周波焼入れによって表面硬さを 5 8〜64 H RCの範囲に硬化処理されている。  [0058] Hub wheel 1 3 'is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the inner rolling surface from seal land portion 3 b in which seal 15 is in sliding contact. The surface hardness is hardened to a range of 58 to 64 H RC by induction hardening over 1 3 a and the small diameter step portion 1 3 b ′.
[0059] ここで、 本実施形態は、 前述した第 3の実施形態と同様、 インナ一側の円 錐ころ 1 0列のピッチ円直径 PC D iがアウター側の円錐ころ 9列のピッチ 円直径 P CD oよりも大径 (PCD i > P C D o) に設定され、 さらに、 ィ ンナ一側の円錐ころ 1 0列のころ径 d iがアウター側の円錐ころ 9列のころ 径 d oよりも大径 (d i >d o) に設定されると共に、 アウター側の円錐こ ろ 9列のころ長さ L oがインナ一側の円錐ころ 1 0列のころ長さ L i よりも 長く設定されている (L o>L i ) 。 これにより、 軽量 ' コンパク ト化を図 りつつ軸受の剛性と寿命を向上させることができると共に、 インナ一側の円 錐ころ 1 0列におけるピッチ円直径 P CD iの拡径量に対応してインナ一側 のハブ輪 1 3' における小径段部 1 3 b' の軸径 d 2を大径 (d 2>d 1 ( 図 2) ) に形成することができ、 ハブ輪 1 3' の強度■耐久性を向上させる ことができる。  [0059] Here, in the present embodiment, as in the third embodiment described above, the pitch circle diameter of the inner one side tapered roller 10 row 10 PCi is the pitch circle diameter of the outer row tapered roller 9 row. Larger than PCDo (PCD i> PCDo), and inner roller tapered roller diameter 10 is larger than roller diameter di of outer side tapered roller 9 rows. (Di> do) and the roller length L o of the outer side conical roller 9 row is set to be longer than the roller length L i of the inner one side tapered roller 10 row (L o> L i). As a result, the rigidity and life of the bearing can be improved while achieving light weight and compactness, and the expansion diameter of the pitch circle diameter P CD i in the tapered row on the inner side 10 can be accommodated. The shaft diameter d2 of the small diameter step 1 3 b 'in the hub ring 1 3' on the inner side can be made larger (d 2> d 1 (Fig. 2)), and the strength of the hub ring 1 3 ' ■ Durability can be improved.
実施例 5 [0060] 図 5は、 本発明に係る車輪用軸受装置の第 5の実施形態を示す縦断面図で ある。 なお、 この実施形態は、 前述した第 1の実施形態 (図 1 ) と基本的に はアウター側の円錐ころの構成が異なるだけで、 その他同一部品同一部位あ るいは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略 する。 Example 5 FIG. 5 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing device according to the present invention. This embodiment is basically the same as the first embodiment (FIG. 1) described above except that the configuration of the tapered roller on the outer side is different, and other parts and parts having the same parts or the same functions. The same reference numerals are given to the same parts and detailed explanations are omitted.
[0061] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 と、 このハブ輪 1に固定された車輪用軸受 1 8とを備えている。 車輪用軸受 1 8は、 ハブ輪 1の肩部 1 aに衝合した状態で小径段部 1 bに所定のシメシ 口を介して圧入されると共に、 小径段部 1 bの端部を塑性変形させて形成し た加締部 1 cによって軸方向に固定されている。  This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 18 fixed to the hub wheel 1. The wheel bearing 18 is press-fitted into the small-diameter step 1 b through a predetermined squeeze opening while being abutted against the shoulder 1 a of the hub wheel 1 and the end of the small-diameter step 1 b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this manner.
[0062] 車輪用軸受 1 8は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複 列の外側転走面 4 a、 4 bが形成された外方部材 4と、 外周にこれら複列の 外側転走面 4 a、 4 bに対向する内側転走面 1 9 a、 6 aがそれぞれ形成さ れた 2つの内輪 1 9、 6と、 両転走面 4 a、 1 9 aおよび 4 b、 6 a間に保 持器 20、 8を介して転動自在に収容された複列の円錐ころ 2 1、 1 0列を 備えている。  [0062] The wheel bearing 18 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and a plurality of outer rolling surfaces 4a and 4b formed on the inner periphery, and on the outer periphery. Two inner races 1 9 and 6 formed with inner rolling surfaces 1 9 a and 6 a opposite to these double-row outer rolling surfaces 4 a and 4 b, and both rolling surfaces 4 a and 19 Double row tapered rollers 21 and 10 rows are provided between a and 4 b and 6 a so as to be freely rollable via cages 20 and 8.
[0063] 内輪 1 9、 6の内側転走面 1 9 a、 6 aは、 円錐ころ 2 1、 1 0にライン コンタク トするテ一パ状に形成され、 小径 (正面) 側端面 5 d、 6 dが突合 せ状態で衝合された背面合せタイプの複列円錐ころ軸受を構成している。 そ して、 内側転走面 1 9 a、 6 aの大径側に円錐ころ 2 1、 1 0を案内するた めの大鍔 5 b、 6 bと、 小径側に円錐ころ 2 1、 1 0の脱落を防止するため の小鍔 5 c、 6 cがそれぞれ形成されている。  [0063] Inner raceway surfaces 19a and 6a of inner rings 19 and 6 are formed in a taper shape in line contact with tapered rollers 21 and 10 and have a small diameter (front) side end surface 5d, 6d constitutes a back-to-back type double row tapered roller bearing where they are abutted in abutting condition. And the large roller 5 b, 6 b to guide the tapered rollers 2 1, 10 on the large diameter side of the inner rolling surfaces 1 9 a, 6 a, and the tapered rollers 2 1, 1 on the small diameter side Gavels 5c and 6c are formed to prevent 0 from falling off.
[0064] ここで、 本実施形態では、 インナ一側の円錐ころ 1 0列のピッチ円直径 P CD iがアウター側の円錐ころ 2 1列のピッチ円直径 P CD oよりも大径 ( P CD i >P CD o) に設定されると共に、 インナ一側の円錐ころ 1 0列の ころ径 d iがアウター側の円錐ころ 2 1列のころ径 d oよりも大径 (d i > d o) に設定されている。 また、 アウター側の円錐ころ 2 1列のころ長さ L oとインナ一側の円錐ころ 1 0列のころ長さ L iが同一 (L o = L i ) に設 定される共に、 それらの円錐ころ 2 1、 1 0列のころ個数は同一になるよう に設定されている。 これにより、 軸受の剛性と寿命を向上させることができ ると共に、 軸受スペースを有効に活用して軽量■ コンパク ト化を図った車輪 用軸受装置を提供することができる。 [0064] Here, in this embodiment, the pitch circle diameter P CD i of the inner one side tapered roller 10 row is larger than the pitch circle diameter P CD o of the outer side tapered roller 21 row (P CD i> P CD o) and the roller diameter di of the inner one side 10 row is set larger than the roller diameter do of the outer row 2 roller row do (di> do) ing. Also, the outer side tapered roller 2 1 row roller length L o and the inner 1 side tapered roller length 10 row roller length L i are the same (L o = L i). In addition, the number of rollers in the 2 1 and 1 0 rows is set to be the same. As a result, it is possible to improve the rigidity and life of the bearing, and to provide a wheel bearing device that is lightweight and compact by effectively utilizing the bearing space.
[0065] また、 設計自由度が増すため、 ピッチ円直径 P C D o、 P C D i に違いが あってもそれぞれの内輪 1 9、 6の内径を同一にすることにより、 内輪 1 9[0065] Further, since the degree of freedom in design increases, even if there is a difference in pitch circle diameters P C D o and P C D i, the inner diameters of the inner rings 19 and 6 are made the same, so that the inner rings 19
、 6が嵌合する小径段部 1 bが軸径 d 1からなるストレー卜な軸状に形成で き、 ハブ輪 1の加工性を向上させることができると共に、 インナ一側の円錐 ころ 1 0列におけるピッチ円直径 P C D iの拡径量に対応してインナ一側の 内輪 6の肉厚 tを厚くすることができ、 加締部 1 cの塑性変形に伴い内輪 6 の内側転走面 6 aや外径 6 eに発生するフープ応力を抑制して内輪 6の強度, 6 can be formed into a straight shaft shape with the shaft diameter d 1 and the small diameter stepped portion 1 b can improve the workability of the hub wheel 1 and the tapered roller on the inner side 1 0 The inner diameter of inner ring 6 on the inner side can be increased corresponding to the amount of expansion of pitch circle diameter PCD i in the row, and the inner raceway surface 6 of inner ring 6 can be increased along with plastic deformation of caulking portion 1c. Strength of inner ring 6 by suppressing hoop stress generated at a and outer diameter 6 e
■耐久性を向上させることができる。 ■ Durability can be improved.
実施例 6  Example 6
[0066] 図 6は、 本発明に係る車輪用軸受装置の第 6の実施形態を示す縦断面図で ある。 なお、 この実施形態は、 前述した第 2の実施形態 (図 2 ) と基本的に はアウター側の円錐ころの構成が異なるだけで、 その他同一部品同一部位あ るいは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略 する。  FIG. 6 is a longitudinal sectional view showing a sixth embodiment of the wheel bearing device according to the invention. This embodiment is basically the same as the second embodiment (FIG. 2) described above except that the configuration of the tapered roller on the outer side is different, and other parts and parts having the same parts or the same functions. The same reference numerals are given to the same parts and detailed explanations are omitted.
[0067] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 4と、 ハブ輪 2 2、 およびこのハブ輪 2 2の小径段部 1 3 bに圧入された内 輪 6からなる内方部材 2 3とを備えている。 ハブ輪 2 2は、 外周にアウター 側の外側転走面 4 aに対向するァウタ一側の内側転走面 2 2 aと、 この内側 転走面 2 2 aから軸方向に延びる小径段部 1 3 bが形成されている。 ハブ輪 2 2は S 5 3 C等の炭素 0 . 4 0〜0 . 8 0 w t %を含む中高炭素鋼で形成 され、 シール 1 5が摺接するシールランド部 3 bから内側転走面 2 2 aおよ び小径段部 1 3 bに亙って高周波焼入れによって表面硬さを 5 8〜6 4 H R Cの範囲に硬化処理されている。  This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 2 2, and the small-diameter step portion 1 3 b of the hub wheel 2 2. And an inner member 23 made of an inner ring 6. The hub wheel 2 2 has an outer rolling surface 4 a on the outer side facing the outer rolling surface 4 a on the outer side and a small diameter step portion 1 extending in the axial direction from the inner rolling surface 2 2 a. 3 b is formed. The hub wheel 2 2 is formed of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and the inner surface of the rolling contact 2 2 from the seal land 3 b in which the seal 15 is in sliding contact. The surface hardness is hardened to a range of 58 to 64 HRC by induction hardening over a and the small diameter step 1 3 b.
[0068] ここで、 本実施形態は、 前述した実施形態と同様、 インナ一側の円錐ころ 1 0列のピッチ円直径 P C D iがアウター側の円錐ころ 2 1列のピッチ円直 径 P C D oよりも大径 (P C D i > P C D o ) に設定されていると共に、 ィ ンナ一側の円錐ころ 1 0列のころ径 d iがアウター側の円錐ころ 2 1列のこ ろ径 d oよりも大径 (d i > d o ) に設定されている。 そして、 アウター側 の円錐ころ 2 1列のころ長さ L oとインナ一側の円錐ころ 1 0列のころ長さ L iが同一 (L o = L i ) 設定されると共に、 それらの円錐ころ 2 1 , 1 0 列のころ個数が同一になるように設定されている。 これにより、 さらに軽量 ■ コンパク ト化を図りつつ軸受の剛性と寿命を向上させることができる。 ま た、 インナ一側の円錐ころ 1 0列におけるピッチ円直径 P C D iの拡径量に 対応してインナ一側の内輪 6の肉厚 tを厚くすることができ、 加締部 1 cの 塑性変形に伴い内輪 6の内側転走面 6 aや外径 6 eに発生するフープ応力を 抑制してハブ輪 2 2および内輪 6の強度■耐久性を向上させることができる 実施例 7 [0068] Here, in the present embodiment, the tapered roller on the inner side is the same as the above-described embodiment. 1 0 row pitch circle diameter PCD i is outer tapered roller 2 1 row pitch circle diameter PCD o is larger than PCD o (PCD i> PCD o) and inner one tapered roller The roller diameter di of the 10th row is set to a larger diameter (di> do) than the tapered diameter do of the 2nd row. The outer side tapered roller 21 is set to the same length (L o = L i) as the roller length L o of the first row and the roller length L i of the inner row 10 are set to the same. The number of rollers in the 2 1 and 1 0 rows is set to be the same. This makes it possible to improve the rigidity and life of the bearing while achieving a lighter weight and compactness. In addition, the inner wall 6 on the inner side 6 can be increased in thickness t in accordance with the amount of expansion of the pitch circle diameter PCD i in the row of tapered rollers 10 on the inner side, and the plasticity of the caulking portion 1 c can be increased. The hoop stress generated on the inner raceway surface 6a and outer diameter 6e of the inner ring 6 due to deformation can be suppressed to improve the strength and durability of the hub wheel 22 and inner ring 6 Example 7
[0069] 図 7は、 本発明に係る車輪用軸受装置の第 7の実施形態を示す縦断面図で ある。 なお、 この実施形態は、 前述した第 5の実施形態 (図 5 ) と基本的に は/ \ブ輪と車輪用軸受の構成が一部異なるだけで、 その他同一部品同一部位 あるいは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省 略する。  FIG. 7 is a longitudinal sectional view showing a seventh embodiment of the wheel bearing device according to the invention. This embodiment is basically the same as the above-described fifth embodiment (FIG. 5) except that the structure of the wheel and the wheel bearing is partially different, and has the same parts and the same functions. Parts and parts are denoted by the same reference numerals, and detailed description is omitted.
[0070] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 ' と、 このハブ輪 1 ' に固定された車輪用軸受 2 4とを備えている。 車輪用 軸受 2 4は、 ハブ輪 1 ' の肩部 1 aに衝合した状態で小径段部 1 b ' に所定 のシメシ口を介して圧入されると共に、 小径段部 1 b ' の端部を塑性変形さ せて形成した加締部 1 cによって軸方向に固定されている。  [0070] This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 'and a wheel bearing 24 fixed to the hub wheel 1'. The wheel bearing 2 4 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening while being in contact with the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′. It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.
[0071 ] 車輪用軸受 2 4は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複 列の外側転走面 4 a、 4 bが形成された外方部材 4と、 外周にこれら複列の 外側転走面 4 a、 4 bに対向する内側転走面 1 9 a、 6 aがそれぞれ形成さ れた 2つの内輪 1 9 ' 、 6 ' と、 両転走面 4 a、 1 9 aおよび 4 b、 6 a間 に保持器 20、 8を介して転動自在に収容された複数の円錐ころ 2 1、 1 0 とを備えている。 [0071] The wheel bearing 24 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and formed with a plurality of outer rolling surfaces 4a, 4b on the inner periphery, and on the outer periphery. Two inner races 1 9 ′, 6 ′ formed with inner rolling surfaces 19 a, 6 a facing the outer rolling surfaces 4 a, 4 b of these double rows, and both rolling surfaces 4 a, Between 1 9 a and 4 b, 6 a Are provided with a plurality of tapered rollers 2 1, 1 0, which are rotatably accommodated via cages 20, 8.
[0072] ここで、 本実施形態は、 前述した実施形態と同様、 インナ一側の円錐ころ  [0072] Here, in the present embodiment, the tapered roller on the inner side is similar to the above-described embodiment.
1 0列のピッチ円直径 P C D iがアウター側の円錐ころ 2 1列のピッチ円直 径 P CD oよりも大径 (P CD i >P CD o) に設定されると共に、 インナ —側の円錐ころ 1 0列のころ径 d iがアウター側の円錐ころ 2 1列のころ径 d oよりも大径 (d i >d o) に設定されている。 そして、 アウター側の円 錐ころ 2 1列のころ長さ L oとインナ一側の円錐ころ 1 0列のころ長さ L i が同一 (L o = L i ) に設定されると共に、 それらの円錐ころ 2 1、 1 0列 のころ個数が同一になるように設定されている。 これにより、 軽量 ' コンパ ク ト化を図りつつ軸受の剛性と寿命を向上させることができると共に、 イン ナ一側の円錐ころ 1 0列におけるピッチ円直径 P C D iの拡径量に対応して ィンナ一側のハブ輪 1 ' における小径段部 1 b ' の軸径 d 2を大径 ( d 2 > d 1 (図 1 ) ) に形成することができ、 ハブ輪 1 ' の強度■耐久性を向上さ せることができる。  1 0 row pitch circle diameter PCD i is the outer tapered roller 2 1 row pitch diameter P CD o is larger than P CD o (P CD i> P CD o) and the inner cone The roller diameter di of the roller 10 row is set to be larger than the roller diameter do of the outer side roller 2 (di> do). And the outer side tapered roller 2 1 row roller length L o and inner one side tapered roller length L i are set to be the same (L o = L i) The number of rollers in the tapered roller 2 1 and 1 0 rows is set to be the same. As a result, the rigidity and life of the bearing can be improved while achieving light weight and compactness, and the inner diameter of the tapered roller 10 row on the inner side corresponds to the amount of expansion of the pitch circle diameter PCD i. The shaft diameter d2 of the small-diameter stepped portion 1b 'in the hub ring 1' on one side can be made larger (d2> d1 (Fig. 1)), and the strength and durability of the hub ring 1 ' Can be improved.
実施例 8  Example 8
[0073] 図 8は、 本発明に係る車輪用軸受装置の第 8の実施形態を示す縦断面図で ある。 なお、 この実施形態は、 前述した第 6の実施形態 (図 6) と基本的に は/ \ブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは同一機能 を有する部品や部位には同じ符号を付して詳細な説明を省略する。  FIG. 8 is a longitudinal sectional view showing an eighth embodiment of the wheel bearing device according to the invention. Note that this embodiment is basically the same as the above-described sixth embodiment (FIG. 6) except that the configuration of the wheel is different, and that the same parts and parts having the same function or the same function are the same. Reference numerals are assigned and detailed description is omitted.
[0074] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 4と、 ハブ輪 22' 、 およびこのハブ輪 22' の小径段部 1 3 b' に圧入さ れた内輪 6' からなる内方部材 25とを備えている。 ハブ輪 22' は S 53 C等の炭素 0. 40〜0. 8 Ow t %を含む中高炭素鋼で形成され、 シール 1 5が摺接するシールランド部 3 bから内側転走面 22 aおよび小径段部 1 3 b' に亙って高周波焼入れによって表面硬さを 58〜64 H RCの範囲に 硬化処理されている。  [0074] This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 13b' of the hub wheel 22 '. And an inner member 25 made of an inner ring 6 '. The hub wheel 22 'is formed of medium and high carbon steel containing carbon 0.440 to 0.8 ow t%, such as S 53 C, and the inner rolling surface 22a and the small diameter from the seal land 3b where the seal 15 is in sliding contact. The surface hardness of the stepped part 1 3 b 'is in the range of 58 to 64 H RC by induction hardening.
