WO2007018001A1 - Dispositif de roulement d’une roue motrice - Google Patents

Dispositif de roulement d’une roue motrice Download PDF

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Publication number
WO2007018001A1
WO2007018001A1 PCT/JP2006/313402 JP2006313402W WO2007018001A1 WO 2007018001 A1 WO2007018001 A1 WO 2007018001A1 JP 2006313402 W JP2006313402 W JP 2006313402W WO 2007018001 A1 WO2007018001 A1 WO 2007018001A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing device
drive wheel
wheel
hub
joint member
Prior art date
Application number
PCT/JP2006/313402
Other languages
English (en)
Japanese (ja)
Inventor
Yoshikazu Fukumura
Masayuki Kuroda
Masahiro Ozawa
Original Assignee
Ntn Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn Corporation filed Critical Ntn Corporation
Publication of WO2007018001A1 publication Critical patent/WO2007018001A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/007—Cooling of bearings of rolling bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • 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
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0852—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
    • F16D1/092—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces the pair of conical mating surfaces being provided on the coupled hub and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Definitions

  • the present invention relates to a drive wheel bearing device that rotatably supports a drive wheel of a vehicle such as an automobile, and more particularly to a drive wheel in which a bearing portion and a constant velocity universal joint are detachably united.
  • the present invention relates to a bearing device.
  • 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 the radial direction from the wheel that occurs when the vehicle bounces or turns when traveling on a rough road.
  • one end of the drive shaft that is interposed between the engine side and the drive wheel side is connected to the differential through a sliding constant velocity universal joint.
  • the other end is connected to the wheel via a drive wheel bearing device including a fixed type constant velocity universal joint.
  • the drive wheel bearing device shown in FIG. 4 is a typical example satisfying these requirements.
  • This drive wheel bearing device is configured by detachably uniting a double row rolling bearing 51 and a constant velocity universal joint 52.
  • the double row rolling bearing 51 has a vehicle body mounting flange 53b integrally attached to the vehicle body, an outer member 53 having double row outer rolling surfaces 53a, 53a formed on the inner periphery, and one end portion.
  • An inner member having a wheel mounting flange 54b for mounting a wheel (not shown) integrally and having an inner rolling surface 54a, 54a opposite to the double row outer rolling surfaces 53a, 53a formed on the outer periphery.
  • the constant velocity universal joint 52 includes an outer joint member 56, a joint inner ring 57, a cage 58, and a torque transmission ball 59.
  • the outer joint member 56 includes a cup-shaped mouth portion 60 and the mouth portion 6
  • a shoulder portion 61 that forms the bottom of 0 and a hollow shaft portion 62 that extends in the axial direction from the shoulder portion 61 are integrally formed, and a male spline 62 a is formed on the outer periphery of the shaft portion 62.
  • the male spline 62a is engaged with a female spline 54c formed on the inner periphery of the inner member 54, and rotational torque from a drive shaft (not shown) is applied to the wheel mounting flange 54b via the inner member 54. Communicated.
  • the shaft portion 62 is formed to be as short as possible, and a female screw 62b is formed on the inner periphery to which the fastening bolt 63 is screwed.
  • a shoulder portion 64 is formed at the outer end of the female spline 54c of the inner member 54, and a head portion 63a of the fastening bolt 63 is supported by the shoulder portion 64 via a washer 65.
  • the fastening bolt 63 presses and supports the shoulder 61 of the outer joint member 56 on the inner end face 54d of the inner member 54, so that the double-row rolling bearing 51 and the constant velocity universal joint 52 are detachable. It has become.
  • the constant-velocity universal joint related to the support position of the fastening bolt 63 can be attached to and detached from the inner member 54 simply by sliding the shaft 52 in the axial direction toward the differential, and the disassembly and assembly work is simplified.
  • Patent Document 1 Japanese Patent Publication No. 1-51369
  • such a bearing device for a drive wheel has a feature that it can achieve a light weight 'compactity' and at the same time simplify disassembly 'assembly work, but both splines 54c, 62 It is difficult to completely prevent the play in the circumferential direction of the engaging portion of a. If the backlash in the circumferential direction of both splines 54c and 62a is large, both noises are generated when the vehicle suddenly accelerates or decelerates. The engaging portion of the splines 54c and 62a may be worn out and the steering stability may be reduced.
