WO2007125654A1 - Dispositif de palier pour roue motrice et son procedé de fabrication - Google Patents

Dispositif de palier pour roue motrice et son procedé de fabrication Download PDF

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Publication number
WO2007125654A1
WO2007125654A1 PCT/JP2007/000462 JP2007000462W WO2007125654A1 WO 2007125654 A1 WO2007125654 A1 WO 2007125654A1 JP 2007000462 W JP2007000462 W JP 2007000462W WO 2007125654 A1 WO2007125654 A1 WO 2007125654A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing device
drive wheel
wheel
hub
axial direction
Prior art date
Application number
PCT/JP2007/000462
Other languages
English (en)
Japanese (ja)
Inventor
Morihisa Yoshioka
Shigeaki Fukushima
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 JP2006121635A external-priority patent/JP2007290587A/ja
Priority claimed from JP2006121693A external-priority patent/JP2007290591A/ja
Priority claimed from JP2006121636A external-priority patent/JP2007290588A/ja
Priority claimed from JP2006147693A external-priority patent/JP2007315545A/ja
Priority claimed from JP2006160400A external-priority patent/JP2007326503A/ja
Priority claimed from JP2006164239A external-priority patent/JP2007331508A/ja
Application filed by Ntn Corporation filed Critical Ntn Corporation
Publication of WO2007125654A1 publication Critical patent/WO2007125654A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0015—Hubs for driven wheels
    • B60B27/0021—Hubs for driven wheels characterised by torque transmission means from drive axle
    • B60B27/0026—Hubs for driven wheels characterised by torque transmission means from drive axle of the radial type, e.g. splined key
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0015—Hubs for driven wheels
    • B60B27/0036—Hubs for driven wheels comprising homokinetic joints
    • B60B27/0042—Hubs for driven wheels comprising homokinetic joints characterised by the fixation of the homokinetic joint to the hub
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0094—Hubs one or more of the bearing races are formed by the hub
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • F16C35/0635—Fixing them on the shaft the bore of the inner ring being of special non-cylindrical shape which co-operates with a complementary shape on the shaft, e.g. teeth, polygonal sections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D1/108—Quick-acting couplings in which the parts are connected by simply bringing them together axially having retaining means rotating with the coupling and acting by interengaging parts, i.e. positive coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member

Definitions

  • the present invention relates to a drive wheel bearing device that rotatably supports a drive wheel of a vehicle such as an automobile. Specifically, the bearing unit and a constant velocity universal joint are detachably united. TECHNICAL FIELD The present invention relates to a bearing device for a drive wheel and a method for manufacturing the same, which suppresses circumferential rattling without strictly regulating the dimensions ⁇ , and achieves reliability and steering stability.
  • a power transmission device that transmits engine power of a vehicle such as an automobile to a wheel transmits power from the engine to the wheel, and in the radial direction from the wheel that is generated when the vehicle bounces on a rough road or when the vehicle turns. Therefore, one end of the drive shaft that is interposed between the engine side and the drive wheel side is differentially connected through a sliding type constant velocity universal joint. The other end is connected to a wheel via a drive wheel bearing device including a fixed type constant velocity universal joint.
  • This bearing device for a drive wheel includes a hub wheel 10 1 having a drive wheel (not shown) attached to one end thereof, a double row rolling bearing 10 2 that rotatably supports the hub wheel 1 0 1, and A fixed type constant velocity universal joint 103 connected to the hub wheel 1001 and transmitting the power of a drive shaft (not shown) to the hub wheel 101 is provided.
  • the hub wheel 1 0 1 integrally has a wheel mounting flange 1 0 4 for mounting a driving wheel at one end, an inner rolling surface 1 0 1 a on the outer periphery, and the inner rolling surface 1 0.
  • a cylindrical small-diameter step portion 1 0 1 b extending in the axial direction from 1 a is formed.
  • Double row rolling force ⁇ Re-bearing 10 2 has a body mounting flange 1 0 5 b integrally fixed to a suspension device (not shown) on the outer periphery, and double row outer rolling surface on the inner periphery 1 0 5 a, 1 0 5 a is The formed outer member 1 0 5 and the inner member 1 0 7 inserted into the outer member 1 0 5 through double rows of poles 1 0 6 and 1 0 6 are formed.
  • the inner member 1 0 7 is press-fitted into the hub wheel 1 0 1 and a small diameter step portion 1 0 1 b of the hub wheel 1 0 1, and an inner rolling surface 1 0 8 a is formed on the outer periphery. It consists of a separate inner ring 1 0 8. Then, the inner ring 1 0 with respect to the hub ring 1 0 1 is formed by a caulking part 1 0 1 c formed by plastically deforming the end of the small-diameter stepped portion 1 0 1 b of the hub ring 1 0 1 radially outward. 8 is fixed in the axial direction.
  • the constant velocity universal joint 1 0 3 includes a cup-shaped mouth portion 1 0 9, a shoulder portion 1 1 0 that forms the bottom of the mouth portion 1 0 9, and an axial direction extending from the shoulder portion 1 1 0
  • An outer joint member 1 1 2 is integrally provided with the shaft portion 1 1 1.
  • the outer joint member 1 1 2 is fitted into the hub wheel 1 0 1 so that torque can be transmitted. That is, a female spline 1 1 3 is formed on the inner periphery of the hub wheel 10 1, and a male spline 1 1 4 is formed on the outer periphery of the shaft portion 1 1 1 of the outer joint member 1 1 2. 1 3 and 1 1 4 are combined.
  • a locking step portion 1 1 5 is formed at the outer end portion of the inner peripheral surface of the hub wheel 1 0 1, and the tip end portion of the shaft portion 1 1 1 1 corresponding to the locking step portion 1 1 5
  • a locking groove 1 1 6 is formed in the locking groove 1 1 6, and a retaining ring 1 1 7 is attached to the locking groove 1 1 6 in advance.
  • the retaining ring 1 1 7 is aligned with the locking step 1 1 5 at the position where the axial clearance remains between the caulking portion 1 0 1 c and the shoulder portion 1 1 0 of the hub wheel 1 0 1. In this state, the diameter of the retaining ring 1 1 7 is elastically restored, and the retaining ring 1 1 7 can be spanned between the engaging step 1 1 5 and the engaging groove 1 1 6, and the hub wheel 1 0 1 and The outer joint member 1 1 2 is coupled so as to be separable in the axial direction.
  • a seal ring 1 1 8 is fitted on the shoulder 1 1 0 of the outer joint member 1 1 2, and the lip of this seal ring 1 1 8 abuts against the inner end face of the crimping portion 1 0 1 c, The clearance between the caulking 1 0 1 c and the shoulder 1 1 0 is closed.
  • the male spline 114 is a wide spline tooth whose width in the circumferential direction becomes wider toward the inner end side.