[0075] ここで、 本実施形態は、 前述した第 6の実施形態と同様、 インナ一側の円 錐ころ 1 0列のピッチ円直径 PCD iがアウター側の円錐ころ 21列のピッ チ円直径 P CD oよりも大径 (PCD i >PCDo) に設定されると共に、 インナ一側の円錐ころ 1 0列のころ径 d iがアウター側の円錐ころ 21列の ころ径 d oよりも大径 (d i >d o) に設定されている。 また、 アウター側 の円錐ころ 21列のころ長さ L oとインナ一側の円錐ころ 1 0列のころ長さ L iが同一 (L o = L i ) 設定されると共に、 それらの円錐ころ 21 , 1 0 列のころ個数が同一になるように設定されている。 これにより、 軽量 ' コン パク ト化を図りつつ軸受の剛性と寿命を向上させることができると共に、 ィ ンナ一側の円錐ころ 1 0列におけるピッチ円直径 PC D iの拡径量に対応し てィンナ一側のハブ輪 22 ' における小径段部 1 3 b' の軸径 d 2を大径 ( d 2>d 1 ) に形成することができ、 ハブ輪 22' の強度■耐久性を向上さ せることができる。 [0075] Here, this embodiment is similar to the above-described sixth embodiment. Tapered roller 1 Pitch circle diameter of row 0 PCD i is set to a larger diameter (PCD i> PCDo) than the pitch circle diameter P CD o of 21 rows of outer side tapered roller on inner side 1 The 0-row roller diameter di is set to a larger diameter (di> do) than the 21-row roller diameter do. In addition, the roller length L o of the outer row of tapered rollers 21 and the roller length L i of the inner row of 10 are set to be the same (L o = L i). , 1 0 The number of rollers in the row is set to be the same. As a result, it is possible to improve the rigidity and life of the bearing while achieving light weight and compactness, and to cope with the expansion amount of the pitch circle diameter PC D i in the 10-row tapered roller on the inner side. The shaft diameter d2 of the small diameter step 1 3 b 'in the hub ring 22' on the inner side can be made larger (d2> d1), and the strength of the hub ring 22 'is improved. Can be made.
実施例 9  Example 9
[0076] 図 9は、 本発明に係る車輪用軸受装置の第 9の実施形態を示す縦断面図で ある。 なお、 この実施形態は、 前述した第 5の実施形態 (図 5) と基本的に はィンナ一側の円錐ころの構成が異なるだけで、 その他同一部品同一部位あ るいは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略 する。  FIG. 9 is a longitudinal sectional view showing a ninth embodiment of the wheel bearing device according to the invention. This embodiment is basically different from the above-described fifth embodiment (FIG. 5) only in the configuration of the tapered roller on one inner side, and other parts having the same parts, the same parts, or the same functions. The parts are denoted by the same reference numerals, and detailed description is omitted.
[0077] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 と、 このハブ輪 1に固定された車輪用軸受 26とを備えている。 車輪用軸受 26は、 ハブ輪 1の肩部 1 aに衝合した状態で小径段部 1 bに所定のシメシ 口を介して圧入されると共に、 小径段部 1 bの端部を塑性変形させて形成し た加締部 1 cによって軸方向に固定されている。  This wheel bearing device is for a driven wheel referred to as a second generation, and includes a hub wheel 1 and a wheel bearing 26 fixed to the hub wheel 1. The wheel bearing 26 is press-fitted into the small-diameter step portion 1b through a predetermined squeezing opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this way.
[0078] 車輪用軸受 26は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複 列の外側転走面 4 a、 4 bが形成された外方部材 4と、 外周にこれら複列の 外側転走面 4 a、 4 bに対向する内側転走面 1 9 a、 27 aがそれぞれ形成 された 2つの内輪 1 9、 27と、 両転走面 4 a、 1 9 aおよび 4 b、 27 a 間に保持器 20、 28を介して転動自在に収容された複列の円錐ころ 21、 29列を備えている。 [0078] The wheel bearing 26 has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and a plurality of outer rolling surfaces 4a and 4b formed on the inner periphery, and these on the outer periphery. Two inner races 1 9 and 27 formed with inner rolling surfaces 1 9 a and 27 a opposite to the double row outer rolling surfaces 4 a and 4 b, and both rolling surfaces 4 a, 19 a and 4 b, 27 a Double row tapered rollers 21, which are rotatably accommodated between cages 20, 28, It has 29 columns.
[0079] 内輪 27の内側転走面 27 aは、 円錐ころ 29にラインコンタク トするテ ーパ状に形成され、 小径 (正面) 側端面 5 d、 6 dが突合せ状態で衝合され た背面合せタイプの複列円錐ころ軸受を構成している。 内輪 27および円錐 ころ 29は S U J 2等の高炭素クロム鋼で形成され、 ズブ焼入れによって芯 部まで 58〜64 H RCの範囲に硬化処理されている。  [0079] The inner rolling surface 27a of the inner ring 27 is formed in a taper shape that makes line contact with the tapered roller 29, and the rear surface where the small-diameter (front) side end surfaces 5d and 6d are abutted in a butted state A double-row tapered roller bearing of the matching type is constructed. The inner ring 27 and the tapered roller 29 are made of high carbon chrome steel such as SJ2 and hardened in the range of 58 to 64 H RC to the core part by quenching.
[0080] ここで、 本実施形態では、 インナ一側の円錐ころ 29列のピッチ円直径 P CD iがアウター側の円錐ころ 21列のピッチ円直径 PCD oよりも大径 ( PCD i >PCDo) に設定されると共に、 インナ一側の円錐ころ 29列の ころ径 d iがアウター側の円錐ころ 21列のころ径 d oよりも大径 (d i > d o) に設定されている。 また、 インナ一側の円錐ころ 29列のころ長さ L iがアウター側の円錐ころ 21列のころ長さ L oよりも長く設定 (L i >L o) される共に、 それらの円錐ころ 21、 29列のころ個数は同一になるよ うに設定されている。 これにより、 インナ一側の軸受列の基本動定格荷重が 増大して軸受の剛性と寿命を向上させることができると共に、 軸受スペース を有効に活用して軽量■ コンパク ト化を図った車輪用軸受装置を提供するこ とができる。  [0080] Here, in this embodiment, the pitch circle diameter P CD i of 29 inner tapered rollers 29 rows is larger than the pitch circle diameter PCD o of 21 outer tapered rollers 21 rows (PCD i> PCDo) The roller diameter di of 29 rows of tapered rollers on the inner side is set to a larger diameter (di> do) than the roller diameter do of 21 rows of tapered rollers on the outer side. The roller length L i of the inner side tapered roller 29 row is set to be longer than the roller length L o of the outer side tapered roller 21 row (L i> L o). The number of rollers in the 29th row is set to be the same. As a result, the basic dynamic load rating of the inner bearing row can be increased to improve the bearing rigidity and life, and the bearings for wheels can be made lightweight by making effective use of the bearing space. A device can be provided.
[0081] また、 設計自由度が増すため、 ピッチ円直径 PCDo、 PCD i に違いが あってもそれぞれの内輪 1 9、 27の内径を同一にすることにより、 内輪 1 9、 27が嵌合する小径段部 1 bが軸径 d 1からなるストレートな軸状に形 成でき、 ハブ輪 1の加工性を向上させることができると共に、 インナ一側の 円錐ころ 29列におけるピッチ円直径 PC D iの拡径量に対応してインナ一 側の内輪 27の肉厚 tを厚くすることができ、 加締部 1 cの塑性変形に伴い 内輪 27の内側転走面 27 aや外径 6 eに発生するフープ応力を抑制して内 輪 27の強度■耐久性を向上させることができる。  [0081] In addition, since the degree of freedom in design increases, even if there is a difference in pitch circle diameters PCDo and PCD i, the inner rings 19 and 27 are fitted together by making the inner rings 19 and 27 have the same inner diameter. Small diameter step 1 b can be formed into a straight shaft consisting of shaft diameter d 1, improving workability of hub wheel 1 and pitch circle diameter in 29 rows of tapered rollers on the inner side PC D i The inner wall 27 on the inner side 27 can be made thicker in accordance with the amount of expansion of the inner ring 27, and the inner ring 27 inner rolling surface 27a and outer diameter 6e By suppressing the generated hoop stress, the strength and durability of the inner ring 27 can be improved.
実施例 10  Example 10
[0082] 図 1 0は、 本発明に係る車輪用軸受装置の第 1 0の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 9の実施形態 (図 9) と基本 的にはハブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは同一 機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。 FIG. 10 is a longitudinal sectional view showing a tenth embodiment of the wheel bearing device according to the present invention. This embodiment is the same as the ninth embodiment (FIG. 9) described above. Specifically, only the configuration of the hub wheel is different, and other parts and parts having the same parts or functions having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.
[0083] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 4と、 ハブ輪 2 2、 およびこのハブ輪 2 2の小径段部 1 3 bに圧入された内 輪 2 7からなる内方部材 3 0とを備えている。 内輪 2 7は、 その小径側端面 6 dがハブ輪 2 2の肩部 1 3 cに突合せ状態で衝合し、 小径段部 1 3 bに所 定のシメシロを介して圧入されて加締部 1 cによって軸方向に固定されてい る。  This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 2 2, and the small-diameter step portion 1 3 b of the hub wheel 2 2. And an inner member 30 composed of an inner ring 27. The inner ring 27 has its small-diameter end face 6d abutted against the shoulder 1 3c of the hub ring 2 2 in abutting condition and is press-fitted into the small-diameter step 1 3b via a predetermined shimoshiro. 1 It is fixed in the axial direction by c.
[0084] ここで、 本実施形態は、 前述した実施形態と同様、 インナ一側の円錐ころ 2 9列のピッチ円直径 P C D iがアウター側の円錐ころ 2 1列のピッチ円直 径 P C D oよりも大径 (P C D i > P C D o ) に設定されていると共に、 ィ ンナ一側の円錐ころ 2 9列のころ径 d iがアウター側の円錐ころ 2 1列のこ ろ径 d oよりも大径 (d i > d o ) に設定されている。 また、 インナ一側の 円錐ころ 2 9列のころ長さ L iがアウター側の円錐ころ 2 1列のころ長さ L oよりも長く設定 (L i > L o ) される共に、 それらの円錐ころ 2 1、 2 9 列のころ個数は同一になるように設定されている。 これにより、 さらに軽量 ■ コンパク ト化を図りつつインナ一側の軸受列の基本動定格荷重が増大して 軸受の剛性と寿命を向上させることができる。 また、 インナ一側の円錐ころ 2 9列におけるピッチ円直径 P C D iの拡径量に対応してィンナ一側の内輪 2 7の肉厚 tを厚くすることができ、 加締部 1 cの塑性変形に伴い内輪 2 7 の内側転走面 2 7 aや外径 6 eに発生するフープ応力を抑制してハブ輪 2 2 および内輪 2 7の強度■耐久性を向上させることができる。  [0084] Here, in the present embodiment, as in the above-described embodiment, the pitch circle diameter PCD i of the inner side tapered roller 29 row is more than the pitch circle diameter PCD o of the outer side tapered roller 21 row. Is also set to a large diameter (PCD i> PCD o), and the roller diameter di of the inner side of the roller 29 is larger than the roller diameter di of the outer side of the tapered roller 21 of the outer side 21 ( di> do). Also, the inner side tapered roller 2 9 row roller length L i is set to be longer than the outer side tapered roller length 2 row roller length L o (L i> L o). Rollers 2 1 and 2 9 The number of rollers is set to be the same. As a result, the basic dynamic load rating of the inner bearing row can be increased and the rigidity and life of the bearing can be improved while further reducing weight and compactness. Also, the inner ring 27 on the inner side 27 can be increased in thickness t corresponding to the amount of expansion of the pitch circle diameter PCD i in the 29-row tapered roller on the inner side, and the plasticity of the caulking portion 1 c can be increased. It is possible to improve the strength and durability of the hub wheel 2 2 and the inner ring 2 7 by suppressing the hoop stress generated on the inner raceway surface 2 7 a and the outer diameter 6 e of the inner ring 2 7 due to the deformation.
実施例 11  Example 11
[0085] 図 1 1は、 本発明に係る車輪用軸受装置の第 1 1の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 9の実施形態 (図 9 ) と基本 的にはハブ輪と車輪用軸受の構成が一部異なるだけで、 その他同一部品同一 部位あるいは同一機能を有する部品や部位には同じ符号を付して詳細な説明 を省略する。 [0086] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 ' と、 このハブ輪 1 ' に固定された車輪用軸受 31 とを備えている。 車輪用 軸受 31は、 ハブ輪 1 ' の肩部 1 aに衝合した状態で小径段部 1 b ' に所定 のシメシ口を介して圧入されると共に、 小径段部 1 b' の端部を塑性変形さ せて形成した加締部 1 cによって軸方向に固定されている。 FIG. 11 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. This embodiment is basically different from the ninth embodiment (FIG. 9) described above except that the configuration of the hub wheel and the wheel bearing is partially different. Parts are denoted by the same reference numerals and detailed description thereof is omitted. This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1 ′ and a wheel bearing 31 fixed to the hub wheel 1 ′. The wheel bearing 31 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening while being abutted against the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′ is It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.
[0087] 車輪用軸受 31は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複 列の外側転走面 4 a、 4 bが形成された外方部材 4と、 外周にこれら複列の 外側転走面 4 a、 4 bに対向する内側転走面 1 9 a、 27 aがそれぞれ形成 された 2つの内輪 1 9' 、 27' と、 両転走面 4 a、 1 9 aおよび 4 b、 2 7 a間に保持器 20、 28を介して転動自在に収容された複数の円錐ころ 2 1、 29とを備えている。  [0087] The wheel bearing 31 has a vehicle body mounting flange 4c integrally formed on the outer periphery, an outer member 4 having a plurality of outer rolling surfaces 4a and 4b formed on the inner periphery, and these on the outer periphery. Two inner races 1 9 'and 27' formed with inner rolling surfaces 1 9a and 27a opposite to the double row outer rolling surfaces 4a and 4b, and both rolling surfaces 4a and 19 A plurality of tapered rollers 2 1 and 29 are provided between a and 4 b and 2 7 a so as to be freely rollable via cages 20 and 28.
[0088] ここで、 本実施形態は、 前述した実施形態と同様、 インナ一側の円錐ころ 29列のピッチ円直径 P C D iがアウター側の円錐ころ 21列のピッチ円直 径 PCDoよりも大径 (PCD i >PCDo) に設定されると共に、 インナ —側の円錐ころ 29列のころ径 d iがアウター側の円錐ころ 21列のころ径 d oよりも大径 (d i >d o) に設定されている。 そして、 インナ一側の円 錐ころ 29列のころ長さ L iがアウター側の円錐ころ 21列のころ長さ L o よりも長く設定 (L i >L o) されると共に、 それらの円錐ころ 21、 29 列のころ個数が同一になるように設定されている。 これにより、 軽量 ' コン パク ト化を図りつつ軸受の剛性と寿命を向上させることができると共に、 ィ ンナ一側の円錐ころ 29列におけるピッチ円直径 P C D iの拡径量に対応し てインナ一側のハブ輪 1 ' における小径段部 1 b' の軸径 d 2を大径 (d 2 >d 1 ) に形成することができ、 ハブ輪 1 ' の強度■耐久性を向上させるこ とができる。  [0088] Here, in the present embodiment, as in the above-described embodiment, the pitch circle diameter PCD i of 29 rows of tapered rollers on the inner side is larger than the pitch circle diameter PCDo of 21 rows of tapered rollers on the outer side. (PCD i> PCDo) and the roller diameter di of the inner side tapered roller 29 row is set to a larger diameter (di> do) than the roller diameter do of the outer side tapered roller 21 row . The roller length L i of the inner side tapered roller 29 row is set to be longer than the roller length L o of the outer side tapered roller 21 row (L i> L o), and those tapered rollers The number of rollers in the 21st and 29th rows is set to be the same. As a result, the rigidity and life of the bearing can be improved while achieving light weight and compactness, and the inner diameter can be increased in accordance with the amount of expansion of the pitch circle diameter PCD i in the 29 rows of tapered rollers on the inner side. The shaft diameter d2 of the small diameter step 1b 'on the side hub wheel 1' can be made larger (d 2> d 1), and the strength of the hub wheel 1 'can be improved. it can.
実施例 12  Example 12
[0089] 図 1 2は、 本発明に係る車輪用軸受装置の第 1 2の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 1 1の実施形態 (図 1 1 ) と 基本的にはハブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは 同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。 FIG. 12 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. This embodiment is basically the same as the first embodiment (FIG. 11) described above except that the configuration of the hub wheel is different. Parts and parts having the same function are denoted by the same reference numerals, and detailed description thereof is omitted.
[0090] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 4と、 ハブ輪 22' 、 およびこのハブ輪 22' の小径段部 1 3 b' に圧入さ れた内輪 27' からなる内方部材 32とを備えている。  [0090] This wheel bearing device is for a driven wheel referred to as a third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 13b' of the hub wheel 22 '. And an inner member 32 comprising an inner ring 27 ′.
[0091] ここで、 本実施形態は、 前述した第 7の実施形態と同様、 インナ一側の円 錐ころ 29列のピッチ円直径 P C D iがアウター側の円錐ころ 21列のピッ チ円直径 P CD oよりも大径 (PCD i >PCDo) に設定されると共に、 インナ一側の円錐ころ 29列のころ径 d iがアウター側の円錐ころ 21列の ころ径 d oよりも大径 (d i >d o) に設定されている。 また、 インナ一側 の円錐ころ 29列のころ長さ L iがアウター側の円錐ころ 21列のころ長さ L oよりも長く設定 (L i >L o) されると共に、 それらの円錐ころ 21、 29列のころ個数が同一になるように設定されている。 これにより、 さらに 軽量■ コンパク ト化を図りつつインナ一側の軸受列の基本動定格荷重が増大 して軸受の剛性と寿命を向上させることができると共に、 インナ一側のハブ 輪 22 ' における小径段部 1 3 b' の軸径 d 2を大径 ( d 2 > d 1 ) に形成 することができ、 ハブ輪 22' の強度■耐久性を向上させることができる。 実施例 13  [0091] Here, in the present embodiment, like the seventh embodiment described above, the pitch circle diameter of 29 rows of tapered rollers on the inner side PCD i is the pitch circle diameter P of 21 rows of tapered rollers on the outer side. The diameter is set larger than CD o (PCD i> PCDo), and the roller diameter di of the inner side tapered roller 29 row is larger than the roller diameter do of the outer side tapered roller 21 row (di> do ) Is set. Also, the roller length L i of the inner side tapered roller 29 row is set to be longer than the roller length L o of the outer side tapered roller 21 row (L i> L o). , 29 rows are set to have the same number of rollers. This makes it possible to increase the basic dynamic load rating of the inner bearing row while improving weight and compactness, thereby improving the rigidity and life of the bearing, and reducing the inner diameter of the hub ring 22 'on the inner side. The shaft diameter d2 of the stepped portion 13b 'can be formed to have a large diameter (d2> d1), and the strength and durability of the hub wheel 22' can be improved. Example 13
[0092] 図 1 3は、 本発明に係る車輪用軸受装置の第 1 3の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 9の実施形態 (図 9) と基本 的にはィンナ一側の円錐ころの構成が異なるだけで、 その他同一部品同一部 位あるいは同一機能を有する部品や部位には同じ符号を付して詳細な説明を 省略する。  FIG. 13 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. Note that this embodiment is basically different from the ninth embodiment (FIG. 9) described above, except that the configuration of the tapered roller on one side is basically the same. Are denoted by the same reference numerals, and detailed description thereof is omitted.