  • the structure is such that the end face of the inner member 54 and the shoulder of the outer joint member 56 are brought into contact with each other and tightened with the fastening bolts 63, so that when the outer joint member 56 is subjected to a large torque and twisted, it comes into contact. Stick-slip noise is generated due to sudden slip on the surface.
  • a torsion angle is provided in the male spline 62a of the shaft portion 62 and press-fitted into the female spline 54c of the inner member 54 to kill the play in the circumferential direction of the engaging portion of both the splines 54c and 62a.
  • the male spline 62a of the shaft portion 62 is provided with a twist angle, it is difficult to detach the outer joint member 56 from the inner member 54.
  • the present invention has been made in view of such circumstances, and has been made lighter and more compact, is improved in workability during disassembly and assembly, and is low in cost, and eliminates circumferential play in the coupling portion.
  • the purpose is to provide a bearing device for a drive wheel that is reliable and maneuverable. Means for solving the problem
  • the invention according to claim 1 is characterized in that an outer member having a double row outer rolling surface formed on the inner periphery and a wheel mounting flange at one end are integrated.
  • a hub ring having a cylindrical small-diameter stepped portion extending in the axial direction on the outer periphery, and at least one inner ring press-fitted into the small-diameter stepped portion of the hub ring.
  • An inner member formed with opposing double-row inner rolling surfaces; a double-row rolling element housed so as to roll freely between the two rolling surfaces; and a constant velocity universal joint;
  • An outer joint member that is separably coupled to the ring through screw means in an axial direction.
  • the outer joint member includes a cup-shaped mouth portion, a shoulder portion that forms the bottom of the mouth portion, and the shoulder portion. And a shaft portion extending in the axial direction from the shaft, and this shaft portion transmits torque to the hub wheel via a serration.
  • a selection is also formed on the inner periphery of the hub wheel, which also has a small-diameter tapered generating force toward the outer side, and the shaft portion of the outer joint member is A short shaft is formed on the outer periphery of the hub wheel to engage the selection of the hub wheel.
  • an outer member having a double row outer raceway formed on the inner periphery, a wheel mounting flange on one end, and a cylindrical small-diameter step extending in the axial direction on the outer periphery. And a hub ring formed with a portion, and at least one inner ring press-fitted into a small-diameter step portion of the hub ring.
  • An inner member formed with a double row inner rolling surface facing the outer rolling surface of the row, a double row rolling element accommodated between both rolling surfaces, and a constant velocity universal joint.
  • an outer joint member that is axially separably coupled to the hub wheel via a screw means.
  • the outer joint member includes a cup-shaped mouth portion and a shoulder portion that forms the bottom of the mouth portion.
  • the bearing device for a drive wheel which has an integral shaft portion extending in the axial direction from the shoulder portion, and the shaft portion is internally fitted to the hub wheel so as to be able to transmit torque via a serration
  • On the circumference there is formed a selection that also has a small-diameter tapered generating line force toward the outer side, and the shaft portion of the outer joint member is formed with a short axis, and on this outer periphery there is a selection that engages the selection of the hub wheel. Because it is formed, it can realize a strong bond without backlash and is lightweight. It is possible to provide a drive wheel bearing device that achieves a low cost by improving the workability at the time of disassembly and assembly while achieving compactness.
  • the screw means includes a male screw formed at an end of the shaft portion of the outer joint member and a fixing nut screwed into the male screw.
  • the male thread can be easily formed by rolling at the same time as the selection, and the cost can be reduced.
  • a crimped portion is formed by plastically deforming an end portion of the small-diameter step portion of the hub wheel radially outward, and the inner ring is formed by the crimped portion. If the inner member is configured by being fixed in the axial direction, a self-retaining structure can be provided, and the bearing preload can be maintained for a long time without firmly tightening the screw means.
  • the drive wheel bearing device has an outer member having a double row outer raceway formed on the inner periphery, a wheel mounting flange at one end, and an outer periphery in the axial direction.
  • a hub wheel formed with a cylindrical small-diameter step portion that extends and at least one inner ring press-fitted into the small-diameter step portion of the hub ring, and is arranged in a double-row inward rolling surface that faces the double-row outer raceway.
  • An inner member having a running surface, a double row rolling element accommodated in a freely rolling manner between the both rolling surfaces, and a constant velocity universal joint are configured, and a screw means is provided on the hub wheel via screw means.