  • female spline 1 1 3 is outside Tapered spline teeth have a wider width in the circumferential direction toward the end. Then, as the male spline 1 1 4 is inserted into the female spline 1 1 3, the tooth surfaces are brought into close contact with each other and engaged in the circumferential direction without rattling.
  • a cap 1 1 9 serving as a closing member is attached to the opening of the hub wheel 10 1.
  • a circular through hole 1 19 a is formed at the center of the cap 1 19, and a screw hole 1 11 1 a is formed at the center of the outer end surface of the shaft 11 1 1.
  • the bolts 1 2 0 passed through the through holes 1 1 19 a are screwed into the screw holes 1 1 1 a and tightened.
  • both splines 1 1 3 and 1 1 4 can further prevent rattling of the circumferential direction of the engaging portion.
  • a large torque is loaded on the drive wheels of such a vehicle from the engine via a sliding type constant velocity universal joint (not shown) when the engine rotates at a low speed, for example, when the vehicle starts, and is twisted by the drive shaft. Is known to occur.
  • the inner members 10 7 of the double row rolling bearings 10 2 that support the drive shaft are also twisted.
  • the female spline 1 1 3 of the hub wheel 1 0 1 and the male spline of the shaft 1 1 1 fitted into the hub wheel 1 0 1 are here. Since the circumferential direction between 1 1 and 4 prevents rattling, it is possible to prevent the generation of harsh rattling noises over a long period of time.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2 00 2 _ 1 2 0 500
  • both the splines 1 1 3 and 1 1 4 are engaged in the shape of a one-pass spline tooth so that the circumferential direction of the engaging portion is not swayed. It has a feature that can prevent the generation of harsh rattling noises over a long period of time.
  • the male spline 1 1 4 of the shaft 1 1 1 is premised on, for example, finishing by rolling. It is difficult to form a corner, and the range of 0.75 to 1.25 ° is the limit. The smaller the taper angle, the more the variation in dimensional accuracy changes the axial engagement position of the male spline 1 1 4. As a result, the distance between the wheel mounting flange 1 0 4 and the center of the constant velocity universal joint 1 0 3 increases. This is not preferable in terms of the characteristics of the vehicle drive system.
  • the present invention has been made in view of such circumstances, and it is possible to reduce the cost by improving the workability during disassembly and assembly, and to eliminate the play in the circumferential direction of the engaging portion, thereby providing reliability. It is an object of the present invention to provide a drive wheel bearing device and a method for manufacturing the drive wheel device that achieves high performance and steering stability.
  • the present invention integrally includes an outer member having a double row outer rolling surface formed on the inner periphery, and a wheel mounting flange for mounting the wheel at one end.
  • a hub ring having a cylindrical small-diameter step portion extending in the axial direction on the outer periphery, and at least one inner ring press-fitted into the small-diameter step portion of the hub ring, and facing the outer rolling surface of the double row
  • An inner member formed with a double row inner raceway, a double row rolling element housed in a freely rollable manner between the two raceways, a constant velocity universal joint, and a screw on the hub wheel
  • An outer joint member that is detachably coupled in the axial direction via the means, the outer joint member comprising a cup-shaped mouth portion, a shoulder portion that forms the bottom portion of the mouth portion, and a shaft extending from the shoulder portion.
  • the shaft portion is connected to the hub wheel via a torque transmission means.
  • the torque transmission means corresponds to a fitting profile formed by arranging a plurality of convex teeth on the outer periphery of the shaft portion, and the fitting profile, Hub ring And a fitting profile formed by arranging a plurality of concave grooves that engage with the convex teeth on the inner periphery of the inner periphery of the convex teeth, and the tooth surfaces of the convex teeth and the concave grooves have a predetermined pressure angle, In addition, a predetermined inclination angle is formed in the axial direction with respect to the shaft center. ⁇ ⁇ ⁇ Claim 1
  • the hub wheel integrally having the wheel mounting flange at one end, the double row rolling bearing and the constant velocity universal joint are detachably united via the screw means, and the like.
  • the torque transmission means includes a fitting profile formed by arranging a plurality of convex teeth on the outer periphery of the shaft portion, and this fitting And a fitting profile formed by arranging a plurality of concave grooves that engage with the convex teeth on the inner periphery of the hub wheel, and the tooth surfaces of the convex teeth and the concave grooves are at a predetermined pressure.
  • the cross section of the concave groove is formed in a hollow groove shape and the cross section of the convex groove is formed in a substantially trapezoidal shape.
  • the pressure angle at the tooth surfaces of the convex teeth and the concave grooves is set in a range of 0 to ⁇ 30 °, it is related to the expansion amount of the hub wheel during torque transmission. An increase in the separating force generated at the joint can be effectively suppressed.
  • the inclination angle of the tooth surfaces of the convex teeth and the concave grooves is set in the range of 2 to 7 °, the combined tolerance width of the tooth surfaces is suppressed to ⁇ 1 mm or less. It is possible to secure an axial clearance between the shoulder portion and the end surface of the caulking portion. ⁇ ⁇ ⁇ Claim 4
  • the inner ring is fixed in the axial direction with respect to the hub ring by a crimping portion formed by plastically deforming an end portion of the small-diameter stepped portion radially outward.
  • a predetermined axial clearance is interposed between the shoulder portion and the end surface of the caulking portion.
  • an axial clearance between the shoulder portion and the end surface of the caulking portion is
  • the axial clearance can be secured even if the inclination angle of convex teeth and concave grooves in the fitting profile varies, and even if a large torque is applied to the outer joint member and twisting occurs. There is no stick-slip noise. ⁇ ⁇ ⁇ Claim 6
  • an elastic ring is interposed between the caulking portion and the shoulder portion, and an opening portion of the annular space formed between the caulking portion and the shoulder portion is closed. If this is the case, rainwater, dust, etc. from entering the engaging parts of the convex teeth and grooves are prevented from outside, and the engaging parts are prevented from sticking due to bruising, thereby improving disassembly workability during repair. be able to. ⁇ ⁇ ⁇ Claim 7
  • the projection It is possible to prevent foreign matter such as rainwater and dust from entering the engaging portions of the teeth and the concave grooves, and to prevent the engaging portions from generating for a long period of time.
  • the disassembly workability at the time of repair can be improved.
  • the caulking portion can be prevented from generating.
  • a predetermined strength can be secured, and the initially set preload can be maintained over a long period of time.
  • a predetermined hardened layer may be formed in the range of 58 to 64 HRC by induction hardening from the shoulder portion to the convex teeth of the shaft portion. For example, it is possible to reduce the weight by improving the strength of the engaging part with the groove while suppressing the combined tolerance width of the engaging part due to heat treatment deformation, and to improve the wear resistance, for a long time Durability can be ensured. ⁇ ⁇ ⁇ Claim 1 0
  • the present invention integrally includes an outer member having a double row outer rolling surface formed on the inner periphery, and a wheel mounting flange for mounting the wheel on one end, and the outer periphery in the axial direction.