[0093] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 と、 このハブ輪 1に固定された車輪用軸受 33とを備えている。 車輪用軸受 33は、 ハブ輪 1の肩部 1 aに衝合した状態で小径段部 1 bに所定のシメシ 口を介して圧入されると共に、 小径段部 1 bの端部を塑性変形させて形成し た加締部 1 cによって軸方向に固定されている。  This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 33 fixed to the hub wheel 1. The wheel bearing 33 is press-fitted into the small-diameter step portion 1b through a predetermined squeeze opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this way.
[0094] 車輪用軸受 33は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複 列の外側転走面 4 a、 4 bが形成された外方部材 4と、 外周にこれら複列の 外側転走面 4 a、 4 bに対向する内側転走面 1 9 a、 34 aがそれぞれ形成 された 2つの内輪 1 9、 34と、 両転走面 4 a、 1 9 aおよび 4 b、 34 a 間に保持器 20、 35を介して転動自在に収容された複列の円錐ころ 21、 36列を備えている。 内輪 34および円錐ころ 36は S U J 2等の高炭素ク ロム鋼で形成され、 ズブ焼入れによって芯部まで 58〜64 H RCの範囲に 硬化処理されている。 [0094] The wheel bearing 33 has a vehicle body mounting flange 4c integrally on the outer periphery and a plurality of inner periphery flanges. An outer member 4 in which outer rolling surfaces 4 a and 4 b of the row are formed, and inner rolling surfaces 1 9 a and 34 a facing the outer rolling surfaces 4 a and 4 b of these double rows on the outer periphery are provided. Double-row cones accommodated in a freely rolling manner via cages 20 and 35 between two inner rings 1 9 and 34 formed respectively, and both rolling surfaces 4 a and 19 a and 4 b and 34 a It has 21 and 36 rollers. The inner ring 34 and the tapered roller 36 are made of high carbon chrome steel such as SUJ 2 and hardened in the range of 58 to 64 H RC to the core part by quenching.
[0095] ここで、 本実施形態では、 インナ一側の円錐ころ 36列のピッチ円直径 P CD iがアウター側の円錐ころ 21列のピッチ円直径 PCD oよりも大径 ( PCD i >PCDo) に設定されると共に、 インナ一側の円錐ころ 36列の ころ長さ L iがアウター側の円錐ころ 21列のころ長さ L oよりも長く設定 されている (L i >L o) 。 また、 インナ一側の円錐ころ 36列のころ径 d i とアウター側の円錐ころ 21列のころ径 d oが同一 (d i =d o) に設定 されると共に、 インナ一側の円錐ころ 36列のころ個数 Z iがアウター側の 円錐ころ 21列のころ個数 Z oよりも多く設定されている (Z i >Z o) 。 これにより、 軽量■ コンパク ト化を図ると共に、 インナ一側の軸受列の基本 定格荷重が高くなり軸受の剛性と寿命を向上させた車輪用軸受装置を提供す ることができる。 [0095] Here, in this embodiment, the pitch circle diameter P CD i of 36 rows of tapered rollers on the inner side is larger than the pitch circle diameter PCD o of 21 rows of tapered rollers on the outer side (PCD i> PCDo) The roller length L i of 36 rows of tapered rollers on the inner side is set to be longer than the roller length L o of 21 rows of tapered rollers on the outer side (L i> L o). Also, the roller diameter di of 36 rows of inner side tapered rollers and the roller diameter do of 21 rows of outer side tapered rollers are set to be the same (di = do), and the number of rollers of 36 rows of inner side tapered rollers is set. Z i is set to be larger than the number of rollers Z o on the outer side tapered roller 21 row (Z i> Z o). As a result, it is possible to provide a wheel bearing device that is lighter and more compact and has a higher basic rated load on the inner bearing row and improved rigidity and life of the bearing.
[0096] また、 設計自由度が増すため、 ピッチ円直径 PCDo、 PCD i に違いが あってもそれぞれの内輪 1 9、 34の内径を同一にすることにより、 内輪 1 9、 34が嵌合する小径段部 1 bが軸径 d 1からなるストレートな軸状に形 成でき、 ハブ輪 1の加工性を向上させることができると共に、 インナ一側の 円錐ころ 36列におけるピッチ円直径 PC D iの拡径量に対応してインナ一 側の内輪 34の肉厚 tを厚くすることができ、 加締部 1 cの塑性変形に伴い 内輪 34の内側転走面 34 aや外径 6 eに発生するフープ応力を抑制して内 輪 34の強度■耐久性を向上させることができる。  [0096] Further, since the degree of freedom in design increases, even if there is a difference in pitch circle diameters PCDo and PCD i, the inner rings 19 and 34 are fitted together by making the inner diameters of the inner rings 19 and 34 the same. Small diameter step 1 b can be formed into a straight shaft consisting of shaft diameter d 1, improving workability of hub wheel 1 and pitch circle diameter in 36 rows of tapered rollers on one inner side PC D i The inner wall 34 on the inner side 34 can be increased in thickness t corresponding to the amount of expansion of the inner ring 34, and the inner ring 34 inner rolling surface 34a and outer diameter 6e By suppressing the generated hoop stress, the strength and durability of the inner ring 34 can be improved.
実施例 14  Example 14
[0097] 図 1 4は、 本発明に係る車輪用軸受装置の第 1 4の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 1 3の実施形態 (図 1 3) と 基本的にはハブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは 同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。 FIG. 14 is a longitudinal sectional view showing a 14th embodiment of a wheel bearing device according to the present invention. FIG. Note that this embodiment is basically the same as the above-described first and third embodiments (Fig. 13) except that the configuration of the hub wheel is different, and the same parts and parts having the same function or the same function. Reference numerals are assigned and detailed description is omitted.
[0098] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 4と、 ハブ輪 22、 およびこのハブ輪 22の小径段部 1 3 bに圧入された内 輪 34からなる内方部材 37とを備えている。 [0098] This wheel bearing device is for a driven wheel called the third generation, and the inner member is press-fitted into the outer member 4, the hub wheel 22, and the small-diameter step portion 13b of the hub wheel 22. And an inner member 37 composed of a ring 34.
[0099] ここで、 本実施形態は、 前述した実施形態と同様、 インナ一側の円錐ころ 36列のピッチ円直径 P C D iがアウター側の円錐ころ 2 1列のピッチ円直 径 P CD oよりも大径 (P CD i >P CD o) に設定されると共に、 インナ —側の円錐ころ 36列のころ長さ L iがアウター側の円錐ころ 2 1列のころ 長さ L oよりも長く設定されている (L i > L o) 。 また、 インナ一側の円 錐ころ 36列のころ径 d i とアウター側の円錐ころ 2 1列のころ径 d oが同 - (d i =d o) に設定されると共に、 ピッチ円直径の差異に伴い、 インナ —側の円錐ころ 36列のころ個数 Z iがァゥタ一側の円錐ころ 2 1列のころ 個数 Z oよりも多く設定 (Z i >Z o) されている。 これにより、 さらに軽 量■ コンパク ト化を図りつつ軸受の剛性と寿命を向上させることができると 共に、 インナ一側の円錐ころ 36列におけるピッチ円直径 P CD iの拡径量 に対応してインナ一側の内輪 34の肉厚 tを厚くすることができる。 したが つて、 加締部 1 cの塑性変形に伴い内輪 34の内側転走面 34 aや外径 6 e に発生するフープ応力を抑制してハブ輪 22および内輪 34の強度■耐久性 を向上させることができる。 [0099] Here, in the present embodiment, similar to the above-described embodiment, the pitch circle diameter PCD i of the inner side tapered roller 36 row is derived from the pitch circle diameter P CDo of the outer side tapered roller 21 row. Is also set to a large diameter (P CD i> P CD o), and the inner side tapered roller roller 36 row length L i is longer than the outer side tapered roller 2 single row roller length L o. It is set (L i> Lo). Also, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of the outer rows of 2 tapered rollers 21 are set to the same-(di = do), and with the difference in pitch circle diameter, Inner side tapered roller 36 rows of rollers Z i is set larger than roller side tapered roller count Z o (Z i> Z o). This makes it possible to improve the rigidity and life of the bearing while achieving further light weight and compactness, as well as corresponding to the increased diameter of the pitch circle diameter P CDi in the 36-row tapered roller on the inner side. The wall thickness t of the inner ring 34 on the inner side can be increased. Therefore, the hoop stress generated on the inner raceway 34a and outer diameter 6e of the inner ring 34 due to plastic deformation of the caulking portion 1c is suppressed, and the strength and durability of the hub ring 22 and inner ring 34 are improved. Can be made.
実施例 15  Example 15
[0100] 図 1 5は、 本発明に係る車輪用軸受装置の第 1 5の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 1 3の実施形態 (図 1 3) と 基本的にはハブ輪と車輪用軸受の構成が一部異なるだけで、 その他同一部品 同一部位あるいは同一機能を有する部品や部位には同じ符号を付して詳細な 説明を省略する。  FIG. 15 is a longitudinal sectional view showing a fifteenth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically the same as the above-mentioned first to third embodiments (Fig. 13) except that the configuration of the hub wheel and the wheel bearing is partially different, and has the same parts, the same parts, and the same functions. Parts and parts are denoted by the same reference numerals, and detailed description is omitted.
[0101] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 ' と、 このハブ輪 1 ' に固定された車輪用軸受 38とを備えている。 車輪用 軸受 38は、 ハブ輪 1 ' の肩部 1 aに衝合した状態で小径段部 1 b' に所定 のシメシ口を介して圧入されると共に、 小径段部 1 b' の端部を塑性変形さ せて形成した加締部 1 cによって軸方向に固定されている。 [0101] This wheel bearing device is for a driven wheel called the second generation. 'And a wheel bearing 38 fixed to the hub wheel 1'. The wheel bearing 38 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined shim opening while abutting against the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′ is It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.
[0102] 車輪用軸受 38は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複 列の外側転走面 4 a、 4 bが形成された外方部材 4と、 外周にこれら複列の 外側転走面 4 a、 4 bに対向する内側転走面 1 9 a、 34 aがそれぞれ形成 され、 前述した第 1 3の実施形態の内輪 1 9、 34より薄肉に設定された 2 つの内輪 1 9' 、 34' と、 両転走面 4 a、 1 9 aおよび 4 b、 34 a間に 保持器 20、 35を介して転動自在に収容された複数の円錐ころ 2 1、 36 とを備えている。 [0102] The wheel bearing 38 has an outer member 4 having a body mounting flange 4c integrally formed on the outer periphery and a plurality of outer rolling surfaces 4a, 4b formed on the inner periphery, and these on the outer periphery. Inner rolling surfaces 19a and 34a facing the double-row outer rolling surfaces 4a and 4b were formed, respectively, and were set thinner than the inner rings 19 and 34 of the first to third embodiments described above. Two inner rings 1 9 'and 34' and a plurality of tapered rollers 2 1 accommodated in a rolling manner via cages 20 and 35 between both rolling surfaces 4a, 19a and 4b and 34a 2 1 36.
[0103] ここで、 本実施形態は、 前述した実施形態と同様、 インナ一側の円錐ころ 36列のピッチ円直径 P C D iがアウター側の円錐ころ 2 1列のピッチ円直 径 P CD oよりも大径 (P CD i >P CD o) に設定されると共に、 インナ —側の円錐ころ 36列のころ長さ L iがアウター側の円錐ころ 2 1列のころ 長さ L oよりも長く設定されている (L i > L o) 。 また、 インナ一側の円 錐ころ 36列のころ径 d i とアウター側の円錐ころ 2 1列のころ径 d oが同 - (d i =d o) に設定されると共に、 ピッチ円直径の差異に伴い、 インナ —側の円錐ころ 36列のころ個数 Z iがァゥタ一側の円錐ころ 2 1列のころ 個数 Z oよりも多く設定 (Z i >Z o) されている。 これにより、 軽量 - コ ンパク ト化を図りつつ軸受の剛性と寿命を向上させることができると共に、 ィンナ一側の円錐ころ 36列におけるピッチ円直径 P C D iの拡径量に対応 してハブ輪 1 ' における小径段部 1 b' の軸径 d 2を大径 (d 2>d 1 (図 1 3) ) に形成することができ、 ハブ輪 1 ' の強度■耐久性を向上させるこ とができる。  [0103] Here, in the present embodiment, as with the above-described embodiment, the pitch circle diameter PCD i of the inner side tapered roller 36 row is equal to the pitch circle diameter P CD o of the outer side tapered roller 21 row. Is also set to a large diameter (P CD i> P CD o), and the inner side tapered roller roller 36 row length L i is longer than the outer side tapered roller 2 single row roller length L o. It is set (L i> Lo). Also, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of the outer rows of 2 tapered rollers 21 are set to the same-(di = do), and with the difference in pitch circle diameter, Inner side tapered roller 36 rows of rollers Z i is set larger than roller side tapered roller count Z o (Z i> Z o). As a result, the rigidity and life of the bearing can be improved while achieving light weight and compactness, and the hub wheel 1 is compatible with the amount of expansion of the pitch circle diameter PCD i in the 36 rows of tapered rollers on the inner side. The shaft diameter d2 of the small diameter step 1b 'at' can be made large (d 2> d 1 (Fig. 1 3)), and the strength of the hub wheel 1 'can be improved. it can.
実施例 16  Example 16
[0104] 図 1 6は、 本発明に係る車輪用軸受装置の第 1 6の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 1 5の実施形態 (図 1 5) と 基本的にはハブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは 同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。 FIG. 16 is a longitudinal sectional view showing a sixteenth embodiment of the wheel bearing device according to the present invention. This embodiment is the same as the above-described 15th embodiment (FIG. 15). Basically, only the configuration of the hub wheel is different, and other parts and parts having the same parts or functions having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.
[0105] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 4と、 ハブ輪 22' 、 およびこのハブ輪 22' の小径段部 1 3 b' に圧入さ れた内輪 34' からなる内方部材 39とを備えている。  [0105] This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 1 3 b' of the hub wheel 22 '. And an inner member 39 made of an inner ring 34 '.
[0106] ここで、 本実施形態は、 インナ一側の円錐ころ 36列のピッチ円直径 PC D iがアウター側の円錐ころ 21列のピッチ円直径 PCD oよりも大径 (P CD i >PCDo) に設定されると共に、 インナ一側の円錐ころ 36列のこ ろ長さ L iがアウター側の円錐ころ 21列のころ長さ L oよりも長く設定さ れている (L i >L o) 。 また、 インナ一側の円錐ころ 36列のころ径 d i とアウター側の円錐ころ 21列のころ径 d oが同一 (d i =d o) に設定さ れると共に、 ピッチ円直径の差異に伴い、 インナ一側の円錐ころ 36列のこ ろ個数 Z iがアウター側の円錐ころ 21列のころ個数 Z oよりも多く設定 ( Z i >Z o) されている。 これにより、 さらに軽量 . コンパク ト化を図りつ つ軸受の剛性と寿命を向上させることができると共に、 インナ一側の円錐こ ろ 36列におけるピッチ円直径 PC D iの拡径量に対応してハブ輪 22' に おける小径段部 1 3 b' の軸径 d 2を大径に形成することができ、 ハブ輪 2 2' の強度■耐久性を向上させることができる。  Here, in this embodiment, the pitch circle diameter PC D i of 36 rows of tapered rollers on the inner side is larger than the pitch circle diameter PCD o of 21 rows of tapered rollers on the outer side (P CD i> PCDo ) And the length L i of the 36-side tapered roller on the inner side is set longer than the roller length L o of the 21-side tapered roller on the outer side (L i> L o ) In addition, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of the 21 rows of tapered rollers on the outer side are set to be the same (di = do). The number of rollers in 36 rows of tapered rollers Z i is set to be greater than the number of rollers Z in outer rows of tapered rollers 21 (Z i> Z o). As a result, the weight and weight of the bearing can be further improved, and the rigidity and life of the bearing can be improved. In addition, it corresponds to the expansion diameter of the pitch circle diameter PC D i in the 36 rows of inner cone cones. The shaft diameter d2 of the small-diameter stepped portion 13b 'in the hub wheel 22' can be formed large, and the strength and durability of the hub wheel 22 'can be improved.
実施例 17  Example 17
[0107] 図 1 7は、 本発明に係る車輪用軸受装置の第 1 7の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 1 3の実施形態 (図 1 3) と 基本的には車輪用軸受の構成が異なるだけで、 その他同一部品同一部位ある いは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略す る。  FIG. 17 is a longitudinal sectional view showing a seventeenth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described first to third embodiments (Fig. 13) except that the configuration of the wheel bearing is basically the same, and other parts and parts having the same parts or the same functions. The same reference numerals are assigned to and detailed descriptions thereof are omitted.
[0108] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 と、 このハブ輪 1に固定された車輪用軸受 40とを備えている。 車輪用軸受 40は、 ハブ輪 1の肩部 1 aに衝合した状態で小径段部 1 bに所定のシメシ 口を介して圧入されると共に、 小径段部 1 bの端部を塑性変形させて形成し た加締部 1 cによって軸方向に固定されている。 This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 40 fixed to the hub wheel 1. The wheel bearing 40 is press-fitted into the small-diameter step portion 1b through a predetermined squeeze opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is plastically deformed. Formed It is fixed in the axial direction by the caulking portion 1c.
[0109] 車輪用軸受 40は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複 列の外側転走面 4 a、 41 aが形成された外方部材 41 と、 外周にこれら複 列の外側転走面 4 a、 41 aに対向する内側転走面 1 9 a、 42 aがそれぞ れ形成された 2つの内輪 1 9、 42と、 両転走面 4 a、 1 9 aおよび 41 a 、 42 a間に保持器 20、 43を介して転動自在に収容された複列の円錐こ ろ 21、 36列を備えている。 内輪 42は S U J 2等の高炭素クロム鋼で形 成され、 ズブ焼入れによって芯部まで 58〜64 H RCの範囲に硬化処理さ れている。 [0109] The wheel bearing 40 has a vehicle body mounting flange 4c integrally formed on the outer periphery, an outer member 41 having a plurality of outer rolling surfaces 4a, 41a formed on the inner periphery, and these on the outer periphery. Two inner races 1 9 and 42 formed with inner rolling surfaces 1 9 a and 42 a opposite to the outer rolling surfaces 4 a and 41 a in double rows, and both rolling surfaces 4 a and 19 A double row of conical rollers 21, 36 are accommodated between a and 41a, 42a via rolling cages 20, 43, respectively. The inner ring 42 is made of high carbon chrome steel such as S U J 2 and hardened in the range of 58 to 64 H RC up to the core part by quenching.