  • An outer joint member coupled in a separable manner in the axial direction, the outer joint member force cup-shaped mouth portion, a shoulder portion forming the bottom of the mouse portion, and an axially extending shaft from the shoulder portion And a shaft that is internally fitted to the hub wheel so as to be able to transmit torque via a serration.
  • a selection that also has a small-diameter tapered generating line force toward the outer side is formed on the inner periphery of the hub wheel, and the shaft portion of the outer joint member is formed with a short shaft, A selection that engages with the selection of the hub wheel is formed on the outer periphery! Therefore, it is possible to realize a strong connection without backlash and to improve the workability when assembling lightweight and compact. Thus, it is possible to provide a drive wheel bearing device that achieves low cost.
  • the vehicle body mounting flange is integrally formed on the outer periphery, the outer member having a double row outer raceway formed on the inner periphery, and the wheel mounting flange is integrally formed on one end, and the double row is formed on the outer periphery.
  • a nove ring formed with one inner rolling surface facing the outer rolling surface, a cylindrical small-diameter step portion extending in an axial direction from the inner rolling surface, and a small-diameter step portion of the hub ring.
  • An inner member consisting of an inner ring that is press-fitted and has the other inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a composite member that is rotatably accommodated between the both rolling surfaces.
  • the mouth portion that forms the bottom of the mouse portion and the shaft portion that extends in the axial direction from the shoulder portion are integrally formed.
  • a selection having a small-diameter tapered generating line force is formed on the inner periphery of the hub wheel toward the outer side, and the shaft portion of the outer joint member is formed with a short shaft, and the selection is formed on the outer periphery.
  • a selection is formed on the outer periphery of the sleeve, and an axial clearance is formed between the crimped portion and the shoulder portion in a state where the hub wheel and the outer joint member are coupled to each other.
  • An elastic ring is interposed between the upper part and the shoulder part.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a drive wheel bearing device according to the present invention.
  • the side closer to the outer side of the vehicle when assembled to the vehicle is the outer side (left side of the drawing), and the side closer to the center is the inner side (right side of the drawing) t.
  • This drive wheel bearing device has a so-called third generation configuration in which a hub wheel 1, a double row rolling bearing 2, and a constant velocity universal joint 3 are detachably used.
  • RU 1 hub wheel 1
  • RU 2 constant velocity universal joint 3
  • 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 carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and integrally has a vehicle body mounting flange 7b for mounting to the vehicle body (not shown) on the outer periphery.
  • vehicle body mounting flange 7b for mounting to the vehicle body (not shown) on the outer periphery.
  • the double-row outer raceway surfaces 7a and 7a are subjected to a hardening treatment in a range of 58 to 64 HRC by induction hardening.
  • the inner member 8 is formed with double-row inner rolling surfaces la, 5a facing the outer rolling surfaces 7a, 7a of the outer member 7 described above.
  • double-row inner rolling surfaces la and 5a one (outer side) inner rolling surface la is on the outer periphery of the hub wheel 1, and the other (inner side) inner rolling surface 5a is on the outer periphery of the inner ring 5, respectively.
  • the inner member 8 refers to the hub wheel 1 and the inner ring 5.
  • Double-row rolling elements 9 and 9 are accommodated between these rolling surfaces, and are held by the cages 10 and 10 so that they can roll freely.
  • seals 11 and 12 are attached to both ends of the outer member 7 to prevent leakage of the lubricating grease sealed inside the bearing. This prevents rainwater and dust from entering the bearing from the inside.
  • the hub wheel 1 integrally has a wheel mounting flange 4 for mounting a wheel (not shown) at an end on the outer side, and has a cylindrical shape that extends in the axial direction from the inner raceway la on the outer periphery.
  • a small diameter step 1b is formed, and an inner ring 5 is press-fitted into the small diameter step lb.
  • the inner ring 5 has a preload applied to the hub ring 1 by a crimping portion 28 formed by plastically deforming the end of the small diameter step lb of the hub ring 1 radially outward. It is fixed in the axial direction.
  • a tapered (or spline) 13 having a tapered generative force that gradually decreases in diameter toward the outer side is formed on the inner periphery of the hub wheel 1.
  • a shoulder 6 is formed at the end of the selection 13 on the small diameter side.
  • the hub wheel 1 is made of medium carbon steel containing carbon 0.40-0.80wt% such as S53C, and from the seal land portion where the seal 11 on the one side of the water slidably contacts the inner rolling surface la and the small diameter step portion.