  • a hub ring formed with an extending cylindrical small-diameter step portion, and at least one inner ring press-fitted into the small-diameter step portion of the hub ring, the double-row inward rolling facing the double-row outer raceway
  • An outer joint member that is detachably coupled to the hub wheel in the axial direction via screw means, and the outer joint member includes a cup-shaped mouth portion and a shoulder portion that forms the bottom of the mouse portion.
  • a shaft portion extending in the axial direction from the shoulder portion is integrally formed, and this shaft portion is a torque transmitting hand to the hub wheel.
  • a first male screw is formed at the end of the shaft portion, and a second male screw is formed on one outer side of the first male screw.
  • the first male screw and the second male screw are set to different screw specifications, and the first nut is fastened to the first male screw with a predetermined tightening torque, and the first male screw is in contact with the first nut.
  • a second nut is fastened to the second male screw.
  • the hub ring integrally having the wheel mounting flange at one end, the double row rolling bearing and the constant velocity universal joint are detachably united via the screw means, and the like.
  • the first male screw is formed at the end of the shaft portion, and the second male screw is formed on the outer side of the first male screw,
  • These first and second male screws are set to different screw specifications, and the first nut is fastened to the first male screw with a predetermined tightening torque, and the first male screw is in contact with the first nut.
  • the second nut ⁇ is fastened to the male screw of 2, the difference in the frictional force of the contact surface and the screw specifications
  • the first nut can be effectively prevented from loosening, and the first nut can be fastened with the minimum necessary axial force, preventing loosening over a long period of time and improving reliability. It is possible to provide a bearing device for a drive wheel that achieves steering stability.
  • the outer diameter of the second male screw is set to be smaller than the root diameter of the first male screw, and the pitch of the second male screw is the first male screw. If both nuts are tightened with the same tightening torque, the axial force due to tightening will be reduced by the increase in the pitch of the first nut ⁇ , and this will be applied to the torque transmission means. The accompanying expansion of the hub ring can be suppressed. ⁇ ⁇ ⁇ Claim 1 3
  • the present invention relates to a fitting profile in which the torque transmission means is formed by arranging a plurality of convex teeth on the outer periphery of the shaft portion, and corresponds to the fitting profile. And a fitting profile formed by arranging a plurality of groove-shaped concave grooves that engage with the convex teeth, and the convex teeth have a predetermined negative pressure angle. If it is formed in a trapezoidal shape and a predetermined inclination angle is formed in the axial direction with respect to the shaft center on the tooth surface, even if the pressure angle of the fitting profile is positive, it is excessive due to expansion of the inner member. Hoop stress can be suppressed. ⁇ ⁇ ⁇ Claim 1 4
  • the torque transmission means is formed on the outer periphery of the shaft portion, and includes a selection formed of a teno-shaped bus bar that gradually decreases in diameter toward the outer side of the shaft, and is engaged with the selection.
  • a selection formed on the inner periphery of the hub wheel it eliminates the backlash in the circumferential direction of the connecting portion, and does not require a special dedicated jig such as a power press as in the prior art.
  • the outer joint member can be easily pulled into the hub wheel simply by tightening the first nut into the first male thread of the part. Therefore, the workability during disassembly and assembly can be improved and the cost can be reduced. it can . ⁇ ⁇ ⁇ Claim 1 5
  • the method invention of the present invention integrally includes an outer member having a double row outer rolling surface formed on the inner periphery, and a wheel mounting flange for mounting the wheel at one end.
  • a hub ring formed with a cylindrical small-diameter step portion extending in the axial direction on the circumference, and at least one inner ring press-fitted into the small-diameter step portion of the hub ring.
  • a process for forming a mating profile with multiple teeth and the corresponding mating profile Forming a fitting profile in which a plurality of concave grooves having a cross-sectional groove shape engaging with the convex teeth are formed on the inner periphery of the hub wheel, and the inner periphery of the hub wheel.
  • the upper surface is formed by forging, and a square spline-shaped pilot hole of an axial streak is formed by a predetermined processing method.
  • vibration press processing A predetermined pressure angle and a predetermined inclination angle are formed in the axial direction with respect to the shaft center.
  • a front shape is formed on the outer periphery of the shaft portion by forging or rolling, and a tapered surface is formed by a die, and thereafter, the convex portion is formed by a mechanical processing means. If the teeth are formed in a substantially trapezoidal cross section, the material yield is improved and the machining cost can be reduced by shortening the machining time. ⁇ ⁇ ⁇ Claim 1 7
  • a double-row outer rolling surface is formed on the inner periphery.
  • An outer member, and a hub wheel having a wheel mounting flange for mounting a wheel at one end, and a cylindrical small-diameter step portion extending in the axial direction on the outer periphery, and a small-diameter step portion of the hub ring
  • An inner member formed of at least one inner ring press-fitted into the inner surface and formed with a double row inner rolling surface facing the double row outer rolling surface, and accommodated in a freely rollable manner between the two rolling surfaces.
  • the drive wheel bearing device according to claim 1, wherein the torque transmission means comprises the shaft.
  • a fitting profile formed by arranging a plurality of convex teeth on the outer periphery of the hub, and a plurality of concave grooves corresponding to the fitting profile and engaging the convex teeth on the inner circumference of the hub wheel.
  • the tooth surfaces of the convex teeth and the concave grooves have a predetermined pressure angle, and a predetermined inclination angle is formed in the axial direction with respect to the axial center.
  • No pressure input is required, and it is possible to easily obtain a strong fitting state without backlash in the circumferential direction at the final stage of insertion, and the diameter generated in the engaging portion of the convex teeth and the concave groove during torque transmission The component force outside the direction can be suppressed, and the bearing clearance is not adversely affected.
  • the drive wheel bearing device integrally includes an outer member having a double row outer raceway formed on the inner periphery, and a wheel mounting flange for mounting the wheel at one end.
  • a hub ring formed with a cylindrical small-diameter step portion extending in the axial direction on the outer periphery, and at least one inner ring press-fitted into the small-diameter step portion of the hub ring,
  • an outer joint member that is separably coupled to the hub wheel in the axial direction via screw means, the outer joint member comprising a cup-shaped mouth portion and a shoulder portion that forms the bottom of the mouth portion And a shaft portion extending in the axial direction from the shoulder portion.
  • a first male screw is formed at the end of the shaft portion, and a second male screw is formed on the outer side of the first male screw.
  • the male screw is set to a different screw specification, and the first nut is fastened to the first male screw with a predetermined tightening torque, and the second male screw is connected to the second male screw until it comes into contact with the first nut. Since the nuts of 2 are fastened, the first nut can be effectively prevented from loosening due to the difference in the frictional force of the contact surface and the screw specifications, and the first nut is minimized. It is possible to provide a bearing device for a drive wheel that can be fastened with an axial force of the same, prevents loosening for a long period of time, and achieves reliability and steering stability.