[0110] ここで、 本実施形態では、 アウター側の円錐ころ 21列のピッチ円直径 P CD oがィンナ一側の円錐ころ 36列のピッチ円直径 P C D i よりも大径 ( PCDo>PCD i ) に設定されると共に、 インナ一側の円錐ころ 36列の ころ長さ L iがアウター側の円錐ころ 21列のころ長さ L oよりも長く設定 されている (L i >L o) 。 また、 インナ一側の円錐ころ 36列のころ径 d i とアウター側の円錐ころ 21列のころ径 d oが同一 (d i =d o) に設定 されると共に、 アウター側の円錐ころ 21列のころ個数 Z oがインナ一側の 円錐ころ 36列のころ個数 Z i よりも多く設定されている (Z o>Z i ) 。 これにより、 軽量■ コンパク ト化を図ると共に、 インナ一側の軸受列の基本 定格荷重が高くなり、 外方部材 41の外径をアップすることなく軸受の剛性 と寿命を向上させた車輪用軸受装置を提供することができる。  [0110] Here, in this embodiment, the pitch circle diameter P CDo of 21 rows of outer side tapered rollers is larger than the pitch circle diameter PCD i of 36 rows of tapered rollers on the inner side (PCDo> PCD i) The roller length L i of 36 rows of tapered rollers on the inner side is set to be longer than the roller length L o of 21 rows of tapered rollers on the outer side (L i> L o). Also, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of 21 rows of outer tapered rollers are set to be the same (di = do), and the number of rollers Z of the outer side tapered rollers 21 row is set to Z. o is set to be larger than the number of rollers Z i in the 36-row tapered roller on the inner side (Z o> Z i). This makes the wheel bearings lighter and more compact, increases the basic load rating of the inner bearing row, and increases the rigidity and life of the bearing without increasing the outer diameter of the outer member 41. An apparatus can be provided.
実施例 18  Example 18
[0111] 図 1 8は、 本発明に係る車輪用軸受装置の第 1 8の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 1 7実施形態 (図 1 7) と基 本的にはハブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは同 一機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。  [0111] FIG. 18 is a longitudinal sectional view showing a eighteenth embodiment of the wheel bearing device according to the present invention. This embodiment is basically different from the 17th embodiment described above (Fig. 17) except that the configuration of the hub wheel is different, and other parts and parts having the same function or the same function are not used. The same reference numerals are assigned and detailed description is omitted.
[0112] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 41 と、 ハブ輪 22、 およびこのハブ輪 22の小径段部 1 3 bに圧入された 内輪 42からなる内方部材 44とを備えている。 [0113] ここで、 本実施形態は、 前述した実施形態と同様、 アウター側の円錐ころ 21列のピッチ円直径 P C D oがィンナ一側の円錐ころ 36列のピッチ円直 径 PCD i よりも大径 (PCDo>PCD i ) に設定されると共に、 インナ —側の円錐ころ 36列のころ長さ L iがアウター側の円錐ころ 21列のころ 長さ L oよりも長く設定されている (L i >L o) 。 また、 インナ一側の円 錐ころ 36列のころ径 d i とアウター側の円錐ころ 21列のころ径 d oが同 - (d i =d o) に設定されると共に、 ピッチ円直径の差異に伴い、 ァウタ —側の円錐ころ 21列のころ個数 Z oがィンナ一側の円錐ころ 36列のころ 個数 Z i よりも多く設定されている (Z o>Z i ) 。 これにより、 さらに軽 量■ コンパク ト化を図りつつ軸受の剛性と寿命を向上させることができると 共に、 インナ一側の軸受列の基本定格荷重が高くなり、 外方部材 41の外径 をアップすることなく軸受の剛性と寿命を向上させることができる。 [0112] This wheel bearing device is for a driven wheel called the third generation, and includes an outer member 41, a hub wheel 22, and an inner ring press-fitted into the small-diameter step portion 13b of the hub wheel 22. And an inner member 44 made of 42. [0113] Here, in the present embodiment, the pitch circle diameter PCDo of the outer side tapered roller 21 row is larger than the pitch circle diameter PCDi of the inner side tapered roller roller 36 row, similarly to the embodiment described above. The diameter (PCDo> PCD i) is set, and the roller length L i of the inner side tapered roller row 36 is set to be longer than the roller length L o of the outer side tapered roller row 21 (L i> L o). Also, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of 21 rows of tapered rollers on the outer side are set to be the same-(di = do). The roller number Z o in the 21-side tapered roller is set to be larger than the roller number Z i in the 36-side tapered roller 36 on the inner side (Z o> Z i). This makes it possible to improve the rigidity and life of the bearing while reducing the weight and making it more compact, as well as increase the basic load rating of the inner bearing row and increase the outer diameter of the outer member 41. The rigidity and life of the bearing can be improved without doing so.
実施例 19  Example 19
[0114] 図 1 9は、 本発明に係る車輪用軸受装置の第 1 9の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 1 3実施形態 (図 1 3) と基 本的にはハブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは同 一機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。  FIG. 19 is a longitudinal sectional view showing a nineteenth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described first to third embodiments (Fig. 13) except that the configuration of the hub wheel is different, and other parts or parts having the same function or the same function are used. The same reference numerals are assigned and detailed description is omitted.
[0115] この車輪用軸受装置は第 2世代と呼称される駆動輪用であって、 ハブ輪 4 5と、 このハブ輪 45に固定された車輪用軸受 33' とを備えている。 ハブ 輪 45は、 アウター側の一端部に車輪取付フランジ 3を一体に有し、 外周に この車輪取付フランジ 3から肩部 1 aを介して軸方向に延びる円筒状の小径 段部 1 bが形成されると共に、 内周にトルク伝達用のセレ一シヨン (または スプライン) 45 aが形成されている。  This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 33 ′ fixed to the hub wheel 45. The hub wheel 45 integrally has a wheel mounting flange 3 at one end portion on the outer side, and a cylindrical small-diameter stepped portion 1 b extending in the axial direction from the wheel mounting flange 3 via a shoulder portion 1 a is formed on the outer periphery. In addition, a torque transmission selection (or spline) 45 a is formed on the inner periphery.
[0116] 車輪用軸受 33' は、 ハブ輪 45の肩部 1 aに衝合した状態で小径段部 1 bに所定のシメシ口を介して圧入されている。 ハブ輪 45は S 53 C等の炭 素 0. 40〜0. 8 Ow t %を含む中高炭素鋼で形成され、 肩部 1 aから小 径段部 1 bに亙って高周波焼入れによって表面硬さを 58〜64 H RCの範 囲に硬化処理されている。 [0117] 車輪用軸受 33' は、 外周に車体取付フランジ 4 cを一体に有し、 内周に 複列の外側転走面 4 a、 4 bが形成された外方部材 4と、 外周にこれら複列 の外側転走面 4 a、 4 bに対向する内側転走面 1 9 a、 34 aがそれぞれ形 成された 2つの内輪 1 9、 34と、 両転走面 4 a、 1 9 aおよび 4 b、 34 a間に保持器 20、 35' を介して転動自在に収容された複列の円錐ころ 2 1、 36列を備えている。 [0116] The wheel bearing 33 'is press-fitted into the small-diameter stepped portion 1b through a predetermined squeeze opening in a state where it abuts against the shoulder portion 1a of the hub wheel 45. The hub wheel 45 is made of medium and high carbon steel containing 0.44 to 0.8 Ow t% of carbon such as S 53 C, and is hardened by induction hardening from the shoulder 1a to the small diameter step 1b. Hardened to a range of 58-64 H RC. [0117] The wheel bearing 33 'has an outer member 4 integrally formed with a vehicle body mounting flange 4c on the outer periphery and formed with double-row outer rolling surfaces 4a, 4b on the inner periphery, and on the outer periphery. Two inner rings 1 9 and 34 formed with inner rolling surfaces 1 9 a and 34 a opposite to these double-row outer rolling surfaces 4 a and 4 b, and both rolling surfaces 4 a and 19 Double row tapered rollers 2 1 and 36 rows are provided between a and 4 b and 34 a so as to be freely rollable via cages 20 and 35 ′.
[0118] ここで、 本実施形態では、 インナ一側の円錐ころ 36列のピッチ円直径 P CD iがアウター側の円錐ころ 21列のピッチ円直径 PCD oよりも大径 ( PCD i >PCDo) に設定されると共に、 インナ一側の円錐ころ 36列の ころ長さ L iがアウター側の円錐ころ 21列のころ長さ L oよりも長く設定 されている (L i >L o) 。 また、 インナ一側の円錐ころ 36列のころ径 d i とアウター側の円錐ころ 21列のころ径 d oが同一 (d i =d o) に設定 されると共に、 これらの円錐ころ 21、 36のころ個数 Z i、 Z oが同一 ( Z i = Z o) に設定されている。 これにより、 軽量 ' コンパク ト化を図ると 共に、 ころ径 d i およびころ個数 Z iの増加による保持器 35' の強度ダウ ンを防止しつつインナ一側の軸受列の基本定格荷重が増大され、 軸受の剛性 と寿命を向上させた車輪用軸受装置を提供することができる。  [0118] Here, in this embodiment, the pitch circle diameter P CD i of the inner side tapered roller 36 row is larger than the pitch circle diameter PCD o of the outer side tapered roller 21 row (PCD i> PCDo). The roller length L i of 36 rows of tapered rollers on the inner side is set to be longer than the roller length L o of 21 rows of tapered rollers on the outer side (L i> L o). In addition, the roller diameter di of 36 rows of tapered rollers on the inner side and the roller diameter do of 21 rows of tapered rollers on the outer side are set to be the same (di = do), and the number of rollers Z of these tapered rollers 21, 36 is Z. i and Zo are set to the same value (Zi = Zo). As a result, the basic load rating of the inner side bearing row is increased while reducing the strength of the cage 35 'due to the increase in the roller diameter di and the number of rollers Z i, while reducing the weight and making it compact. It is possible to provide a wheel bearing device in which the rigidity and life of the bearing are improved.
実施例 20  Example 20
[0119] 図 20は、 本発明に係る車輪用軸受装置の第 20の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 1 5の実施形態 (図 1 5) と ィンナー側の円錐ころの個数が異なるだけで、 その他同一部品同一部位ある いは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略す る。  FIG. 20 is a longitudinal sectional view showing a twentieth embodiment of the wheel bearing device according to the invention. This embodiment is different from the above-mentioned 15th embodiment (Fig. 15) except that the number of tapered rollers on the inner side is different, and other parts or parts having the same function or function are the same. The same reference numerals are assigned and detailed description is omitted.
[0120] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 ' と、 このハブ輪 1 ' に固定された車輪用軸受 38' とを備えている。  [0120] This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1 'and a wheel bearing 38' fixed to the hub wheel 1 '.
[0121] ここで、 本実施形態は、 インナ一側の円錐ころ 36列のピッチ円直径 PC D iがアウター側の円錐ころ 21列のピッチ円直径 PCD oよりも大径 (P CD i >PCDo) に設定されると共に、 インナ一側の円錐ころ 36列のこ ろ長さ L iがアウター側の円錐ころ 2 1列のころ長さ L oよりも長く設定さ れている (L i > L o) 。 また、 インナ一側の円錐ころ 36列のころ径 d i とアウター側の円錐ころ 2 1列のころ径 d oが同一 (d i =d o) に設定さ れると共に、 インナ一側の円錐ころ 36列のころ個数 Z i とアウター側の円 錐ころ 2 1列のころ個数 Z oが同一 (Z i =Z o) に設定されている。 これ により、 軽量 ' コンパク ト化を図ると共に、 インナ一側の軸受列の基本定格 荷重が増大して軸受の剛性と寿命を向上させることができる。 また、 インナ —側の円錐ころ 36列におけるピッチ円直径 P C D iの拡径量に対応してィ ンナー側の内輪 34' の肉厚を厚くすることができる。 [0121] Here, in this embodiment, the pitch circle diameter PC D i of the inner side tapered roller 36 row is larger than the pitch circle diameter PCD o of the outer side tapered roller 21 row (P CD i> PCDo ) And a 36-row saw roller on the inner side. The filter length L i is set to be longer than the roller length L o of one row of outer tapered rollers 2 (L i> L o). Further, the roller diameter di of the inner side tapered roller 36 row and the outer side tapered roller roller 21 are set to be the same (di = do), and the inner side tapered roller 36 row roller is set. The number Z i and the tapered roller 2 on the outer side 2 The number of rollers Z o in one row is set to be the same (Z i = Z o). As a result, it is possible to reduce the size and weight, and increase the basic load rating of the inner side bearing row to improve the rigidity and life of the bearing. Further, the inner side inner ring 34 'can be increased in thickness corresponding to the diameter expansion amount of the pitch circle diameter PCD i in the 36 rows of tapered rollers on the inner side.
実施例 21  Example 21
[0122] 図 2 1は、 本発明に係る車輪用軸受装置の第 2 1の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 1 6の実施形態 (図 1 6) と ィンナー側の円錐ころの個数が異なるだけで、 その他同一部品同一部位ある いは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略す る。  FIG. 21 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. This embodiment is different from the above-mentioned 16th embodiment (Fig. 16) except that the number of tapered rollers on the inner side is different, and other parts or parts having the same function or function are the same. The same reference numerals are assigned and detailed description is omitted.
[0123] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 4と、 ハブ輪 22' 、 およびこのハブ輪 22' の小径段部 1 3 b' に圧入さ れた内輪 34' からなる内方部材 39' とを備えている。  [0123] This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 22 ', and the small-diameter step portion 13b' of the hub wheel 22 '. And an inner member 39 ′ composed of an inner ring 34 ′.
[0124] ここで、 本実施形態は、 インナ一側の円錐ころ 36列のピッチ円直径 P C D iがアウター側の円錐ころ 2 1列のピッチ円直径 P CD oよりも大径 (P CD i >P CD o) に設定されると共に、 インナ一側の円錐ころ 36列のこ ろ長さ L iがアウター側の円錐ころ 2 1列のころ長さ L oよりも長く設定さ れている (L i > L o) 。 また、 インナ一側の円錐ころ 36列のころ径 d i とアウター側の円錐ころ 2 1列のころ径 d oが同一 (d i =d o) に設定さ れると共に、 インナ一側の円錐ころ 36列のころ個数 Z i とアウター側の円 錐ころ 2 1列のころ個数 Z oが同一 (Z i =Z o) に設定されている。 これ により、 さらに軽量■ コンパク ト化を図り、 保持器 35' の強度ダウンを防 止することができる。 実施例 11 [0124] Here, in this embodiment, the pitch circle diameter PCD i of the inner side tapered roller 36 row is larger than the pitch circle diameter P CD o of the outer side tapered roller 2 row (P CD i> P CD o), and the length L i of the inner side tapered roller 36 row is set to be longer than the length L o of the outer side tapered roller 21 row (L i> Lo). Further, the roller diameter di of the inner side tapered roller 36 row and the outer side tapered roller roller 21 are set to be the same (di = do), and the inner side tapered roller 36 row roller is set. The number Z i and the tapered roller 2 on the outer side 2 The number of rollers Z o in one row is set to be the same (Z i = Z o). As a result, a lighter and more compact body can be achieved, and the strength of the cage 35 'can be prevented from being lowered. Example 11
[0125] 図 22は、 本発明に係る車輪用軸受装置の第 22の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 5の実施形態 (図 5) と基本 的にはハブ輪と車輪用軸受の構成が異なるだけで、 その他同一部品同一部位 あるいは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省 略する。  FIG. 22 is a longitudinal sectional view showing a twenty-second embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described fifth embodiment (Fig. 5) only in the configuration of the hub wheel and the wheel bearing, except that the same parts are the same or have the same functions. Are denoted by the same reference numerals, and detailed description is omitted.
[0126] この車輪用軸受装置は第 2世代と呼称される駆動輪用であって、 ハブ輪 4 5と、 このハブ輪 45に固定された車輪用軸受 46とを備えている。 車輪用 軸受 46は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複列の外側 転走面 4 a、 47 aが形成された外方部材 47と、 外周にこれら複列の外側 転走面 4 a、 47 aに対向する内側転走面 1 9 a、 48 aがそれぞれ形成さ れた 2つの内輪 1 9、 48と、 両転走面 4 a、 1 9 aおよび 4 b、 48 a間 に保持器 20、 49を介して転動自在に収容された複列の円錐ころ 21、 1 0列を備えている。  This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 46 fixed to the hub wheel 45. The wheel bearing 46 is integrally formed with an outer member 47 having a body mounting flange 4 c on the outer periphery and a plurality of outer rolling surfaces 4 a and 47 a on the inner periphery, and these double rows on the outer periphery. Outer rolling surfaces 4 a, 47 a Inside inner rolling surfaces 1 9 a, 48 a facing each other Two inner rings 1 9, 48, and both rolling surfaces 4 a, 19 a and 4 b , 48 a are provided with double row tapered rollers 21, 10 rows accommodated so as to roll freely through cages 20, 49.
[0127] 外方部材 47は S 53 C等の炭素 0. 40〜0. 80w t %を含む中高炭 素鋼で形成され、 複列の外側転走面 4 a、 47 aが高周波焼入れによって表 面硬さを 58〜64 H RCの範囲に硬化処理されている。 また、 内輪 48は S U J 2等の高炭素クロム鋼で形成され、 ズブ焼入れによって芯部まで 58 〜64 H RCの範囲に硬化処理されている。  [0127] The outer member 47 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the double-row outer rolling surfaces 4 a and 47 a are represented by induction hardening. Hardened to a surface hardness of 58 to 64 H RC. The inner ring 48 is made of high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 H RC up to the core part by quenching.
[0128] ここで、 本実施形態では、 アウター側の円錐ころ 21列のピッチ円直径 P CD oとインナ一側の円錐ころ 1 0列のピッチ円直径 PC D iが同一 (PC Do = PCD i ) に設定されると共に、 インナ一側の円錐ころ 1 0列のころ 径 d iがアウター側の円錐ころ 21列のころ径 d oより大径 (d i >d o) に設定されている。 また、 インナ一側の円錐ころ 1 0列のころ長さ L i とァ ウタ一側の円錐ころ 21列のころ長さ L oが同一 (L i =L o) に設定され ると共に、 これら円錐ころ 21、 1 0列のころ個数 Z o、 Z iが同一 (Z o =Z i ) に設定されている。 これにより、 インナ一側の円錐ころ 1 0列のピ ツチ円直径 PCD i を大きくすることなくインナ一側の軸受列の基本定格荷 重を高くすることができ、 外方部材 4 7の外径アップを抑制し、 軽量■ コン パク ト化を図りつつ軸受の剛性と寿命を向上させた車輪用軸受装置を提供す ることができる。 Here, in this embodiment, the pitch circle diameter P CDo of the outer side tapered roller 21 row and the pitch circle diameter PC D i of the inner row of tapered roller 10 row are the same (PC Do = PCD i ) And the roller diameter di of the inner one side tapered roller 10 is set to be larger than the roller diameter do of the outer side tapered roller 21 row (di> do). In addition, the roller length L i of the inner row of tapered rollers 10 and the roller length L o of the outer row of tapered rollers 21 are set to be the same (L i = L o). The number of rollers Zo, Zi in the rollers 21, 10 row is set to be the same (Zo = Zi). As a result, the basic rated load of the inner-side bearing row can be increased without increasing the pitch circle diameter PCD i of the inner row-side tapered roller 10 row. It is possible to provide a wheel bearing device that can increase the weight, suppress the outer diameter increase of the outer member 47, reduce the weight, and improve the rigidity and life of the bearing while achieving compactness. .