  • the outer peripheral surface over lb and the inner peripheral selection 13 are hardened to a surface hardness of 58 to 64 HRC by induction hardening.
  • the caulking portion 28 is left as it is.
  • the inner ring 5 is also made of high carbon chrome bearing steel such as SUJ2, and is hardened in the range of 54 to 64 HRC to the core part by quenching.
  • the seal land portion which is the base of the wheel mounting flange 4 has sufficient mechanical strength against the rotational bending load applied to the wheel mounting flange 4 which is not forced by force if the wear resistance is improved.
  • the durability of the hub wheel 1 is further improved. Further, fretting wear occurring on the fitting surface between the small diameter step lb and the inner ring 5 can be minimized.
  • a third generation double row rolling bearing in which the inner rolling surface la is directly formed on the outer periphery of the hub wheel 1 is illustrated here, the present invention is not limited thereto, and a pair of inner rings is provided on the hub ring. It may be a press-fit first or second generation structure. Further, the double-row angular ball bearing using balls as the rolling elements 9 is illustrated, but a double-row tapered roller bearing using tapered rollers as the rolling elements 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 force.
  • the outer joint member 14 includes a cup-shaped mouth portion 18, a shoulder portion 19 that forms the bottom of the mouth portion 18, and a hollow shaft portion 20 that extends in the axial direction from the shoulder portion 19.
  • a curved track groove extending in the axial direction on the inner periphery of 18 and the outer periphery of the joint inner ring 15 1 8a and 15a are formed.
  • the outer joint member 14 also has medium carbon steel strength including carbon 0.40-0.80 wt% such as S53C, and induction hardening is applied to the outer circumferential surface extending from the shoulder 19 to the shaft 20 including the track grooves 18a and 15a. Therefore, the surface hardness is in the range of 58 to 64HRC.
  • the shaft portion 20 of the outer joint member 14 is formed with a short shaft, the outer periphery is engaged with the selection 13 of the hub wheel 1, and a selection (or spline) 21 in which the bus bar is tapered is formed. It is. An internal thread 20a is formed at the end by rolling. Then, the shaft portion 20 of the outer joint member 14 is fitted to the hub wheel 1 via the selections 13 and 21 so that a predetermined axial clearance ⁇ is interposed between the shoulder portion 19 and the end face of the crimping portion 28.
  • the fixing nut 23 is screwed onto the male screw 20a of the shaft portion 20 via the washer 22 that contacts the shoulder portion 6 of the hub wheel 1, so that the hub wheel 1 and the outer joint member 14 can be separated in the axial direction. Are combined.
  • the outer joint member 14 can be easily attached to the hub wheel 1 simply by tightening the fixing nut 23 to the male screw 20a of the shaft portion 20 without requiring a special special jig such as a conventional power press. Can be retracted.
  • a special special jig such as a conventional power press.
  • it is light-weight and compact, and improves workability at the time of disassembly and assembly, thereby reducing the cost. Therefore, it is possible to provide a bearing device for a drive wheel that eliminates the backlash in the circumferential direction of the coupling portion and achieves reliability and steering stability.
  • the axial length of the shaft portion 20 is set to be smaller than the sliding stroke of a differential-type sliding-type constant velocity universal joint (not shown), for example, the outer member 7 is suspended (see FIG.
  • the shaft portion 20 can be easily separated from the hub wheel 1 simply by sliding the outer joint member 14 in the axial direction toward the inner side in a state where the outer joint member 14 is fixed to the inner side. Can be jealous.
  • FIG. 2 is a longitudinal sectional view showing a second embodiment of the drive wheel bearing device according to the present invention. This embodiment is different from the first embodiment described above only in the configuration of the double row rolling bearing and the coupling part, and other parts having the same parts or parts having the same functions are denoted by the same reference numerals. Therefore, detailed description is omitted.
  • this drive wheel bearing device has a configuration referred to as a third generation in which the hub wheel 1, the double row rolling bearing 2, and the constant velocity universal joint 24 are detachably unitized. It is making.
  • the double-row rolling bearing 2 includes an outer member 7, an inner member 8, and double-row rolling elements 9, 9.
  • the inner member 8 includes a hub wheel 1 and a small-diameter step portion of the hub wheel 1 lb. It consists of an inner ring 5 press-fitted into.