  • the method for manufacturing a drive wheel bearing device includes an outer member having a double row outer raceway formed on the inner periphery, and a wheel mounting flange for mounting a wheel at one end. And a hub ring having a cylindrical small-diameter step portion extending in the axial direction on the outer periphery, and at least one inner ring press-fitted into the small-diameter step portion of the hub ring, and facing the double row outer rolling surface
  • An outer joint member that is detachably coupled in the axial direction via a screw means.
  • the outer joint member includes a cup-shaped mouth portion, a shoulder portion that forms the bottom portion of the mouth portion, and a shaft extending from the shoulder portion.
  • the body has a shaft portion extending in the direction, and the shaft portion provides torque to the hub wheel.
  • a vehicle body mounting flange is integrally formed on the outer periphery, an outer member having a double row outer rolling surface formed on the inner periphery, a wheel mounting flange is integrally formed on one end, and One inner rolling surface facing the outer rolling surface of the row, a hub ring formed with a cylindrical small diameter step portion extending in the axial direction from the inner rolling surface, and press-fitted into the small diameter step portion of the hub ring
  • An inner member comprising an inner ring formed on the outer periphery with the other inner rolling surface facing the outer rolling surface of the double row, and a double row accommodated in a freely rolling manner between the two rolling surfaces.
  • the inner ring is fixed in the axial direction by a caulking portion formed by plastic deformation of the outer joint member, and the outer joint member is A cup-shaped mouse portion, a shoulder portion that forms the bottom portion of the mouse portion, and a shaft portion that extends in the axial direction from the shoulder portion, and is provided between the shoulder portion and the end surface of the crimping portion.
  • the torque transmission means has a substantially trapezoidal cross section on the outer periphery of the shaft portion.
  • a fitting profile formed by arranging a plurality of convex teeth equally, and a plurality of concave grooves having a cross-sectional groove shape engaging with the convex teeth on the inner periphery of the hub ring, etc.
  • the tooth surfaces of the convex teeth and the concave grooves have a predetermined negative pressure angle, and a predetermined inclination angle is formed in the axial direction with respect to the shaft center.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a bearing device for a drive wheel according to the present invention
  • FIG. 2 (a) is a front view showing a fitting profile of the shaft portion of FIG. 1, and (b) is (A) is a cross-sectional view taken along line II-II, (c) is an explanatory diagram showing the difference in shape when the pressure angle of the fitting profile is negative and positive
  • FIG. Fig. 4 shows the amount of expansion of the hub wheel with respect to the pressure angle and the separation generated in the engaging part.
  • FIG. 5 is a graph showing the amount of expansion of the hub wheel with respect to the inclination angle and the separation force generated in the engaging portion.
  • the side closer to the outer side of the vehicle in the state assembled to the vehicle is referred to as the outer side (left side of the drawing), and the side closer to the center is referred to as the inner side (right side of the drawing).
  • This drive wheel bearing device has a so-called third generation configuration in which the hub wheel 1, the double row rolling bearing 2 and the constant velocity universal joint 3 are detachably mounted.
  • the double-row rolling bearing 2 includes an outer member 7, an inner member 8, and double-row rolling elements (balls) 9 and 9.
  • the outer member 7 is made of medium and high carbon steel containing carbon 0.40 to 0.8 O wt%, such as S 53 C, and has a vehicle body mounting flange 7 b for mounting to the vehicle body (not shown) on the outer periphery.
  • vehicle body mounting flange 7 b for mounting to the vehicle body (not shown) on the outer periphery.
  • double row outer rolling surfaces 7 a and 7 a are formed on the inner periphery.
  • the double row outer rolling surfaces 7a and 7a are subjected to a hardening treatment in a range of 5 8 to 64 4 H R C by induction hardening.
  • the inner member 8 is formed with double row inner rolling surfaces 1a, 5a opposite to the outer rolling surfaces 7a, 7a of the outer member 7 described above.
  • double-row inner raceway surfaces 1a and 5a one (outer side) inner raceway surface 1a is on the outer periphery of hub wheel 1, and the other (inner side) inner raceway surface 5a is inner ring 5.
  • the inner member 8 refers to the hub wheel 1 and the inner ring 5.
  • the double row rolling elements 9 and 9 are respectively accommodated between the rolling surfaces and held by the cages 10 and 10 so as to freely roll. Seals 11 and 12 are attached to the opening of the annular space formed between the outer member 7 and the inner member 8, and leakage of lubricating grease sealed inside the bearing can be prevented. It prevents rainwater and dust from entering the bearing.
  • the hub wheel 1 is integrally provided with a wheel mounting flange 4 for mounting a wheel (not shown) at an end portion on the outer side, and the wheel is fixed to the circumferential direction of the wheel mounting flange 4 at equal intervals.
  • Hub bolt 4a is installed. Then, on the outer periphery, the inner rolling surface 1 a via the seal land portion 13 that becomes the base of the wheel mounting flange 4, and this A cylindrical small-diameter step portion 1 b extending in the axial direction from the inner rolling surface 1 a is formed.
  • the inner ring 5 is press-fitted into the small-diameter step portion 1b through a predetermined squeeze opening, and further, a crimping portion 6 formed by plastically deforming an end portion of the small-diameter step portion 1b radially outward. Fixed to the hub wheel 1 in the axial direction with bearing preload applied.
  • the hub wheel 1 is made of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and the inner ring 1 is rotated inward from the seal land portion 13 where the outer seal 11 is in sliding contact.
  • the outer peripheral surface over the running surface 1a and the small diameter step 1b is hardened by induction hardening in the range of 58 to 64 HRC (indicated by cross-hatching in the figure). Note that the caulking portion 6 remains the surface hardness after forging.
  • Inner ring 5 and rolling element 9 are made of high carbon chrome bearing steel such as SU J 2 and are hardened in the range of 58 to 64 HR C to the core part by quenching.
  • the third generation structure in which the inner raceway surface 1a is directly formed on the outer periphery of the hub wheel 1 is illustrated.
  • the present invention is not limited to this, but a pair of inner rings are press-fitted into the hub wheel. It may be a first or second generation structure.
  • the configuration including the double row angular contact ball bearing using the pole for the rolling element 9 is illustrated, but a double row tapered roller bearing using the tapered roller for the rolling element 9 may be used.
  • the constant velocity universal joint 3 includes an outer joint member 14, a joint inner ring 15, a cage 16 and a torque transmission ball 17.
  • the outer joint member 14 has a cup-shaped mouth portion 18, a shoulder portion 19 that forms the bottom of the mouth portion 18, and a shaft portion 20 that extends in the axial direction from the shoulder portion 19. Curved track grooves 18 a and 15 a extending in the axial direction are formed on the inner periphery of the mouse portion 18 and the outer periphery of the joint inner ring 15, respectively.