実施例 23  Example 23
[0129] 図 2 3は、 本発明に係る車輪用軸受装置の第 2 3の実施形態を示す縦断面 図である。 なお、 この実施形態は前述した第 2 2の実施形態 (図 2 2 ) と基 本的には車輪用軸受の構成が一部異なるだけで、 その他同一部品同一部位あ るいは同一機能を有する部位には同じ符号を付してその詳細な説明を省略す る。  FIG. 23 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. This embodiment is basically the same as the above-described second embodiment (FIG. 2 2) except that the configuration of the wheel bearing is partially different, and other parts having the same parts or the same functions. The same reference numerals are assigned to and detailed descriptions thereof are omitted.
[0130] この車輪用軸受装置は第 2世代と呼称される駆動輪用であって、 ハブ輪 4 5と、 このハブ輪 4 5に固定された車輪用軸受 5 0とを備えている。 車輪用 軸受 5 0は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複列の外側 転走面 4 a、 4 7 aが形成された外方部材 4 7と、 外周にこれら複列の外側 転走面 4 a、 4 7 aに対向する内側転走面 1 9 a、 5 1 aがそれぞれ形成さ れた 2つの内輪 1 9、 5 1 と、 両転走面 4 a、 1 9 aおよび 4 7 a、 5 1 a 間に保持器 2 0、 5 2を介して転動自在に収容された複列の円錐ころ 2 1、 2 9列を備えている。  [0130] This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 50 fixed to the hub wheel 45. The wheel bearing 50 includes an outer member 4 7 having a body mounting flange 4 c integrally formed on the outer periphery and double row outer rolling surfaces 4 a and 4 7 a formed on the inner periphery, and these on the outer periphery. Two inner rings 1 9 and 5 1 formed with inner rolling surfaces 1 9 a and 5 1 a opposite to the outer rolling surfaces 4 a and 4 7 a of the double row, and both rolling surfaces 4 a and 1 9 a and 4 7 a, 5 1 a are provided with double-row tapered rollers 2 1, 2 9 rows that are rotatably accommodated via cages 20, 5 2.
[0131 ] 内輪 5 1の内側転走面 5 1 aは、 円錐ころ 2 9にラインコンタク トするテ —パ状に形成され、 2つの内輪 1 9、 5 1の小径側 (正面) 端面 5 d、 6 d が突合せ状態で衝合された背面合せタイプの複列円錐ころ軸受を構成してい る。 また、 内輪 5 1は S U J 2等の高炭素クロム鋼で形成され、 ズブ焼入れ によって芯部まで 5 8〜6 4 H R Cの範囲に硬化処理されている。  [0131] The inner rolling surface 5 1 a of the inner ring 5 1 is formed in a taper shape that makes line contact with the tapered roller 2 9, and the small diameter side (front) end face 5 d of the two inner rings 1 9, 5 1 6 d is a back-to-back type double row tapered roller bearing that is abutted in a butted state. Further, the inner ring 51 is made of high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 HRC up to the core part by quenching.
[0132] ここで、 本実施形態では、 アウター側の円錐ころ 2 1列のピッチ円直径 P C D oとインナ一側の円錐ころ 2 9列のピッチ円直径 P C D iが同一 (P C D o = P C D i ) に設定されると共に、 インナ一側の円錐ころ 2 9列のころ 径 d iがアウター側の円錐ころ 2 1列のころ径 d oより大径 (d i > d o ) に設定されている。 また、 インナ一側の円錐ころ 2 9列のころ長さ L iがァ ウタ一側の円錐ころ 2 1列のころ長さ L oよりも長く (L i > L o ) 設定さ れると共に、 これら円錐ころ 2 1、 29列のころ個数 0、 2 ;が同_ ( o = Z i ) に設定されている。 これにより、 前述した実施形態と同様、 イン ナ一側の円錐ころ 29列のピッチ円直径 P C D i を大きくすることなくイン ナ一側の軸受列の基本定格荷重をさらに高くすることができ、 外方部材 47 の外径アップを抑制し、 軽量■ コンパク ト化を図りつつ軸受の剛性と寿命を 向上させることができる。 [0132] Here, in this embodiment, the outer side tapered roller 21 has one row of pitch circle diameters PCD o and the inner one side tapered roller 29 has the same pitch circle diameter PCD i (PCD o = PCD i). The roller diameter di of the inner side tapered roller 29 is set larger than the roller diameter do of the outer side roller 21 (di> do). Also, the roller length L i in the inner row of the inner row 29 is set longer than the roller length L o in the row of the tapered roller 21 in the outer row (L i> L o). At the same time, the number of rollers 0 , 2; in these tapered rollers 21, 29 is set to the same _ (o = Z i). As in the above-described embodiment, this makes it possible to further increase the basic load rating of the inner bearing row without increasing the pitch circle diameter PCD i of 29 inner tapered rollers. It is possible to improve the rigidity and life of the bearing while suppressing the increase in the outer diameter of the side member 47 and making it lighter and more compact.
実施例 24  Example 24
[0133] 図 24は、 本発明に係る車輪用軸受装置の第 24の実施形態を示す縦断面 図である。 なお、 この実施形態は前述した第 22の実施形態 (図 22) と基 本的には車輪用軸受の構成が一部異なるだけで、 その他同一部品同一部位あ るいは同一機能を有する部品や部位には同じ符号を付してその詳細な説明を 省略する。  FIG. 24 is a longitudinal sectional view showing a twenty-fourth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the 22nd embodiment described above (Fig. 22) except that the configuration of the wheel bearing is partially different, and other parts and parts having the same parts or the same functions. Are denoted by the same reference numerals, and detailed description thereof is omitted.
[0134] この車輪用軸受装置は第 2世代と呼称される駆動輪用であって、 ハブ輪 4 5と、 このハブ輪 45に固定された車輪用軸受 53とを備えている。 車輪用 軸受 53は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複列の外側 転走面 4 a、 47 aが形成された外方部材 47と、 外周にこれら複列の外側 転走面 4 a、 47 aに対向する内側転走面 5 a、 48 aがそれぞれ形成され た 2つの内輪 5、 48と、 両転走面 4 a、 5 aおよび 47 a、 48 a間に保 持器 7、 49を介して転動自在に収容された複列の円錐ころ 9、 1 0列を備 えている。  This wheel bearing device is for a drive wheel called the second generation, and includes a hub wheel 45 and a wheel bearing 53 fixed to the hub wheel 45. The wheel bearing 53 includes an outer member 47 having a body mounting flange 4c integrally formed on the outer periphery, and formed with double-row outer rolling surfaces 4a and 47a on the inner periphery, and these double-rows on the outer periphery. Outer raceway surfaces 4 a, 47 a Inner raceway surfaces 5 a, 48 a facing each other 5 a, 48 a formed between the two inner races 5, 48, and both raceways 4 a, 5 a and 47 a, 48 a Are equipped with double-row tapered rollers 9, 10 which are rotatably accommodated through cages 7, 49.
[0135] ここで、 本実施形態では、 アウター側の円錐ころ 9列のピッチ円直径 P C D oとインナ一側の円錐ころ 1 0列のピッチ円直径 P C D iが同一 (P CD [0135] Here, in this embodiment, the pitch circle diameter P C D o of the nine rows of the outer side tapered rollers is the same as the pitch circle diameter P C D i of the ten rows of the inner side tapered rollers (P CD
0 = P CD i ) に設定されると共に、 インナ一側の円錐ころ 1 0列のころ径 d iがアウター側の円錐ころ 9列のころ径 d oより大径 (d i >d o) に設 定されている。 また、 アウター側の円錐ころ 9列のころ長さ L oがインナ一 側の円錐ころ 1 0列のころ長さ L iがよりも長く (L o> L i ) 設定される と共に、 これら円錐ころ 9、 1 0列のころ個数 0、 2 ;が同_ ( 0 = 20 = P CD i) and the inner roller roller diameter di is set larger than the roller diameter do of the outer roller roller 9 row (di> do) Yes. Also, the roller length L o of the outer side tapered roller 9 row is set to be longer than the roller length L i of the inner row 10 row (L o> L i). 9, the number of rollers in row 0 , 2; is the same _ ( 0 = 2
1 ) に設定されている。 これにより、 前述した実施形態と同様、 インナ一側 およびアウター側の円錐ころ 1 0、 9列のピッチ円直径 P C D i、 PCDo を大きくすることなく複列の軸受列の基本定格荷重を高くすることができ、 外方部材 47の外径アップを抑制し、 軽量■ コンパク ト化を図りつつ軸受の 剛性と寿命を向上させることができる。 1) is set. As a result, as in the embodiment described above, the inner side And the tapered roller diameters on the outer and outer rows 10 and 9 can increase the basic load rating of the double row bearing row without increasing the PCD i and PCDo, and prevent the outer member 47 from increasing in outer diameter. And light weight ■ The rigidity and life of the bearing can be improved while achieving compactness.
実施例 25  Example 25
[0136] 図 25は、 本発明に係る車輪用軸受装置の第 25の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 22の実施形態 (図 22) と 基本的にはハブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは 同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。  FIG. 25 is a longitudinal sectional view showing a 25th embodiment of the wheel bearing device according to the present invention. This embodiment basically differs from the above-described twenty-second embodiment (Fig. 22) only in the configuration of the hub wheel, and the same reference numerals are given to other parts and parts having the same parts or the same functions. Detailed description will be omitted.
[0137] この車輪用軸受装置は第 3世代と呼称される駆動輪用であって、 外方部材 47と、 ハブ輪 54、 およびこのハブ輪 54の小径段部 1 3 bに圧入された 内輪 48からなる内方部材 55を備えている。 ハブ輪 54は、 アウター側の —端部に車輪取付フランジ 3を一体に有し、 外周にアウター側の内側転走面 22 aと、 この内側転走面 22 aから軸方向に延びる円筒状の小径段部 1 3 bが形成されている。 内輪 48は、 その小径側端面 6 dがハブ輪 54の肩部 1 3 cに突合せ状態で衝合し、 小径段部 1 3 bに所定のシメシ口を介して圧 入されて加締部 1 cによって軸方向に固定されている。  [0137] This wheel bearing device is for a drive wheel referred to as the third generation, and includes an outer member 47, a hub wheel 54, and an inner ring press-fitted into the small-diameter step portion 1 3 b of the hub wheel 54. An inner member 55 consisting of 48 is provided. The hub wheel 54 has a wheel mounting flange 3 integrally at the outer end of the outer ring, and has an outer side inner rolling surface 22 a on the outer periphery and a cylindrical shape extending in the axial direction from the inner rolling surface 22 a. A small diameter step portion 1 3 b is formed. The inner ring 48 has a small-diameter end face 6d abutting against the shoulder part 13c of the hub wheel 54 in abutting condition, and is press-fitted into the small-diameter step part 13b through a predetermined shim. It is fixed in the axial direction by c.
[0138] ハブ輪 54は S 53 C等の炭素 0. 40〜0. 80w t %を含む中高炭素 鋼で形成され、 シール 1 5が摺接するシールランド部 3 bから内側転走面 2 2 aおよび小径段部 1 3 bに亙って高周波焼入れによって表面硬さを 58〜 64 H RCの範囲に硬化処理されている。  [0138] The hub wheel 54 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the inner surface of the rolling ring 2 2 a from the seal land 3 b in which the seal 15 is in sliding contact. In addition, the surface hardness of the small diameter step portion 1 3 b is hardened by induction hardening to a range of 58 to 64 H RC.
[0139] ここで、 本実施形態は、 前述した第 1の実施形態と同様、 インナ一側の円 錐ころ 1 0列のピッチ円直径 PC D i とアウター側の円錐ころ 21列のピッ チ円直径 PCDoが同一 (PCD i =PCDo) に設定されると共に、 イン ナ一側の円錐ころ 1 0列のころ長さ L i とアウター側の円錐ころ 21列のこ ろ長さ L oが同一 (L i = L o) に設定されている。 また、 インナ一側の円 錐ころ 1 0列のころ径 d iがアウター側の円錐ころ 21列のころ径 d oより も大径 (d i >d o) に設定されると共に、 インナ一側の円錐ころ 1 0列の ころ個数 Z i とアウター側の円錐ころ 2 1列のころ個数 Z oが同一 (Z i =[0139] Here, in the present embodiment, like the first embodiment described above, the inner one side tapered roller 10 row pitch circle diameter PC D i and the outer side tapered roller 21 row pitch circle. The diameter PCDo is set to be the same (PCD i = PCDo) and the roller length L i of the inner row of the tapered roller 10 is the same as the roller length Lo of the row of the tapered rollers 21 of the outer side ( L i = L o). In addition, the tapered diameter of the inner one 10 is set to be larger than the roller diameter do of the outer tapered roller 21 (di> do), and the inner tapered roller 1 0 columns Number of rollers Z i and tapered roller on the outer side 2 Same number of rollers Z o in one row (Z i =
Z o ) に設定されている。 Z o).
[0140] これにより、 ハブ輪 5 4の強度アップを図ると共に、 インナ一側の円錐こ ろ 1 0列のピッチ円直径 P C D i を大きくすることなくインナ一側の軸受列 の基本定格荷重を高くすることができ、 外方部材 4 7の外径ァップを抑制し 、 さらに軽量■ コンパク ト化を図りつつ軸受の剛性と寿命を向上させること ができる。 [0140] This increases the strength of the hub wheel 54 and increases the basic load rating of the inner bearing row without increasing the pitch circle diameter PCD i of the inner cone cone 10 row. In addition, the outer diameter up of the outer member 47 can be suppressed, and the rigidity and life of the bearing can be improved while further reducing the size and weight.
実施例 26  Example 26
[0141 ] 図 2 6は、 本発明に係る車輪用軸受装置の第 2 6の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 2 4の実施形態 (図 2 4 ) と 基本的にはハブ輪と車輪用軸受の構成が異なるだけで、 その他同一部品同一 部位あるいは同一機能を有する部品や部位には同じ符号を付して詳細な説明 を省略する。  [0141] FIG. 26 is a longitudinal sectional view showing a 26th embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described 24th embodiment (Fig. 24) except that the configuration of the hub wheel and the bearing for the wheel is different. Parts are denoted by the same reference numerals and detailed description thereof is omitted.
[0142] この車輪用軸受装置は第 2世代と呼称される駆動輪用であって、 ハブ輪 5 6と、 このハブ輪 5 6に固定された車輪用軸受 5 7とを備えている。 ハブ輪 5 6は、 アウター側の一端部に車輪取付フランジ 3を一体に有し、 外周にこ の車輪取付フランジ 3から肩部 1 aを介して軸方向に延びる円筒状の小径段 部 1 bが形成され、 内周にトルク伝達用のセレ一シヨン (またはスプライン ) 4 5 aが形成されている。 ハブ輪 5 6は S 5 3 C等の炭素 0 . 4 0〜0 . 8 O w t %を含む中高炭素鋼で形成され、 肩部 1 aから小径段部 1 bに亙つ て高周波焼入れによって表面硬さを 5 8〜6 4 H R Cの範囲に硬化処理され ている。  [0142] This wheel bearing device is for a drive wheel called second generation, and includes a hub wheel 56 and a wheel bearing 57 fixed to the hub wheel 56. The hub wheel 56 has a wheel mounting flange 3 integrally at one end on the outer side, and a cylindrical small diameter step 1 b extending in the axial direction from the wheel mounting flange 3 to the outer periphery via a shoulder 1 a. And a torque transmission selection (or spline) 45 a is formed on the inner periphery. The hub ring 56 is formed of medium and high carbon steel containing carbon 0.40 to 0.8 O wt%, such as S53C, and is surfaced by induction hardening from the shoulder 1a to the small diameter step 1b. Hardness is hardened in the range of 58-64 HRC.
[0143] 車輪用軸受 5 7は、 ハブ輪 5 6の肩部 1 aに衝合した状態で小径段部 1 b に所定のシメシ口を介して圧入されると共に、 小径段部 1 bの端部を塑性変 形させて形成した加締部 1 cによって軸方向に固定されている。 この車輪用 軸受 5 7は、 外周に車体取付フランジ 4 cを一体に有し、 内周に複列の外側 転走面 4 a、 4 7 aが形成された外方部材 4 7と、 外周にこれら複列の外側 転走面 4 a、 4 7 aに対向する内側転走面 5 8 a、 4 8 aがそれぞれ形成さ れた 2つの内輪 58、 48と、 両転走面 4 a、 58 aおよび 47 a、 48 a 間に保持器 59、 49を介して転動自在に収容された複列の円錐ころ 60、 1 0列を備えている。 内輪 58および円錐ころ 60は S U J 2等の高炭素ク ロム鋼で形成され、 ズブ焼入れによって芯部まで 58〜64 H RCの範囲に 硬化処理されている。 [0143] The wheel bearing 5 7 is press-fitted into the small-diameter step portion 1b through a predetermined squeeze opening while being in contact with the shoulder portion 1a of the hub wheel 56, and the end of the small-diameter step portion 1b. It is fixed in the axial direction by a caulking part 1 c formed by plastic deformation of the part. This wheel bearing 5 7 has an outer member 4 7 integrally formed with a vehicle body mounting flange 4 c on the outer periphery and formed with double-row outer rolling surfaces 4 a and 4 7 a on the inner periphery, and on the outer periphery. Inner rolling surfaces 5 8 a and 4 8 a facing the outer rolling surfaces 4 a and 4 7 a of these double rows are formed, respectively. Two inner rings 58 and 48, and double-row tapered rollers 60 and 1 accommodated between the rolling surfaces 4 a, 58 a and 47 a and 48 a via cages 59 and 49, respectively. It has 0 columns. The inner ring 58 and the tapered roller 60 are made of high carbon chrome steel such as SUJ 2 and hardened in the range of 58 to 64 H RC up to the core part by quenching.