  • the outer joint member 14 is made of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 5 3 C, and the shoulder portion 1 9 including track grooves 1 8 a and 15 a. Surface hardness by induction hardening on the outer peripheral surface extending from the shaft 20 to 58 Hardened in the 64 H RC range.
  • the shaft portion 20 of the outer joint member 14 is constituted by a short shaft, and a female screw 20a is formed at the outer end portion.
  • the fitting profile 21 is formed on the outer periphery so that the convex teeth 21a force ⁇ plurality (3 to 10) are equally distributed.
  • the convex tooth 21 a is formed into a substantially trapezoidal cross section by machining such as an end mill described later, has a predetermined pressure angle, and has a predetermined inclination angle / in the axial direction with respect to the axial center of the tooth surface. S is formed.
  • a plurality of fitting profiles 22 with a plurality of grooves 22 a force corresponding to the fitting profile 21 a are formed on the inner periphery of the hub wheel 1, a plurality of fitting profiles 22 with a plurality of grooves 22 a force corresponding to the fitting profile 21 a are formed.
  • the concave groove 22a is formed into a groove shape by a forging process, which will be described later, and has a predetermined pressure angle corresponding to the convex tooth 21a.
  • a predetermined inclination angle / S is formed in the axial direction.
  • the graph shown in FIG. 4 shows the force indicating the expansion amount of the hub wheel 1 and the separation force generated in the engagement portion with respect to the pressure angle during torque transmission, with the axial force and torque being constant.
  • the pressure angle of the tooth 21a and the concave groove 22a is set in the range of ⁇ 30 ° where both the expansion and separation force do not increase.
  • the pressure angle is set in a negative region, that is, in a range of 0 to 1-30 °
  • the cross-sectional shape of the concave groove 22a in the hub wheel 1 becomes a groove shape, and the hub wheel 1 Expansion can be effectively suppressed.
  • the definition of pressure angle is as shown in Fig. 2 (c), where the convex tooth 2 1a goes outward in the circumferential direction and the tooth width increases, and the reverse (minus 0).
  • the state in which the tooth width decreases is positive ( ⁇ > 0).
  • the graph shown in FIG. 5 shows a force convexity indicating the expansion amount of the hub wheel 1 with respect to the inclination angle / S during torque transmission and the separation force generated in the engaging portion, with the axial force and torque being constant.
  • the inclination angle of the teeth 21a and the concave grooves 22a; 8 is set in the range of 2 to 7 °, preferably 3 to 6 °, in which both the expansion amount and the separation force do not increase.
  • the module m is set to 3 to 10 in consideration of the strength and economics of the convex teeth 21a and the concave grooves 22a (approximately 3 to 10 teeth).
  • m dZz (d: average diameter in the axial radial direction of the fitting profile, z: number of teeth or grooves).
  • the surface hardness of the outer joint member 14 from the shoulder portion 19 to the convex portion 2 1 a of the shaft portion 20 is increased to a predetermined hardness within a range of 58 to 64 HRC by high frequency quenching.
  • Layer 26 is formed (indicated by cross-hatching in the figure).
  • the surface hardness of the recessed groove 2 2a of the fitting profile 2 2 in the hub wheel 1 that engages with the convex tooth 2 1a is set to a predetermined hardness within the range of 58 to 64 HRC by high-frequency quenching.
  • Layer 27 is formed (indicated by cross-hatching in the figure).
  • the weight of the engaging portion between the convex tooth 21a and the concave groove 22a can be improved, the weight can be reduced, and the wear resistance can be improved, and the durability can be ensured over a long period of time.
  • the hardened surface of both the convex tooth 2 1 a and the concave groove 2 2 a is not hardened, so that only the convex tooth 2 1 a is hardened, thereby reducing the combined tolerance width of the engaging portion due to heat treatment deformation.
  • the axial clearance S between the shoulder portion 19 and the end surface of the crimping portion 6 can be secured.
  • the shaft portion 20 of the outer joint member 14 is such that a predetermined axial clearance S is interposed between the shoulder portion 19 and the end surface of the crimping portion 6. It is fitted to the hub wheel 1 through the fitting plug files 2 1 and 2 2, and the fastening port 2 4 is screwed to the female screw 2 0 a of the shaft portion 2 0 through the washer 2 3, 1 and the outer joint member 1 4 are coupled in an axially separable manner.
  • the axial clearance (5 is set to 1 mm or more from the combined tolerance width of the convex tooth 2 1 a and the concave groove 2 2 a.
  • the washer 2 3 has a coating film, rubber, etc. Sealing layer 2 3a made of elastomer is coated, which improves the sealing performance at the contact portion between the hub wheel 1 and the washer 23.
  • the convex teeth 2 1a and the concave grooves 2 in which the fitting profiles 2 1 and 2 2 have a predetermined pressure angle and a predetermined inclination angle / S is formed in the axial direction with respect to the shaft center. 2 Since each is composed of a, it does not require excessive pressure input and can be easily inserted. In the final stage, it is possible to obtain a strong fitting state with no circumferential play, and the radially outward component force generated at the engaging portion of the convex tooth 21a and the concave groove 22a during torque transmission Can be suppressed and the bearing clearance is not adversely affected.
  • the bearing preload can be maintained for a long time without firmly tightening the fastening bolts 2 4, and a large torque is applied to the outer joint member 14, which is twisted. Even if it occurs, there will be no sweet slip noise.
  • annular groove 19 a is formed on the outer periphery of the shoulder portion 19, and an elastic ring comprising an O-ring or the like is formed in the annular groove 19 a.
  • the opening portion of the annular space formed between the shoulder portion 19 and the caulking portion 6 is liquid-tightly closed.
  • FIG. 6 is a diagram showing the shape of the hub wheel after forging
  • (b) is a longitudinal cross-sectional view of the hub wheel
  • (a) is a cross-sectional view taken along line A_A of (b).
  • Fig. 7 shows the shape of the hub wheel after broaching.
  • (B) is a longitudinal cross-sectional view of the hub ring
  • (a) is a cross-sectional view taken along line B_B of (b).
  • FIG. 8 is a view showing the shape of the hub wheel after broaching, where (a) is a top view of the fitting profile portion, and (b) is a longitudinal sectional view of the fitting profile portion.
  • FIG. 9 is a diagram showing an outline of the vibration press apparatus.
  • (A) shows a state before press working, and (b) shows a state during press working.
  • FIG. 10 is a view showing a longitudinal sectional view of the fitting profile portion after the vibration press processing.
  • Fig. 11 is an end view of the mating profile part after vibration press processing.
  • (A) is a diagram of Fig. 10 End view along line D_D,
  • (b) is an end view along line E—E in FIG. 10, and
  • (c) is an end view along line FF in FIG.
  • Fig. 12 shows the shape of the hub wheel after vibration press.
  • (B) is a longitudinal cross-sectional view of the hub wheel, and (a) is a cross-sectional view along line C_C of (b).
  • FIG. Fig. 13 is a diagram showing the gap formed in the shaft and hole of the fitting profile.
  • the forging process is performed so that the paper surface 2 2 b is formed on the portion of the hub wheel 1 ′ where the fitting profile 2 2 is formed.
  • the upper surface 2 2 b has a large diameter on the inner side (upper side in the figure), and the escape of meat due to the vibration press processing performed later is considered.
  • a rectangular spline-like concave groove 22 c of the axial tray rod is formed by a broach cutter or the like.
  • the concave groove 2 2 c has a negative pressure angle and has a cross-sectionally groove shape.
  • the pressure angle is set in a range of 0 to ⁇ 30 °. At this stage, the pressure angle is formed, but the predetermined inclination angle is not formed in the axial direction with respect to the shaft center.
  • the vibration press machine has, for example, the principle shown in Japanese Patent No. 3 5 7 2 5 4 4.
  • the vibration press working machine used in the manufacturing method of the present invention includes a slide part 28 that slides up and down, a punch 29 provided at the lower end of the slide part 28, and a work table.
  • the cradle 30 is placed on the cradle.
  • the slide unit 28 is a frequency generation device that generates vibration at a predetermined frequency.
  • the slide portion 28 is provided with a lubricant supply unit 31 that supplies lubricant to the processing portion of the punch 29 from the outside.
  • a convex part 29a inclined by a predetermined inclination angle; 8 in the axial direction with respect to the axial center is formed.
  • a hub wheel 1 ' which is a workpiece, is placed on the cradle 30.
  • a work presser 3 2 that holds and holds the work.
  • the slide part 28 is lowered while the convex part 29a of the punch 29 is vibrated at a predetermined frequency.
  • the tilt angle is set in the range of 2 to 7 °.
  • the inner periphery of the hub wheel 1 ′ is formed with a concave groove 22 a force ⁇ plurality of fitting profiles 22 arranged in plurality. Yes. Since the side surface of the groove 2 2 a is inclined by a predetermined inclination angle / S, the circumferential direction of the groove 22 a in each of the cross sections D_D, E_E, and F_F in FIGS. The width is gradually reduced. In addition, the side surface of the groove 22a is moved with the plastic working by the vibration press as shown in the enlarged upper right part of FIGS. 11 (a) and 11 (b). That is, when the vibration pressing process is performed, convex portions 22 d are formed in which both side surfaces of the concave grooves 22 a are raised inward in the circumferential direction.
  • FIG. 13 shows a state where the convex teeth 2 1 a of the fitting profile 21 and the concave grooves 22 a of the fitting profile 22 are fitted.
  • This clearance can be used for the relief of the convex part 22d by the vibration press process shown in Fig. 11. Thus, interference other than the fitting surface can be avoided.
  • Fig. 14 (a) is a front view of the mating profile 21. (b) is an X of (a).
  • This fitting profile 21 is cut by an end mill 45 on the outer periphery of the shaft portion 20 to form convex teeth 21 having a substantially trapezoidal cross section. .
  • a shaft-shaped front shape is formed on the outer periphery of the shaft portion 20 by forging or rolling in advance, and then the inner diameter is increased by a die.
  • a paper surface may be formed.
  • the end of the end mill 45 is shaped so that the pressure angle of the convex tooth 21a becomes a predetermined value in the range of 0 to 1-30 °. In this way, while processing the side surface of the convex tooth 21a with the pressure angle, as shown in Fig. 14 (a), the end mill 45 is moved in a direction shifted by an angle 8 in the axial direction, thereby forming the convex tooth. 2 1 a inclination angle; 8 is formed.
  • the pressure angle and inclination angle of convex teeth 2 1 a Can be formed at the same time by moving the steel 45, so the processing method is simple.
  • FIG. 15 (a) is a longitudinal sectional view showing a second embodiment of the drive wheel bearing device according to the present invention, and (b) is an enlarged view of the main part of (a).
  • This embodiment is basically the same as the first embodiment (FIG. 1) described above except that the fastening portion and the sealing structure are different, and other parts having the same parts or similar functions have the same reference numerals. The detailed description is omitted.
  • This drive wheel bearing device has a configuration called a third generation in which the hub wheel 1, the double row rolling bearing 2 and the constant velocity universal joint 3 3 are detachably united as in the embodiment described above. I am doing.
  • the shaft portion 20 of the outer joint member 3 4 in the constant velocity universal joint 3 3 is composed of a short shaft, and a convex tooth 2 1 a and a plurality of equally-fitted fitting profiles 21 are formed on the outer periphery. .
  • a male screw 35 is projected from the end of the shaft 20, and a predetermined axial clearance S is interposed between the shoulder 36 and the end face of the crimping portion 6.
  • the shaft portion 20 of 4 is fitted to the hub wheel 1 through the fitting profiles 2 1 and 2 2, and the fixing nut 3 7 is screwed to the male screw 3 5 of the shaft portion 20,
  • the outer joint member 34 is coupled to the outer joint member 34 in an axially separable manner.
  • An end cap 3 8 is attached to the end of the hub wheel 1 on the one side of the counter, and the hub wheel 1
  • the shoulder 3 6 and the caulking portion 6 are metal-fitted (circled in the figure), and the shoulder 3 6 and the caulking portion are closed.
  • the opening of the annular space formed between the two is closed.
  • the caulking portion 6 is prevented from being blown. Ensure the specified strength and maintain the initially set bearing preload for a long period of time. Can do.
  • FIG. 16 is a longitudinal sectional view showing a third embodiment of the drive wheel bearing device according to the present invention
  • FIG. 17 is an explanatory view showing a fastening portion of the shaft portion of the outer joint member. Note that this embodiment is basically different from the second embodiment (FIG. 15) described above except that the fastening portion 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 drive wheel bearing device has a so-called third generation configuration in which the hub wheel 1, the double row rolling bearing 2 and the constant velocity universal joint 39 are detachably unitized. .
  • the shaft portion 20 of the outer joint member 40 is constituted by a short shaft, and the first male screw 4 1 is formed at the outer end portion, and the second male screw 42 is formed at the outer side. ing.
  • the outer diameter D o of the second male thread 4 2 is smaller than the root diameter di of the first male thread 4 1 (D o ⁇ di), as shown in FIG.
  • the second male screw 4 2 and the first male screw 4 1 are set to different pitches (Po ⁇ P i). Therefore, when the second nut 4 4 fastened to the second male screw 42 is brought into contact with the first nut 43, the friction force of the contact surface and the difference between the pitches Po and Pi cause the first nut It is possible to effectively prevent the nut 1 4 3 from loosening.