[0144] ここで、 本実施形態では、 アウター側の円錐ころ 60列のピッチ円直径 P CD oとインナ一側の円錐ころ 1 0列のピッチ円直径 PC D iが同一 (PC Do = PCD i ) に設定されると共に、 アウター側の円錐ころ 60列のころ 長さ L oがインナ一側の円錐ころ 1 0列のころ長さ L i よりも長く設定され ている (L o>L i ) 。 また、 アウター側の円錐ころ 60列のころ径 d oと インナ一側の円錐ころ 1 0列のころ径 d iが同一 (d o = d i ) に設定され ると共に、 これら円錐ころ 60、 1 0列のころ個数 Z o、 Z iが同一 (Z o =Z i ) に設定されている。 これにより、 アウター側の円錐ころ 60列のピ ツチ円直径 PCDoを大きくすることなく、 また、 その円錐ころ 60のころ 個数 Z oを増やすことなくァウタ一側の軸受列の基本定格荷重を高くするこ とができ、 外方部材 47の外径アップを抑制し、 軽量■ コンパク ト化を図り つつ軸受の剛性と寿命を向上させた車輪用軸受装置を提供することができる Here, in this embodiment, the pitch circle diameter P CD o of the outer side tapered roller 60 rows and the pitch circle diameter PC D i of the inner row of tapered rollers PC D i are the same (PC Do = PCD i ) And the roller length L o of the outer side tapered roller 60 row is set to be longer than the roller length L i of the inner side tapered roller 10 row (L o> L i). . In addition, the roller diameter do of the outer side tapered roller 60 row and the roller diameter di of the inner row 10 tapered roller 10 are set to be the same (do = di), and the tapered roller 60, 10 row roller The numbers Z o and Z i are set to be the same (Z o = Z i). This increases the basic load rating of the outer bearing row without increasing the pitch circle diameter PCDo of the outer side tapered roller 60 row and without increasing the number of rollers Zo of the tapered roller 60 row. Therefore, it is possible to provide a wheel bearing device that suppresses an increase in the outer diameter of the outer member 47 and is light and compact while improving the rigidity and life of the bearing.
実施例 27 Example 27
[0145] 図 27は、 本発明に係る車輪用軸受装置の第 27の実施形態を示す縦断面 図である。 なお、 この実施形態は前述した第 26の実施形態 (図 26) と基 本的にはハブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは同 一機能を有する部品や部位には同じ符号を付してその詳細な説明を省略する  FIG. 27 is a longitudinal sectional view showing a twenty-seventh embodiment of the wheel bearing device according to the invention. Note that this embodiment is basically different from the above-described 26th embodiment (Fig. 26) only in the configuration of the hub wheel, and other parts and parts having the same parts or parts having the same functions are designated by the same reference numerals. The detailed description is omitted.
[0146] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 ' と、 このハブ輪 1 ' に固定された車輪用軸受 57とを備えている。 車輪用 軸受 57は、 ハブ輪 1 ' の肩部 1 aに衝合した状態で小径段部 1 b ' に所定 のシメシ口を介して圧入されると共に、 小径段部 1 b' の端部を塑性変形さ せて形成した加締部 1 cによって軸方向に固定されている。 [0146] This wheel bearing device is for a driven wheel referred to as a second generation, and includes a hub wheel 1 'and a wheel bearing 57 fixed to the hub wheel 1'. The wheel bearing 57 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening in contact with the shoulder portion 1 a of the hub wheel 1 ′, and the end portion of the small-diameter step portion 1 b ′ is Plastic deformation It is fixed in the axial direction by a caulking portion 1 c formed by the above.
[0147] ここで、 本実施形態では、 アウター側の円錐ころ 60列のピッチ円直径 P CD oとインナ一側の円錐ころ 1 0列のピッチ円直径 PC D iが同一 (PC Do = PCD i ) に設定されると共に、 アウター側の円錐ころ 60列のころ 長さ L oがインナ一側の円錐ころ 1 0列のころ長さ L i よりも長く設定され ている (L o>L i ) 。 また、 アウター側の円錐ころ 60列のころ径 d oと インナ一側の円錐ころ 1 0列のころ径 d iが同一 (d o = d i ) に設定され ると共に、 これら円錐ころ 60、 1 0列のころ個数 Z o、 Z iが同一 (Z o =Z i ) に設定されている。 これにより、 アウター側の円錐ころ 60列のピ ツチ円直径 PCDoを大きくすることなく、 また、 その円錐ころ 60のころ 個数 Z oを増やすことなくァウタ一側の軸受列の基本定格荷重を高くするこ とができ、 外方部材 47の外径アップを抑制して軽量■ コンパク ト化を図り つつ軸受の剛性と寿命を向上させることができる。 Here, in this embodiment, the pitch circle diameter P CDo of the outer side tapered roller 60 rows and the pitch circle diameter PC D i of the inner row of tapered rollers PC D i are the same (PC Do = PCD i ) And the roller length L o of the outer side tapered roller 60 row is set to be longer than the roller length L i of the inner side tapered roller 10 row (L o> L i). . In addition, the roller diameter do of the outer side tapered roller 60 row and the roller diameter di of the inner row 10 tapered roller 10 are set to be the same (do = di), and the tapered roller 60, 10 row roller The numbers Z o and Z i are set to be the same (Z o = Z i). This increases the basic load rating of the outer bearing row without increasing the pitch circle diameter PCDo of the outer side tapered roller 60 row and without increasing the number of rollers Zo of the tapered roller 60 row. Therefore, the outer diameter of the outer member 47 can be suppressed and the rigidity and life of the bearing can be improved while reducing the weight and size.
実施例 28  Example 28
[0148] 図 28は、 本発明に係る車輪用軸受装置の第 28の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 26の実施形態 (図 26) と 基本的にはハブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは 同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。  FIG. 28 is a longitudinal sectional view showing a twenty-eighth embodiment of the wheel bearing device according to the invention. Note that this embodiment is basically different from the above-described twenty-sixth embodiment (Fig. 26) except that the configuration of the hub wheel is basically the same, and other parts and parts having the same parts or the same functions are denoted by the same reference numerals. Detailed description will be omitted.
[0149] この車輪用軸受装置は第 3世代と呼称される駆動輪用であって、 外方部材 47と、 ハブ輪 61、 およびこのハブ輪 61の小径段部 1 3 bに圧入された 内輪 48からなる内方部材 62を備えている。 ハブ輪 61は、 アウター側の —端部に車輪取付フランジ 3を一体に有し、 外周にアウター側の内側転走面 61 aと、 この内側転走面 61 aから軸方向に延びる円筒状の小径段部 1 3 bが形成されている。  [0149] This wheel bearing device is for a drive wheel referred to as the third generation, and includes an outer member 47, a hub wheel 61, and an inner ring press-fitted into the small-diameter step portion 1 3 b of the hub wheel 61. An inner member 62 consisting of 48 is provided. The hub wheel 61 integrally has a wheel mounting flange 3 at the outer end thereof, and has an outer inner rolling surface 61 a on the outer periphery and a cylindrical shape extending in the axial direction from the inner rolling surface 61 a. A small diameter step portion 1 3 b is formed.
[0150] ハブ輪 61は S 53 C等の炭素 0. 40〜0. 80w t %を含む中高炭素 鋼で形成され、 シール 1 5が摺接するシールランド部 3 bから内側転走面 6 1 aおよび小径段部 1 3 bに亙って高周波焼入れによって表面硬さを 58〜 64 H RCの範囲に硬化処理されている。 [0151] ここで、 本実施形態は、 前述した実施形態と同様、 アウター側の円錐ころ 60列のピッチ円直径 P CD oとインナ一側の円錐ころ 1 0列のピッチ円直 径 P CD iが同一 (P CD o = P CD i ) に設定されると共に、 アウター側 の円錐ころ 60列のころ長さ L oがインナ一側の円錐ころ 1 0列のころ長さ L i よりも長く設定されている (L o> L i ) 。 また、 アウター側の円錐こ ろ 60列のころ径 d oとインナ一側の円錐ころ 1 0列のころ径 d iが同一 ( d o=d i ) に設定されると共に、 これら円錐ころ 60、 1 0列のころ個数 Z o、 Z iが同一 (Z o = Z i ) に設定されている。 これにより、 ハブ輪 6 1の強度■剛性を高めると共に、 アウター側の円錐ころ 60列のピッチ円直 径 P CD oを大きくすることなく、 また、 その円錐ころ 60のころ個数 Z o を増やすことなくァウタ一側の軸受列の基本定格荷重を高くすることができ 、 外方部材 47の外径アップを抑制して軽量■ コンパク ト化を図りつつ軸受 の剛性と寿命を向上させることができる。 [0150] The hub wheel 61 is made of medium and high carbon steel containing 0.44 to 0.80 wt% of carbon such as S 53 C, and the seal land portion 3 b in sliding contact with the seal 1 5 to the inner rolling surface 6 1 a In addition, the surface hardness of the small diameter step portion 1 3 b is hardened by induction hardening to a range of 58 to 64 H RC. [0151] Here, in the present embodiment, as in the above-described embodiment, the pitch circle diameter P CDo of the outer side tapered roller 60 rows and the pitch circle diameter P CD i of the 10 inner row tapered rollers P CD i Are set to the same (P CD o = P CD i), and the roller length L o of the outer side tapered roller 60 row is set longer than the roller length L i of the inner side tapered roller 100 row. (L o> L i). Further, the roller diameter do of the outer side conical roller 60 rows and the roller diameter di of the inner row 10 tapered rollers 10 are set to be the same (do = di), and the tapered rollers 60, 10 rows The number of rollers Zo and Zi are set to be the same (Zo = Zi). This increases the strength and rigidity of the hub wheel 61, and also increases the number of rollers Z o of the tapered roller 60 without increasing the pitch diameter P CD o of the outer tapered roller 60 row. As a result, the basic load rating of the bearing row on the one side of the counter can be increased, and the outer diameter of the outer member 47 can be suppressed to increase the weight and the rigidity and life of the bearing can be improved while achieving compactness.
実施例 29  Example 29
[0152] 図 29は、 本発明に係る車輪用軸受装置の第 29の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 28の実施形態 (図 28) と 基本的にはハブ輪の構成が異なるだけで、 その他同一部品同一部位あるいは 同一機能を有する部位には同じ符号を付して詳細な説明を省略する。  [0152] Fig. 29 is a longitudinal sectional view showing a twenty-ninth embodiment of the wheel bearing device according to the present invention. This embodiment is basically different from the 28th embodiment (FIG. 28) described above except that the configuration of the hub wheel is different, and other parts having the same parts or the same functions are denoted by the same reference numerals. Detailed description is omitted.
[0153] この車輪用軸受装置は第 3世代と呼称される従動輪用であって、 外方部材 47と、 ハブ輪 63、 およびこのハブ輪 63の小径段部 1 3 bに圧入された 内輪 48からなる内方部材 64を備えている。 ハブ輪 63は、 アウター側の —端部に車輪取付フランジ 3を一体に有し、 外周にアウター側の内側転走面 6 1 aと、 この内側転走面 6 1 aから軸方向に延びる小径段部 1 3 bが形成 されている。 このハブ輪 63は S 53 C等の炭素 0. 40〜0. 80w t % を含む中高炭素鋼で形成され、 シール 1 5が摺接するシールランド部 3 bか ら内側転走面 6 1 aおよび小径段部 1 3 bに亙って高周波焼入れによって表 面硬さを 58〜64 H RCの範囲に硬化処理されている。  [0153] This wheel bearing device is for a driven wheel referred to as a third generation, and includes an outer member 47, a hub wheel 63, and an inner ring press-fitted into the small-diameter step portion 1 3 b of the hub wheel 63. An inner member 64 consisting of 48 is provided. The hub wheel 63 integrally has a wheel mounting flange 3 at the outer end portion, and has an outer inner rolling surface 61a on the outer periphery and a small diameter extending in the axial direction from the inner rolling surface 61a. A stepped portion 1 3 b is formed. This hub ring 63 is formed of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and from the seal land portion 3 b in which the seal 15 is in sliding contact to the inner rolling surface 6 1 a and The surface hardness is hardened to 58 to 64 H RC by induction hardening over the small diameter step 1 3 b.
[0154] ここで、 本実施形態は、 前述した実施形態と同様、 アウター側の円錐ころ 60列のピッチ円直径 PCD oとインナ一側の円錐ころ 1 0列のピッチ円直 径 PCD iが同一 (PCDo = PCD i ) に設定されると共に、 アウター側 の円錐ころ 60列のころ長さ L oがインナ一側の円錐ころ 1 0列のころ長さ L i よりも長く設定されている (L o>L i ) 。 また、 アウター側の円錐こ ろ 60列のころ径 d oとインナ一側の円錐ころ 1 0列のころ径 d iが同一 ( d o=d i ) に設定されると共に、 これら円錐ころ 60、 1 0列のころ個数 Z o、 Z iが同一 (Z o = Z i ) に設定されている。 これにより、 ハブ輪 6 3の強度■剛性を高めると共に、 アウター側の円錐ころ 60列のピッチ円直 径 PCDoを大きくすることなく、 また、 その円錐ころ 60のころ個数 Z o を増やすことなくァウタ一側の軸受列の基本定格荷重を高くすることができ 、 外方部材 47の外径アップを抑制して軽量■ コンパク ト化を図りつつ軸受 の剛性と寿命を向上させることができる。 [0154] Here, the present embodiment is similar to the above-described embodiment, in that the outer side tapered roller 60-row pitch circle diameter PCD o and inner one-side tapered roller 10 0-row pitch circle diameter PCD i is set to the same (PCDo = PCD i) and outer-side tapered roller 60-row roller length L o is set to be longer than the roller length L i of the row 10 tapered roller on the inner side (L o> L i). Further, the roller diameter do of the outer side conical roller 60 rows and the roller diameter di of the inner row 10 tapered rollers 10 are set to be the same (do = di), and the tapered rollers 60, 10 rows The number of rollers Zo and Zi are set to be the same (Zo = Zi). As a result, the strength and rigidity of the hub wheel 63 are increased, and the outer diameter of the tapered roller 60 rows of the 60 rows is increased without increasing the pitch diameter PCDo and without increasing the number of rollers Z o of the tapered roller 60. The basic load rating of the bearing row on one side can be increased, and the outer diameter of the outer member 47 can be prevented from increasing and the rigidity and life of the bearing can be improved while achieving light weight and compactness.
実施例 30  Example 30
[0155] 図 30は、 本発明に係る車輪用軸受装置の第 30の実施形態を示す縦断面 図である。 なお、 この実施形態は、 前述した第 28の実施形態 (図 28) と 基本的には/ \ブ輪の構成が一部異なるだけで、 その他同一部品同一部位ある いは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略す る。  [0155] Fig. 30 is a longitudinal sectional view showing a thirtieth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the 28th embodiment (Fig. 28) described above, except that the structure of the wheel is only partially different, and other parts having the same parts, the same parts, or the same functions. Parts are denoted by the same reference numerals and detailed description is omitted.
[0156] この車輪用軸受装置は第 3世代と呼称される駆動輪用であって、 ハブ輪 6 3と、 このハブ輪 63に圧入固定された内輪 48とからなる内方部材 64と 、 この内方部材 64に外挿された外方部材 47とを備えている。  [0156] This wheel bearing device is for a drive wheel called a third generation, and includes an inner member 64 comprising a hub wheel 63 and an inner ring 48 press-fitted and fixed to the hub wheel 63. And an outer member 47 inserted on the inner member 64.
[0157] ハブ輪 63は、 アウター側の一端部に車輪取付フランジ 3を一体に有し、 外周にアウター側のテ一パ状の内側転走面 63 aと、 この内側転走面 63 a から肩部 1 3 cを介して軸方向に延びる円筒状の小径段部 1 3 bが形成され 、 内周にトルク伝達用のセレ一シヨン (またはスプライン) 45 aが形成さ れている。 ハブ輪 63は S 53 C等の炭素 0. 40〜0. 80w t %を含む 中高炭素鋼で形成され、 車輪取付フランジ 3のインナ一側の基部 3 bから内 側転走面 63 aおよび肩部 1 3 cを介して小径段部 1 3 bに亙って高周波焼 入れによって表面硬さを 58〜64 H RCの範囲に硬化処理されている。 [0157] The hub wheel 63 integrally has a wheel mounting flange 3 at one end portion on the outer side, and has a taper-shaped inner rolling surface 63a on the outer side on the outer periphery, and the inner rolling surface 63a. A cylindrical small diameter step portion 13 b extending in the axial direction via the shoulder portion 13 c is formed, and a torque transmission selection (or spline) 45 a is formed on the inner periphery. The hub wheel 63 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the base 3 b on the inner side of the wheel mounting flange 3 to the inner rolling surface 63 a and the shoulder. Inductive firing over small diameter step 1 3 b through part 1 3 c The surface hardness is set in the range of 58 to 64 H RC by putting.
[0158] 外方部材 47は、 外周に車体取付フランジ 4 cを一体に有し、 内周にハブ 輪 63の内側転走面 63 aに対向するァウタ一側の外側転走面 4 aと、 内輪 48の内側転走面 48 aに対向するインナ一側の外側転走面 47 aが一体に 形成されている。 そして、 両転走面間に保持器 65、 49を介して複列の円 錐ころ 66、 1 0列が転動自在に収容されている。 円錐ころ 66は S U J 2 等の高炭素クロム鋼で形成され、 ズブ焼入れによって芯部まで 58〜64 H RCの範囲に硬化処理されている。 [0158] The outer member 47 has a vehicle body mounting flange 4c integrally on its outer periphery, and an outer rolling surface 4a on the one side of the hub wheel 63 facing the inner rolling surface 63a of the hub wheel 63 on the inner periphery, An inner side outer raceway surface 47a facing the inner raceway surface 48a of the inner ring 48 is integrally formed. Then, double rows of tapered rollers 66, 10 are accommodated in a freely rolling manner via cages 65, 49 between both rolling surfaces. The tapered roller 66 is made of high carbon chrome steel such as S U J 2 and hardened to the core by a quenching process in the range of 58 to 64 H RC.
[0159] ここで、 本実施形態では、 アウター側の円錐ころ 66列のピッチ円直径 P CD oとインナ一側の円錐ころ 1 0列のピッチ円直径 PC D iが同一 (PC Do = PCD i ) に設定されると共に、 アウター側の円錐ころ 66列のころ 径 d oがインナ一側の円錐ころ 1 0列のころ径 d i よりも小径 (d o<d i ) に設定され、 インナ一側の円錐ころ 1 0列のころ長さ L iがアウター側の 円錐ころ 66列のころ長さ L oよりも長く設定されている (L i >L o) 。 また、 アウター側の円錐ころ 66列のころ個数 Z oがインナ一側の円錐ころ 1 0列のころ個数 Z i よりも多く設定されている (Z o>Z i ) 。 これによ り、 アウター側の円錐ころ 66列のピッチ円直径 PCDoを大きくすること なく、 両軸受列の基本定格荷重を高くすることができ、 外方部材 47の外径 アップを抑制し、 軽量■ コンパク ト化を図りつつ軸受の剛性と寿命を向上さ せた車輪用軸受装置を提供することができる。 [0159] Here, in this embodiment, the pitch circle diameter PCDo of the outer side tapered roller 66 row and the pitch circle diameter PCDi of the inner row of tapered roller 10 row are the same (PC Do = PCD i ) And the outer side tapered roller 66 row roller diameter do is set smaller than the inner roller roller diameter di (do <di), and the inner side tapered roller The roller length L i of the 10th row is set longer than the roller length L o of the outer side tapered roller 66 row (L i> L o). Further, the number of rollers Zo in the outer side tapered roller 66 row is set to be larger than the number of rollers Zi in the inner row of tapered roller 10 row (Zo> Zi). As a result, it is possible to increase the basic load rating of both bearing rows without increasing the pitch circle diameter PCDo of the outer side tapered rollers 66 rows, reducing the outer diameter of the outer member 47 and reducing the weight. ■ It is possible to provide a wheel bearing device that improves the rigidity and life of the bearing while achieving compactness.
実施例 31  Example 31
[0160] 図 31は、 本発明に係る車輪用軸受装置の第 31の実施形態を示す縦断面 図である。 なお、 この実施形態は従動輪用で、 前述した第 30の実施形態 ( 図 30) と基本的にはハブ輪の構成が異なるだけで、 その他同一部品同一部 位あるいは同一機能を有する部品や部位には同じ符号を付してその詳細な説 明を省略する。  FIG. 31 is a longitudinal sectional view showing a thirty-first embodiment of the wheel bearing device according to the present invention. This embodiment is for a driven wheel and basically differs from the 30th embodiment (FIG. 30) described above except that the configuration of the hub wheel is different, and other parts and parts having the same parts or the same functions. The same reference numerals are assigned to the same and detailed description thereof is omitted.
[0161] この車輪用軸受装置は第 2世代と呼称される従動輪用であって、 ハブ輪 1 ' と、 このハブ輪 1 ' に固定された車輪用軸受 67とを備えている。 車輪用 軸受 67は、 ハブ輪 1 ' の肩部 1 aに衝合した状態で小径段部 1 b ' に所定 のシメシ口を介して圧入されると共に、 小径段部 1 b' の端部を塑性変形さ せて形成した加締部 1 cによって軸方向に固定されている。 [0161] This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 'and a wheel bearing 67 fixed to the hub wheel 1'. For wheels The bearing 67 is press-fitted into the small-diameter step portion 1 b ′ through a predetermined squeeze opening while being abutted against the shoulder portion 1 a of the hub wheel 1 ′, and the end of the small-diameter step portion 1 b ′ is plastically deformed It is fixed in the axial direction by the caulking portion 1 c formed in advance.
[0162] 車輪用軸受 67は、 外方部材 47と、 外周に複列の外側転走面 4 a、 47 aに対向する内側転走面 68 a、 48 aがそれぞれ形成された 2つの内輪 6 8、 48と、 両転走面 4 a、 68 aおよび 47 a、 48 a間に保持器 65、 49を介して転動自在に収容された複列の円錐ころ 66、 1 0列を備えてい る。 [0162] The wheel bearing 67 is composed of an outer member 47 and two inner rings 6 each formed with an inner rolling surface 68a, 48a opposite to the outer circumferential surface 4a, 47a of the double row on the outer circumference. 8, 48, and double-row tapered rollers 66, 10 which are rotatably accommodated via cages 65, 49 between both rolling surfaces 4a, 68a and 47a, 48a. The
[0163] アウター側の内輪 68の内側転走面 68 aは、 円錐ころ 66にラインコン タク 卜するテ一パ状に形成されている。 そして、 一対の内輪 68、 48の小 径側 (正面) 端面 5 d、 6 dが突合せ状態で衝合された背面合せタイプの複 列円錐ころ軸受を構成している。 この内輪 68の内径は、 インナ一側の内輪 48の内径と同一に設定されている。 これにより、 小径段部 1 b' をストレ 一卜な形状で一体加工することができ、 加工工数を簡素化できて低コスト化 を図ることができる。 なお、 この内輪 68は、 インナ一側の内輪 48と同様 、 S U J 2等の高炭素クロム鋼で形成され、 ズブ焼入れによって芯部まで 5 8〜64 H RCの範囲に硬化処理されている。  [0163] The inner rolling surface 68a of the inner ring 68 on the outer side is formed in a taper shape that makes a line contact with the tapered roller 66. Then, a back-to-back type double-row tapered roller bearing in which the small-diameter side (front) end faces 5 d and 6 d of the pair of inner rings 68 and 48 are abutted in a butted state is configured. The inner diameter of the inner ring 68 is set to be the same as the inner diameter of the inner ring 48 on the inner side. As a result, the small-diameter stepped portion 1 b ′ can be integrally processed in a uniform shape, and the number of processing steps can be simplified and the cost can be reduced. The inner ring 68 is formed of a high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 HRC to the core portion by quenching, like the inner ring 48 on the inner side.
[0164] ここで、 本実施形態では、 前述した第 1の実施形態と同様、 アウター側の 円錐ころ 66列のピッチ円直径 P CD oとインナ一側の円錐ころ 1 0列のピ ツチ円直径 PC D iが同一 (PCDo = PCD i ) に設定されると共に、 ァ ゥタ一側の円錐ころ 66列のころ径 d oがィンナ一側の円錐ころ 1 0列のこ ろ径 d i よりも小径 (d o<d i ) に設定され、 インナ一側の円錐ころ 1 0 列のころ長さ L iがアウター側の円錐ころ 66列のころ長さ L oよりも長く 設定されている (L i >L o) 。 また、 アウター側の円錐ころ 66列のころ 径 d oとインナ一側の円錐ころ 1 0列のころ径 d i との径差に伴い、 ァウタ —側の円錐ころ 66列のころ個数 Z oがィンナ一側の円錐ころ 1 0列のころ 個数 Z i よりも多く収容されている (Z o>Z i ) 。 これにより、 アウター 側の円錐ころ 66列のピッチ円直径 P CD oを大きくすることなく、 両軸受 列の基本定格荷重を高くすることができ、 外方部材 4 7の外径アップを抑制 し、 軽量 ' コンパク ト化を図りつつ軸受の剛性と寿命を向上させることがで さる。 Here, in the present embodiment, as in the first embodiment described above, the outer side tapered roller 66 rows of pitch circle diameters P CDo and the inner one side tapered rollers 10 rows of pitch circle diameters. PC D i is set to the same value (PCDo = PCD i), and the roller diameter dough of the outer roller row 66 is smaller than the roller diameter di of the 10 row tapered roller di ( do <di), and the roller length L i of the inner one side roller is set to be longer than the roller length L o of the outer side tapered roller row 66 (L i> L o ) Also, due to the difference in diameter between the outer side tapered roller 66 row roller diameter do and the inner side tapered roller roller 10, the outer roller side tapered roller 66 row roller count Z o Tapered roller on the side 10 Rollers in row 0 are accommodated more than Z i (Z o> Z i). This allows both bearings without increasing the pitch circle diameter P CD o of the 66 rows of tapered rollers on the outer side. The basic load rating of the row can be increased, the outer diameter of the outer member 47 can be suppressed, and the rigidity and life of the bearing can be improved while achieving light weight and compactness.
[01 65] 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く、 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。  Although 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. In addition, it is needless to say that the present invention can be carried out in various forms, and the scope of the present invention is indicated by the description of the scope of claims, and further, the equivalent meaning and scope of the scope of the claims Includes all changes.
産業上の利用可能性  Industrial applicability
[01 66] 本発明に係る車輪用軸受装置は、 駆動輪用、 従動輪用に拘わらず、 第 2ま たは第 3世代構造の車輪用軸受装置に適用することができる。  The wheel bearing device according to the present invention can be applied to a wheel bearing device of a second or third generation structure regardless of whether it is for a driving wheel or a driven wheel.
図面の簡単な説明  Brief Description of Drawings
[01 67] [図 1 ]本発明に係る車輪用軸受装置の第 1の実施形態を示す縦断面図である。  FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
[図 2]本発明に係る車輪用軸受装置の第 2の実施形態を示す縦断面図である。  FIG. 2 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention.
[図 3]本発明に係る車輪用軸受装置の第 3の実施形態を示す縦断面図である。  FIG. 3 is a longitudinal sectional view showing a third embodiment of a wheel bearing device according to the present invention.
[図 4]本発明に係る車輪用軸受装置の第 4の実施形態を示す縦断面図である。  FIG. 4 is a longitudinal sectional view showing a fourth embodiment of a wheel bearing device according to the present invention.
[図 5]本発明に係る車輪用軸受装置の第 5の実施形態を示す縦断面図である。  FIG. 5 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing device according to the invention.
[図 6]本発明に係る車輪用軸受装置の第 6の実施形態を示す縦断面図である。  FIG. 6 is a longitudinal sectional view showing a sixth embodiment of the wheel bearing device according to the invention.
[図 7]本発明に係る車輪用軸受装置の第 7の実施形態を示す縦断面図である。  FIG. 7 is a longitudinal sectional view showing a seventh embodiment of the wheel bearing device according to the invention.
[図 8]本発明に係る車輪用軸受装置の第 8の実施形態を示す縦断面図である。  FIG. 8 is a longitudinal sectional view showing an eighth embodiment of the wheel bearing device according to the invention.
[図 9]本発明に係る車輪用軸受装置の第 9の実施形態を示す縦断面図である。  FIG. 9 is a longitudinal sectional view showing a ninth embodiment of the wheel bearing device according to the invention.
[図 10]本発明に係る車輪用軸受装置の第 1 0の実施形態を示す縦断面図であ る。  FIG. 10 is a longitudinal sectional view showing a tenth embodiment of the wheel bearing device according to the present invention.
[図 1 1 ]本発明に係る車輪用軸受装置の第 1 1の実施形態を示す縦断面図であ る。  FIG. 11 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
[図 12]本発明に係る車輪用軸受装置の第 1 2の実施形態を示す縦断面図であ る。 [図 13]本発明 ί::係る車輪用軸受装置の第 1 3の実施形態を示す縦断面図であ る。 FIG. 12 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. FIG. 13 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention ί ::.
[図 14]本発明 ί::係る車輪用軸受装置の第 1 4の実施形態を示す縦断面図であ る。  FIG. 14 is a longitudinal sectional view showing a fourteenth embodiment of the wheel bearing device according to the present invention ί ::.
[図 15]本発明 I::係る車輪用軸受装置の第 1 5の実施形態を示す縦断面図であ る。  FIG. 15 is a longitudinal sectional view showing the fifteenth embodiment of the wheel bearing device according to the present invention I :.
[図 16]本発明 I::係る車輪用軸受装置の第 1 6の実施形態を示す縦断面図であ る。  FIG. 16 is a longitudinal sectional view showing the sixteenth embodiment of the wheel bearing device according to the present invention I :.
[図 17]本発明 I::係る車輪用軸受装置の第 1 7の実施形態を示す縦断面図であ る。  FIG. 17 is a longitudinal sectional view showing the seventeenth embodiment of the present invention I :: wheel bearing device according to the present invention.
[図 18]本発明 I::係る車輪用軸受装置の第 1 8の実施形態を示す縦断面図であ る。  FIG. 18 is a longitudinal sectional view showing the eighteenth embodiment of the wheel bearing device according to the present invention I :.
[図 19]本発明 I::係る車輪用軸受装置の第 1 9の実施形態を示す縦断面図であ る。  FIG. 19 is a longitudinal sectional view showing the nineteenth embodiment of the wheel bearing device according to the present invention I :.
[図 20]本発明 I: :係る車輪用軸受装置の第 2 0の実施形態を示す縦断面図であ る。  FIG. 20 is a longitudinal sectional view showing the 20th embodiment of the wheel bearing device according to the present invention I :.
[図 21 ]本発明 I::係る車輪用軸受装置の第 2 1の実施形態を示す縦断面図であ る。  FIG. 21 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention I :.
[図 22]本発明 I: :係る車輪用軸受装置の第 2 2の実施形態を示す縦断面図であ る。  FIG. 22 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention I :.
[図 23]本発明 I: :係る車輪用軸受装置の第 2 3の実施形態を示す縦断面図であ る。  FIG. 23 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention I :.
[図 24]本発明 I: :係る車輪用軸受装置の第 2 4の実施形態を示す縦断面図であ る。  FIG. 24 is a longitudinal sectional view showing a 24th embodiment of the wheel bearing device according to the present invention I :.
[図 25]本発明 I: :係る車輪用軸受装置の第 2 5の実施形態を示す縦断面図であ る。  FIG. 25 is a longitudinal sectional view showing a 25th embodiment of the wheel bearing device according to the present invention I :.
[図 26]本発明 I: :係る車輪用軸受装置の第 2 6の実施形態を示す縦断面図であ る。 [図 27]本発明に係る車輪用軸受装置の第 27の実施形態を示す縦断面図であ る。 FIG. 26 is a longitudinal sectional view showing a 26th embodiment of the wheel bearing device according to the present invention I :. FIG. 27 is a longitudinal sectional view showing a twenty-seventh embodiment of a wheel bearing device according to the invention.
[図 28]本発明に係る車輪用軸受装置の第 28の実施形態を示す縦断面図であ る。  FIG. 28 is a longitudinal sectional view showing a twenty-eighth embodiment of the wheel bearing device according to the invention.
[図 29]本発明に係る車輪用軸受装置の第 29の実施形態を示す縦断面図であ る。  FIG. 29 is a longitudinal sectional view showing a twenty-ninth embodiment of the wheel bearing device according to the present invention.
[図 30]本発明に係る車輪用軸受装置の第 30の実施形態を示す縦断面図であ る。  FIG. 30 is a longitudinal sectional view showing a thirtieth embodiment of the wheel bearing device according to the invention.
[図 31]本発明に係る車輪用軸受装置の第 3 1の実施形態を示す縦断面図であ る。  FIG. 31 is a longitudinal sectional view showing a 31st embodiment of a wheel bearing device according to the present invention.
[図 32]従来の車輪用軸受装置を示す縦断面図である。  FIG. 32 is a longitudinal sectional view showing a conventional wheel bearing device.
[図 33]従来の他の車輪用軸受装置を示す縦断面図である。 FIG. 33 is a longitudinal sectional view showing another conventional wheel bearing device.
符号の説明 Explanation of symbols
1、 1 ' 、 1 3、 1 3' 、 22、 22' 、 45、 54、 56、 6 1、 63 - ■ハブ輪  1, 1 ', 1 3, 1 3', 22, 22 ', 45, 54, 56, 6 1, 63-
1 a、 1 3 c  1 a, 1 3 c
肩部 Shoulder
1 b、 1 b' 、 1 3 b、 1 3 b'  1 b, 1 b ', 1 3 b, 1 3 b'
•小径段部  • Small diameter step
1 c  1 c
加締部 Caulking section
2、 1 6、 1 8、 24 26、 3 1、 33、 33 38、 38' 、 40、 46、 50、 53、 5 、 67 ■ ■ ■車輪用軸受  2, 1 6, 1 8, 24 26, 3 1, 33, 33 38, 38 ', 40, 46, 50, 53, 5, 67
3 单輪 取付フランジ ルランド部 3 Single wheel Mounting flange Leland
4、 4 1、 47 外方 部材  4, 4 1, 47 Outer member
4 a、 4 b、 4 1 a、 47 a 外側 転走面  4 a, 4 b, 4 1 a, 47 a Outer rolling surface
4 c 車体 取付フランジ  4 c Body mounting flange
5、 6、 5' 、 6' 、 1 9、 1 9' 、 27、 27' 、 34、 34' 、 42、 48、 5 1、 58、 68 - ■ ■内輪  5, 6, 5 ', 6', 1 9, 19 ', 27, 27', 34, 34 ', 42, 48, 51, 58, 68-
5 a、 6 a、 1 3 a、 1 9 a、 22 a、 27 a、 34 a、 42 a、 48 a、 5 1 a、 58 a、 6 1 a、 63 a、 68 a - ■ ■内側転走面  5 a, 6 a, 1 3 a, 1 9 a, 22 a, 27 a, 34 a, 42 a, 48 a, 5 1 a, 58 a, 6 1 a, 63 a, 68 a- Running surface
5 b、 6 b 大鍔 5 b, 6 b
5 c、 6 c 小! ¾5 c, 6 c small! ¾
5 d、 6 d 小径 側 u而卤 5d, 6d small diameter side u meta
6 e インナ一側 の内輪の外径  6 e Outer diameter of inner ring on inner side
7、 8、 20、 28、 35、 35' 、 43、 49、 52、 59、 65 - '保 持器  7, 8, 20, 28, 35, 35 ', 43, 49, 52, 59, 65-' Retainer
9、 2 1、 66 ァウタ一側 の円錐ころ  9, 2 1, 66 One side of tapered roller
1 0、 29、 36、 60 ィンナ一側 の円錐ころ  1 0, 29, 36, 60 One side tapered roller
1 1、 1 2、 1 5 シ一 ル  1 1, 1 2, 1 5 series
1 4、 1 7、 23、 25、 30、 32、 37、 39、 39' 、 44、 55、 1 4, 1 7, 23, 25, 30, 32, 37, 39, 39 ', 44, 55,
62、 64 内方部材62, 64 Inner member
45 a セレ —シヨン 45 a celebrity —Chillon
1 00、 1 1 4 ハブ 車 m  1 00, 1 1 4 Hub car m
1 00 a、 1 07 a、 1 1 4 a、 1 1 5 a 内側 転走面  1 00 a, 1 07 a, 1 1 4 a, 1 1 5 a Inside Rolling surface
1 00 b、 1 1 3 車輪 取付フランジ  1 00 b, 1 1 3 Wheel mounting flange
1 0 1 複列 の転がり軸受  1 0 1 Double row rolling bearing
1 02 等速 自在継手  1 02 Constant velocity universal joint
1 03、 1 1 2 外方 部材  1 03, 1 1 2 Outer part
1 03 a、 1 03 b、 1 1 2 a、 1 1 2 b 外側 転走面  1 03 a, 1 03 b, 1 1 2 a, 1 1 2 b Outer rolling surface
1 03 c、 1 1 2 c 車体 取付フランジ  1 03 c, 1 1 2 c Body mounting flange
1 04、 1 1 6 内方 部材  1 04, 1 1 6 Inner part
1 05、 1 1 7、 1 1 8 ポ一 ル  1 05, 1 1 7, 1 1 8 Poles
1 06 円錐 ころ  1 06 Conical roller
1 07、 1 1 5 内輪 1 07, 1 1 5 Inner ring
1 08 外側 継手部材 1 08 Outer joint member
1 08 a トラ ック溝 1 09 マウ ス部 1 08 a Track groove 1 09 Mouse part
1 1 0 肩部 1 1 0 shoulder
1 1 1 止め 車 ffl 1 1 1 stop car ffl
1 1 4 b 小径 段部  1 1 4 b Small diameter Step
1 1 4 c 加締 部  1 1 4 c Clamping section
1 1 9、 1 20 保持  1 1 9, 1 20 hold
1 21、 1 22 シ一 ル 1 21, 1 22 series
d 1、 d 2 小径 段部の軸径 d 1, d 2 Small diameter Step diameter
d i インナ一側の円錐ころの ころ径 d i Roller diameter of tapered roller on inner side
d o アウター側の円錐ころの ころ径 d o Outer side tapered roller diameter
D 1 アウター側のポールのピ ツチ円直径  D 1 Pitch circle diameter of outer pole
D 2 ィンナ一側のポールのピ ツチ円直径  D 2 Inner side pole pitch circle diameter
L i インナ一側の円錐ころの ころ長さ  L i Roller length of tapered roller on one side
L o アウター側の円錐ころの ころ長さ  L o Roller length of outer side tapered roller
PCD i インナ一側の円錐ころの ピッチ円直径 PCD i inner tapered roller Pitch circle diameter
PCDo アウター側の円錐ころの ピッチ円直径  PCDo Pitch circle diameter of outer side tapered roller
t インナ一側の円錐ころの内輪 肉厚  t Inner ring of inner roller
Z i インナ一側の円錐ころのころ 個数  Z i Tapered roller on one inner side
Z o アウター側の円錐ころのころ 個数  Z o Outer side tapered roller

Claims

請求の範囲 The scope of the claims
[ 1 ] 外周にナックルに取り付けられるための車体取付フランジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、  [1] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;
—端部に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に 小径段部が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外 周に前記複列の外側転走面に対向する内側転走面が形成された少なくとも一 つの内輪からなる内方部材と、  -Hub wheel with a wheel mounting flange for mounting the wheel at the end, with a small diameter step formed on the outer periphery, and press-fitted into the small diameter step of this hub wheel, and the outer periphery of the double row on the outer periphery An inner member composed of at least one inner ring formed with an inner rolling surface facing the rolling surface;
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 円錐ころ列とを備えた車輪用軸受装置において、  In the wheel bearing device comprising the inner member and a double row tapered roller row accommodated so as to roll between both rolling surfaces of the outer member,
前記複列の円錐ころ列のうちインナ一側の円錐ころ列のピッチ円直径がァ ウタ一側の円錐ころ列のピッチ円直径よりも大径に設定され、 さらに、 前記 ィンナー側の円錐ころ列のころ径が前記ァウタ一側の円錐ころ列のころ径ょ りも大径に設定されると共に、 前記アウター側の円錐ころ列のころ長さが前 記ィンナ一側の円錐ころ列のころ長さよりも長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 tapered roller row of the double row tapered roller row is set larger than the pitch circle diameter of the outer side tapered roller row, and further, the inner side tapered roller row. The roller diameter of the tapered roller row on the one side of the outer side is set to be larger than the roller diameter of the tapered roller row on the one side, and the roller length of the tapered roller row on the outer side is set to the roller length of the tapered roller row on the one side. The wheel bearing device is characterized in that it is set longer than the above.