  • the first nut 4 3 can be fastened with the minimum necessary axial force, eliminating the backlash in the circumferential direction of the joint, and preventing looseness over a long period of time, thereby improving reliability and steering stability.
  • the intended wheel bearing device can be provided.
  • the locking effect can be further strengthened by forming an engagement groove such as a face spline on the contact surface of the first nut and the second nut.
  • both nuts can be used with the same tightening torque.
  • the axial force due to fastening with a large pitch Pi of the first nut 4 3 is reduced. That is, the expansion of the hub wheel 1 accompanying the application of the axial force to the fitting profiles 2 1 and 2 2 can be suppressed.
  • FIG. 18 (a) is a longitudinal sectional view showing a fourth embodiment of the drive wheel bearing device according to the present invention, and (b) is an enlarged view of the main part of (a).
  • This embodiment is basically different from the third embodiment described above (FIG. 16) except that the torque transmission means is different, and other parts having the same parts or parts having the same functions are denoted by the same reference numerals. Detailed description will be omitted.
  • This drive wheel bearing device is referred to as the third generation in which the hub wheel 46, the double row rolling bearing 47 and the constant velocity universal joint 48 are detachably united as in the above-described embodiment.
  • the structure is made.
  • the double row rolling bearing 4 6 includes an outer member 7, an inner member 4 9, and double row rolling elements 9 and 9.
  • the inner member 4 9 indicates the hub wheel 4 6 and the inner ring 5, and the hub wheel 4 6 has an inner rolling surface 1a on the outer periphery and a cylindrical shape extending in the axial direction from the inner rolling surface 1a.
  • a small-diameter step portion 1 b is formed, and an inner ring 5 is press-fitted into the small-diameter step portion 1 b.
  • a selection (or spline) 50 is formed on the inner periphery, which is composed of a single / shaped bus bar that gradually decreases in diameter toward the outer side.
  • a shoulder 51 is formed at the end of the selection 50 on the small diameter side.
  • the hub ring 46 is made of medium carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and the inner side from the seal land 13 to which the outer seal 11 is in sliding contact.
  • the outer peripheral surface extending over the rolling surface 1a and the small diameter step 1b is hardened by induction hardening to a surface hardness in the range of 58 to 64 HRC.
  • the shaft portion 5 4 protrudes from the shoulder portion 5 3 of the outer joint member 52 in the constant velocity universal joint 48, and engages with the selection 50 of the hub wheel 46 on the outer periphery of the shaft portion 54.
  • a serration (or spline) 5 5 is formed.
  • This selection 55 is formed in a taper shape in which the generatrix gradually becomes smaller in diameter toward the outer side (end). Also, at the end is the first male screw 5 6 consisting of a right-hand thread and the left A second male screw 57 made of a screw is formed by rolling.
  • the shaft portion 5 4 of the outer joint member is a selection 50 0, 5 5 so that a predetermined axial clearance S is interposed between the shoulder portion 5 3 of the outer joint member 52 and the end surface of the crimping portion 6.
  • the first nut 5 8 which is fitted to the hub wheel 4 6 through the shoulder portion 5 1 of the hub wheel 4 6 with a right-hand thread, is tightened to the first male screw 5 6 of the shaft portion 5 4 with a predetermined tightening.
  • the second nut 59 which is composed of a left-hand screw, is fastened to the second male screw 57, and the hub wheel 46 and the outer joint member 52 are connected in the axial direction. They are separable.
  • a screw means such as a nut is used.
  • the inner member 49 the hub ring 46 and the inner ring 5
  • the shaft part 54 may expand, and an excessive hoop stress may occur.
  • the axial force that is, the tightening torque of the nut or the like is suppressed to the minimum necessary to suppress the hoop stress, the nut or the like is loosened and play occurs at the joint, which is not preferable.
  • the first male screw 5 6 and the second male screw 5 7, which are opposite to each other, are formed at the end of the shaft portion 54, and the first and second nuts 5 are formed in these. Since 8 and 59 are fastened with a predetermined tightening torque, the second nut 59 can effectively prevent the first nut 58 from loosening. As a result, the first nut 58 can be fastened with the minimum necessary axial force, eliminating looseness in the circumferential direction of the joint and preventing looseness over a long period of time, and reliability and handling stability. It is possible to provide a wheel bearing device that achieves the above.
  • a special special jig such as a conventional part press is not required, and the outer joint member 5 2 can be attached only by tightening the first nut 5 8 to the first male screw 5 6 of the shaft part 54. Since it can be easily pulled into the hub wheel 46, the workability during disassembly and assembly can be improved and the cost can be reduced.
  • a predetermined axial clearance (5 is formed between the shoulder portion 53 of the outer joint member 52 and the end surface of the crimping portion 6 of the hub wheel 46, and 1 8 (b
  • an annular groove 60 is formed on the outer periphery of the shoulder 53, and an elastic ring 61 made of an O-ring or the like is attached to the annular groove 60.
  • the elastic ring 61 elastically contacts the caulking portion 6 and liquid-tightly closes the annular space formed between the caulking portion 6 and the shoulder portion 53.
  • a drive wheel bearing device is a drive wheel in which a bearing portion having a hub ring and a constant velocity universal joint are connected so as to be able to transmit torque, and both are detachably united by screw means.
  • the present invention can be applied to a bearing device.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a drive wheel bearing device according to the present invention.
  • FIG. 2 (a) is a front view showing a fitting profile of the shaft portion of FIG. (B) is a cross-sectional view taken along line I I—I I of (a).
  • (C) is an explanatory view showing the difference in shape between the case where the pressure angle of the fitting profile file is negative and the case where it is positive
  • FIG. 3 is an enlarged view of the main part of FIG.
  • FIG. 4 is a graph showing the expansion amount of the hub wheel and the separation force generated in the engaging portion with respect to the pressure angle. It is.
  • FIG. 5 is a graph showing the expansion amount of the hub wheel with respect to the inclination angle and the separation force generated in the engaging portion.
  • FIG. 6 A diagram showing the shape of the hub wheel after forging, (b) is a longitudinal cross-sectional view of the hub wheel, and (a) is a cross-sectional view taken along line AA of (b).
  • FIG. 7 is a view showing the shape of the hub wheel after broaching, in which (b) is a longitudinal sectional view of the hub wheel, and (a) is a transverse sectional view taken along line BB in (b).
  • FIG. 8 is a view showing the shape of the hub wheel after broaching, where (a) is a top view of the fitting profile portion and (b) is a longitudinal sectional view of the fitting profile portion.
  • FIG. 9 is a diagram showing an outline of a vibration press apparatus, where (a) shows a state before pressing and (b) shows a state during pressing.
  • FIG. 10 is a longitudinal sectional view showing a fitting profile portion after vibration press processing.
  • FIG. 11 The fitting profile after vibration press processing is shown.