[2] 外周にナックルに取り付けられるための車体取付フランジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 [2] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;
—端部に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に 小径段部が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外 周に前記複列の外側転走面に対向する内側転走面が形成された少なくとも一 つの内輪からなる内方部材と、  -Hub wheel with a wheel mounting flange for mounting the wheel at the end, with a small diameter step formed on the outer periphery, and press-fitted into the small diameter step of this hub wheel, and the outer periphery of the double row on the outer periphery An inner member composed of at least one inner ring formed with an inner rolling surface facing the rolling surface;
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 円錐ころ列とを備えた車輪用軸受装置において、  In the wheel bearing device comprising the inner member and a double row tapered roller row accommodated so as to roll between both rolling surfaces of the outer member,
前記複列の円錐ころ列のうちインナ一側の円錐ころ列のピッチ円直径がァ ウタ一側の円錐ころ列のピッチ円直径よりも大径に設定されると共に、 前記 ィンナー側の円錐ころ列のころ径が前記ァウタ一側の円錐ころ列のころ径ょ りも大径に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 tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row, and the inner side tapered roller row The roller bearing is characterized in that the roller diameter of the tapered roller row on one side of the outer is set to be larger.
[3] 前記インナ一側の円錐ころ列のころ長さが前記アウター側の円錐ころ列の ころ長さよりも長く設定されている請求項 1または 2に記載の車輪用軸受装 置。 [3] The roller length of the inner side tapered roller row is equal to that of the outer side tapered roller row. 3. The wheel bearing device according to claim 1, wherein the wheel bearing device is set longer than the roller length.
[4] 前記複列の円錐ころ列のころ個数が同一に設定されている請求項 1乃至 3 いずれかに記載の車輪用軸受装置。  [4] The wheel bearing device according to any one of claims 1 to 3, wherein the number of rollers of the double row tapered roller row is set to be the same.
[5] 外周にナックルに取り付けられるための車体取付フランジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 [5] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;
—端部に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に 小径段部が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外 周に前記複列の外側転走面に対向する内側転走面が形成された少なくとも一 つの内輪からなる内方部材と、  -Hub wheel with a wheel mounting flange for mounting the wheel at the end, with a small diameter step formed on the outer periphery, and press-fitted into the small diameter step of this hub wheel, and the outer periphery of the double row on the outer periphery An inner member composed of at least one inner ring formed with an inner rolling surface facing the rolling surface;
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 円錐ころ列とを備えた車輪用軸受装置において、  In the wheel bearing device comprising the inner member and a double row tapered roller row accommodated so as to roll between both rolling surfaces of the outer member,
前記複列の円錐ころ列のうちインナ一側の円錐ころ列のピッチ円直径がァ ウタ一側の円錐ころ列のピッチ円直径よりも大径に設定されると共に、 前記 ィンナー側の円錐ころ列のころ長さが前記アウター側の円錐ころ列のころ長 さよりも長く設定され、 力、つ、 前記インナ一側の円錐ころ列のころ個数が前 記アウター側の円錐ころ列のころ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 tapered roller row of the double row tapered roller rows is set larger than the pitch circle diameter of the outer side tapered roller row, and the inner side tapered roller row The roller length is set to be longer than the roller length of the outer side tapered roller row, and the number of rollers in the inner side tapered roller row is larger than the number of rollers in the outer side tapered roller row. A wheel bearing device characterized by a large number of settings.
[6] 外周にナックルに取り付けられるための車体取付フランジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 [6] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;
—端部に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に 小径段部が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外 周に前記複列の外側転走面に対向する内側転走面が形成された少なくとも一 つの内輪からなる内方部材と、  -Hub wheel with a wheel mounting flange for mounting the wheel at the end, with a small diameter step formed on the outer periphery, and press-fitted into the small diameter step of this hub wheel, and the outer periphery of the double row on the outer periphery An inner member composed of at least one inner ring formed with an inner rolling surface facing the rolling surface;
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 円錐ころ列とを備えた車輪用軸受装置において、  In the wheel bearing device comprising the inner member and a double row tapered roller row accommodated so as to roll between both rolling surfaces of the outer member,
前記複列の円錐ころ列のうちアウター側の円錐ころ列のピッチ円直径がィ ンナ一側の円錐ころ列のピッチ円直径よりも大径に設定されると共に、 前記 インナ一側の円錐ころ列のころ長さが前記アウター側の円錐ころ列のころ長 さよりも長く設定され、 力、つ、 前記アウター側の円錐ころ列のころ個数が前 記ィンナ一側の円錐ころ列のころ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 outer side tapered roller row of the double row tapered roller row is set larger than the pitch circle diameter of the inner side tapered roller row, and The roller length of the inner side tapered roller row is set to be longer than the roller length of the outer side tapered roller row, and the number of rollers in the outer side tapered roller row is equal to the inner side cone. A bearing device for a wheel, characterized in that the number of rollers is set to be greater than the number of rollers in a roller train.
[7] 前記インナ一側の円錐ころ列のころ径と前記ァウタ一側の円錐ころ列のこ ろ径が同一に設定されている請求項 5または 6に記載の車輪用軸受装置。  7. The wheel bearing device according to claim 5, wherein a roller diameter of the inner side tapered roller array and a roller diameter of the outer side tapered roller array are set to be the same.
[8] 外周にナックルに取り付けられるための車体取付フランジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、  [8] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery,
—端部に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に 小径段部が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外 周に前記複列の外側転走面に対向する内側転走面が形成された少なくとも一 つの内輪からなる内方部材と、  -Hub wheel with a wheel mounting flange for mounting the wheel at the end, with a small diameter step formed on the outer periphery, and press-fitted into the small diameter step of this hub wheel, and the outer periphery of the double row on the outer periphery An inner member composed of at least one inner ring formed with an inner rolling surface facing the rolling surface;
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 円錐ころ列とを備えた車輪用軸受装置において、  In the wheel bearing device comprising the inner member and a double row tapered roller row accommodated so as to roll between both rolling surfaces of the outer member,
前記複列の円錐ころ列のうちインナ一側の円錐ころ列のピッチ円直径がァ ウタ一側の円錐ころ列のピッチ円直径よりも大径に設定されると共に、 前記 インナ一側の円錐ころ列のころ長さが前記アウター側の円錐ころ列のころ長 さよりも長く設定され、 かつ、 これらの円錐ころのころ径ぉよびころ個数が 同一に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 tapered roller row of the double row tapered roller row is set larger than the pitch circle diameter of the outer side tapered roller row, and the inner side tapered roller A roller bearing in which the roller length of the row is set longer than the roller length of the tapered roller row on the outer side, and the diameter of the roller and the number of rollers of these tapered rollers are set to be the same. apparatus.
[9] 外周にナックルに取り付けられるための車体取付フランジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 [9] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double-row outer rolling surface formed on the inner periphery,
—端部に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に 小径段部が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外 周に前記複列の外側転走面に対向する内側転走面が形成された少なくとも一 つの内輪からなる内方部材と、  -Hub wheel with a wheel mounting flange for mounting the wheel at the end, with a small diameter step formed on the outer periphery, and press-fitted into the small diameter step of this hub wheel, and the outer periphery of the double row on the outer periphery An inner member composed of at least one inner ring formed with an inner rolling surface facing the rolling surface;
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 円錐ころ列とを備えた車輪用軸受装置において、  In the wheel bearing device comprising the inner member and a double row tapered roller row accommodated so as to roll between both rolling surfaces of the outer member,
前記複列の円錐ころ列のピッチ円直径が同一に設定されると共に、 前記複 列の円錐ころ列のうちインナ一側の円錐ころ列のころ径がアウター側の円錐 ころ列のころ径よりも大径に設定され、 かつ、 これらの円錐ころ列のころ個 数が同一に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 diameters of the double row tapered roller rows are set to be the same, and the double row The roller diameter of the tapered roller row on the inner side of the row is set to be larger than the roller diameter of the outer tapered roller row, and the number of rollers in these tapered roller rows is set to be the same. A bearing device for a wheel, characterized in that
[10] 前記インナ一側の円錐ころ列のころ長さが前記アウター側の円錐ころ列の ころ長さよりも長く設定されている請求項 9に記載の車輪用軸受装置。  10. The wheel bearing device according to claim 9, wherein a roller length of the inner one side tapered roller row is set to be longer than a roller length of the outer side tapered roller row.
[11 ] 前記アウター側の円錐ころ列のころ長さが前記インナ一側の円錐ころ列の ころ長さよりも長く設定されている請求項 9に記載の車輪用軸受装置。  [11] The wheel bearing device according to claim 9, wherein a roller length of the outer side tapered roller row is set to be longer than a roller length of the inner one side tapered roller row.
[12] 外周にナックルに取り付けられるための車体取付フランジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、  [12] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;
—端部に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に 小径段部が形成されたハブ輪、 およびこのハブ輪の小径段部に圧入され、 外 周に前記複列の外側転走面に対向する内側転走面が形成された少なくとも一 つの内輪からなる内方部材と、  -Hub wheel with a wheel mounting flange for mounting the wheel at the end, with a small diameter step formed on the outer periphery, and press-fitted into the small diameter step of this hub wheel, and the outer periphery of the double row on the outer periphery An inner member composed of at least one inner ring formed with an inner rolling surface facing the rolling surface;
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 円錐ころ列とを備えた車輪用軸受装置において、  In the wheel bearing device comprising the inner member and a double row tapered roller row accommodated so as to roll between both rolling surfaces of the outer member,
前記複列の円錐ころ列のピッチ円直径が同一に設定されると共に、 前記複 列の円錐ころ列のうちアウター側の円錐ころ列のころ長さがインナ一側の円 錐ころ列のころ長さよりも長く設定され、 かつ、 これらの円錐ころ列のころ 個数が同一に設定されていることを特徴とする車輪用軸受装置。  The double-row tapered roller rows have the same pitch circle diameter, and the outer-side tapered roller row of the double-row tapered roller rows has a roller length of the inner one-side tapered roller row. The wheel bearing device is characterized in that the number of rollers of the tapered roller rows is set to be the same, and the number of rollers of these tapered roller rows is set to be the same.
[13] 前記アウター側の円錐ころ列のころ径と前記インナ一側の円錐ころ列のこ ろ径が同一に設定されている請求項 1 2に記載の車輪用軸受装置。 13. The wheel bearing device according to claim 12, wherein a roller diameter of the outer tapered roller array and a diameter of the inner tapered roller array are set to be the same.
[14] 外周にナックルに取り付けられるための車体取付フランジを一体に有し、 内周に複列の外側転走面が形成された外方部材と、 [14] An outer member integrally having a vehicle body mounting flange to be attached to the knuckle on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;
—端部に車輪を取り付けるための車輪取付フランジを一体に有し、 外周に この車輪取付フランジから軸方向に延びる小径段部が形成されたハブ輪、 お よびこのハブ輪の小径段部に圧入され、 外周に前記複列の外側転走面に対向 する内側転走面が形成された少なくとも一つの内輪からなる内方部材と、 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 円錐ころ列とを備えた車輪用軸受装置において、 —Hub wheel that has a wheel mounting flange for mounting the wheel at the end and has a small diameter step formed on the outer periphery extending in the axial direction from this wheel mounting flange, and press fit into the small diameter step of this hub ring An inner member formed of at least one inner ring having an inner race surface facing the outer race surface of the double row on the outer periphery, and between the inner race member and the outer member. Double row of rolls In a wheel bearing device having a tapered roller array,
前記複列の円錐ころ列のピッチ円直径が同一に設定され、 前記複列の円錐 ころ列のうちアウター側の円錐ころ列のころ径がィンナー側の円錐ころ列の ころ径よりも小径に設定されると共に、 前記アウター側の円錐ころ列のころ 個数が前記インナ一側の円錐ころ列のころ個数よりも多く設定され、 力、つ、 前記インナ一側の円錐ころ列のころ長さが前記アウター側の円錐ころ列のこ ろ長さよりも長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 double row tapered roller row is set to be the same, and the roller diameter of the outer side tapered roller row in the double row tapered roller row is set smaller than the roller diameter of the inner side tapered roller row. And the number of rollers in the outer side tapered roller train is set to be greater than the number of rollers in the inner side tapered roller train, and the force of the roller length of the inner side tapered roller train is A wheel bearing device characterized in that it is set longer than the length of the outer tapered roller row.
[15] 前記小径段部の端部を径方向外方に塑性変形させて形成した加締部により 前記内輪が軸方向に固定されている請求項 1乃至 1 4いずれかに記載の車輪 用軸受装置。  15. The wheel bearing according to any one of claims 1 to 14, wherein the inner ring is fixed in an axial direction by a crimping portion formed by plastically deforming an end portion of the small diameter step portion radially outward. apparatus.
[16] 前記ハブ輪の外周にアウター側の内側転走面が直接形成されると共に、 こ の内側転走面から軸方向に延びる前記小径段部が形成され、 この小径段部に 所定のシメシ口を介して前記インナ一側の内輪が圧入されている請求項 1乃 至 1 5いずれかに記載の車輪用軸受装置。  [16] An outer side inner rolling surface is directly formed on the outer periphery of the hub wheel, and the small-diameter step portion extending in the axial direction from the inner rolling surface is formed. The wheel bearing device according to any one of claims 1 to 15, wherein an inner ring on the inner side is press-fitted through a mouth.
[17] 前記ハブ輪の小径段部に一対の内輪が圧入され、 これらの内輪の内径が同 —に設定されている請求項 1乃至 1 6いずれかに記載の車輪用軸受装置。  17. The wheel bearing device according to any one of claims 1 to 16, wherein a pair of inner rings are press-fitted into the small-diameter step portion of the hub ring, and the inner diameters of these inner rings are set to be the same.
PCT/JP2007/001177 2006-10-26 2007-10-26 Bearing device for wheel WO2008050488A1 (en)

Applications Claiming Priority (16)

Application Number Priority Date Filing Date Title
JP2006-290916 2006-10-26
JP2006290915A JP2008106860A (en) 2006-10-26 2006-10-26 Bearing device for wheel
JP2006-290915 2006-10-26
JP2006290916A JP2008106861A (en) 2006-10-26 2006-10-26 Bearing device for wheel
JP2006300145A JP2008115954A (en) 2006-11-06 2006-11-06 Bearing device for wheel
JP2006-300146 2006-11-06
JP2006-300145 2006-11-06
JP2006300146A JP2008114733A (en) 2006-11-06 2006-11-06 Bearing device for wheel
JP2006348840A JP2008157394A (en) 2006-12-26 2006-12-26 Bearing device for wheel
JP2006-348840 2006-12-26
JP2006-352665 2006-12-27
JP2006352665A JP2008164005A (en) 2006-12-27 2006-12-27 Wheel bearing device
JP2007001674A JP2008169875A (en) 2007-01-09 2007-01-09 Wheel bearing device
JP2007001110A JP2008169859A (en) 2007-01-09 2007-01-09 Wheel bearing device
JP2007-001674 2007-01-09
JP2007-001110 2007-01-23

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WO2008050488A1 true WO2008050488A1 (en) 2008-05-02

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PCT/JP2007/001177 WO2008050488A1 (en) 2006-10-26 2007-10-26 Bearing device for wheel

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000002239A (en) * 1998-06-16 2000-01-07 Tochigi Fuji Ind Co Ltd Thrust bearing mechanism
JP2002295505A (en) * 2001-01-24 2002-10-09 Ntn Corp Bearing device of wheel
JP2004090732A (en) * 2002-08-30 2004-03-25 Ntn Corp Bearing device of driving wheel
JP2004108449A (en) * 2002-09-17 2004-04-08 Koyo Seiko Co Ltd Rolling bearing device
JP2004219161A (en) * 2003-01-10 2004-08-05 Nsk Ltd Instrument and method for measuring load of axle bearing of rolling stock
JP2004345439A (en) * 2003-05-21 2004-12-09 Honda Motor Co Ltd Wheel supporting hub unit

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000002239A (en) * 1998-06-16 2000-01-07 Tochigi Fuji Ind Co Ltd Thrust bearing mechanism
JP2002295505A (en) * 2001-01-24 2002-10-09 Ntn Corp Bearing device of wheel
JP2004090732A (en) * 2002-08-30 2004-03-25 Ntn Corp Bearing device of driving wheel
JP2004108449A (en) * 2002-09-17 2004-04-08 Koyo Seiko Co Ltd Rolling bearing device
JP2004219161A (en) * 2003-01-10 2004-08-05 Nsk Ltd Instrument and method for measuring load of axle bearing of rolling stock
JP2004345439A (en) * 2003-05-21 2004-12-09 Honda Motor Co Ltd Wheel supporting hub unit

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