  • (A) is the end view along the D-D line in Fig. 10
  • (b) is the end view along the E-E line.
  • (C) is an end view taken along line FF.
  • FIG.12 The shape of the hub ring after vibration press processing is shown.
  • (B) is a longitudinal sectional view of the hub ring.
  • (A) is a cross-sectional view along the line CC in (b).
  • FIG. 13 is a view showing a gap formed in the shaft and hole of the fitting profile.
  • FIG. 14 (a) is a front view of the fitting profile 21.
  • (B) is (a
  • FIG. 15 (a) is a longitudinal sectional view showing a second embodiment of the drive wheel bearing device according to the present invention.
  • (B) is an enlarged view of the main part of (a).
  • FIG. 16 is a longitudinal sectional view showing a third embodiment of the bearing device for a drive wheel according to the present invention.
  • FIG. 17 is an explanatory view showing a fastening portion of a shaft portion in the outer joint member.
  • FIG. 18 (a) is a longitudinal sectional view showing a fourth embodiment of the drive wheel bearing device according to the present invention.
  • (B) is an enlarged view of the main part of (a).
  • FIG. 19 is a longitudinal sectional view showing a conventional drive wheel bearing device. Explanation of symbols

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Abstract

L'invention concerne un dispositif de palier de roue motrice, lequel est amélioré en maniabilité en ce qui concerne le temps de montage / démontage pour réduire de ce fait le coût et lequel élimine un jeu de rotation des parties insérées pour atteindre de ce fait une fiabilité et une stabilité directionnelle. Dans le dispositif de palier de roue motrice, une bague de moyeu (1) ayant une jante de montage de roue (4) intégralement sur sa partie d'extrémité, une multitude de lignes de paliers à roulement (2) et un joint universel uniforme (3) sont unis, de manière à être amovibles, par des vis et le joint universel uniforme (3) est joint à la bague de moyeu (1) par un moyen de transmission de couple. Le moyen de transmission de couple est constitué de sorte à inclure un profile d'application (21) ayant une multitude de dents (21a) placées uniformément sur la circonférence externe d'une tige (20) et un profil d'application (22) correspondant au profil d'application (21) et ayant une multitude de gorges (22a) placées uniformément sur la circonférence interne de la bague de moyeu (1) pour s'engrener dans les dents (21a). Les faces des dents de la dent (21a) et les gorges (22a) ont un angle de pression négatif prédéfini et un angle d'inclinaison prédéfini dans la direction axiale par rapport à l'axe, de sorte que le jeu de rotation des parties insérées peut être éliminé pour établir un état d'application étant ferme.
PCT/JP2007/000462 2006-04-26 2007-04-26 Dispositif de palier pour roue motrice et son procedé de fabrication WO2007125654A1 (fr)

Applications Claiming Priority (12)

Application Number Priority Date Filing Date Title
JP2006-121636 2006-04-26
JP2006121635A JP2007290587A (ja) 2006-04-26 2006-04-26 駆動車輪用軸受装置
JP2006121693A JP2007290591A (ja) 2006-04-26 2006-04-26 駆動車輪用軸受装置
JP2006-121635 2006-04-26
JP2006-121693 2006-04-26
JP2006121636A JP2007290588A (ja) 2006-04-26 2006-04-26 駆動車輪用軸受装置
JP2006147693A JP2007315545A (ja) 2006-05-29 2006-05-29 駆動車輪用軸受装置の製造方法
JP2006-147693 2006-05-29
JP2006160400A JP2007326503A (ja) 2006-06-09 2006-06-09 駆動車輪用軸受装置
JP2006-160400 2006-06-09
JP2006-164239 2006-06-14
JP2006164239A JP2007331508A (ja) 2006-06-14 2006-06-14 駆動車輪用軸受装置の製造方法

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WO2007125654A1 true WO2007125654A1 (fr) 2007-11-08

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PCT/JP2007/000462 WO2007125654A1 (fr) 2006-04-26 2007-04-26 Dispositif de palier pour roue motrice et son procedé de fabrication

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Country Link
WO (1) WO2007125654A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2623334A1 (fr) * 2012-02-02 2013-08-07 Jtekt Corporation Dispositif de support à roues
FR3005124A1 (fr) * 2013-04-30 2014-10-31 Ntn Snr Roulements Montage d’un systeme d’entrainement en rotation d’une roue de vehicule automobile dans un pivot

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JPH11303840A (ja) * 1998-04-22 1999-11-02 Kariya Dekku:Kk 悪事・脱落防止用のロック機構付きボルト及びナット
JP2002200902A (ja) * 2000-05-31 2002-07-16 Nsk Ltd 車輪駆動用ユニットとその製造方法
JP3572544B2 (ja) * 1997-08-16 2004-10-06 ゲブル．フェルス ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント カンバニー コマンデイトゲゼルシャフト ワークピースの成形，特に，冷間成形のための装置と方法
JP2004353724A (ja) * 2003-05-28 2004-12-16 Ntn Corp 駆動車輪用軸受装置
JP2005075067A (ja) * 2003-08-29 2005-03-24 Koyo Seiko Co Ltd 転がり軸受装置
JP2005308034A (ja) * 2004-04-19 2005-11-04 Shikoku Hume Kan Kk 継手を有する管体および管体の接続方法
JP2006062388A (ja) * 2004-08-24 2006-03-09 Honda Motor Co Ltd 車両用ホイール駆動装置

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JP3572544B2 (ja) * 1997-08-16 2004-10-06 ゲブル．フェルス ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント カンバニー コマンデイトゲゼルシャフト ワークピースの成形，特に，冷間成形のための装置と方法
JPH11303840A (ja) * 1998-04-22 1999-11-02 Kariya Dekku:Kk 悪事・脱落防止用のロック機構付きボルト及びナット
JP2002200902A (ja) * 2000-05-31 2002-07-16 Nsk Ltd 車輪駆動用ユニットとその製造方法
JP2004353724A (ja) * 2003-05-28 2004-12-16 Ntn Corp 駆動車輪用軸受装置
JP2005075067A (ja) * 2003-08-29 2005-03-24 Koyo Seiko Co Ltd 転がり軸受装置
JP2005308034A (ja) * 2004-04-19 2005-11-04 Shikoku Hume Kan Kk 継手を有する管体および管体の接続方法
JP2006062388A (ja) * 2004-08-24 2006-03-09 Honda Motor Co Ltd 車両用ホイール駆動装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2623334A1 (fr) * 2012-02-02 2013-08-07 Jtekt Corporation Dispositif de support à roues
US9321311B2 (en) 2012-02-02 2016-04-26 Jtekt Corporation Wheel support device
FR3005124A1 (fr) * 2013-04-30 2014-10-31 Ntn Snr Roulements Montage d’un systeme d’entrainement en rotation d’une roue de vehicule automobile dans un pivot

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