  • the inner ring 5 is axially formed with respect to the nove ring 1 in a state where a preload is applied by a crimping portion 28 formed by plastically deforming an end portion of the small-diameter stepped portion lb of the hub ring 1 radially outward. It is fixed.
  • the outer joint member 25 of the constant velocity universal joint 24 includes a cup-shaped mouth portion 18, a shoulder portion 19 that forms the bottom portion of the mouth portion 18, and a shaft portion 30 that extends from the shoulder portion 19 in the axial direction.
  • the shaft portion 30 is formed with a selection 21 that engages with the selection 13 of the hub wheel 1 on the outer periphery of the shaft portion 30, and a male screw 20 a formed on the inner periphery of the shaft portion 30. Then, the shaft portion 30 of the outer joint member 25 is fitted to the hub wheel 1 via the selections 13 and 21 so that a predetermined axial clearance ⁇ is interposed between the shoulder portion 19 and the end surface of the caulking portion 28.
  • the fastening bolt 31 is screwed into the male screw 20a of the shaft portion 30, and the hub wheel 1 and the outer joint member 25 are coupled so as to be separable in the axial direction.
  • the buses have the tapered selections 13 and 21, the circumferential backlash can be killed, and even if a large torque is applied to the outer joint member 25 and the torsion occurs, the shoulder 19 Since a predetermined axial clearance ⁇ is formed between the end portion of the crimping portion 28 and the end surface of the crimping portion 28, no stick-slip noise is generated between the calorie tightening portion 28.
  • FIG. 3 (a) is a longitudinal sectional view showing a third embodiment of the drive wheel bearing device according to the present invention
  • FIG. 3 (b) is an enlarged view of the main part of FIG. 3 (a).
  • This embodiment is a modification of the above-described first embodiment (FIG. 1), and the same components and parts having the same functions as those of the above-described embodiment are denoted by the same reference numerals and detailed description is given. Is omitted.
  • the outer joint member 29 of the constant velocity universal joint 27 includes a cup-shaped mouth portion 18 and the mouth portion 18. And a shaft portion 33 extending in the axial direction from the shoulder portion 32, a selection portion 21 engaging with the selection 13 of the hub wheel 1 on the outer periphery of the shaft portion 33, and a shaft portion 33.
  • a male screw 20a is formed at the end of the. Then, the shaft portion 33 of the outer joint member 29 is fitted to the hub wheel 1 via the selections 13 and 21 so that a predetermined axial clearance ⁇ is interposed between the shoulder portion 32 and the end surface of the crimping portion 28.
  • the fixing nut 23 is screwed into the male screw 20a of the shaft portion 33, and the hub wheel 1 and the outer joint member 29 are connected to each other in a separable manner in the axial direction.
  • the root diameter of the shaft portion 33 is formed large, the number of teeth of the selection 21 can be substantially increased, and the shaft portion 33 can be made compact in the axial direction.
  • the knuckle fitting surface of the outer member 7 is set to be larger than the maximum outer diameter of the constant velocity universal joint 27, the double row rolling bearing 2 and the constant velocity universal joint 27 are united. Can be incorporated into a nut (not shown).
  • annular groove 32a is formed on the outer periphery of the shoulder 32, and an elastic ring 34 made of an O-ring or the like is attached to the annular groove 32a.
  • the elastic ring 34 is in elastic contact with the crimping portion 28 and liquid-tightly closes the annular space formed between the crimping portion 28 and the shoulder portion 32. This prevents external force rainwater or dust that does not generate stick-slip noise from entering the joint, prevents the joint from sticking due to fire, and improves disassembly workability during repairs. Can be made.
  • a bearing portion having a hub ring and a constant velocity universal joint are connected via a serration so that torque can be transmitted, and both are detachably united by a screw means. It can be applied to a drive wheel 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 is a longitudinal sectional view showing a second embodiment of the bearing device for a drive wheel according to the present invention.
  • FIG. 3 (a) is a longitudinal sectional view showing a third embodiment of the drive wheel bearing device according to the present invention. (b) is the principal part enlarged view of (a).
  • FIG. 4 is a longitudinal sectional view showing a conventional drive wheel bearing device.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

Le problème à résoudre dans le cadre de cette invention est de prévoir un dispositif de roulement d’une roue motrice. Le dispositif de roulement est léger et compact, son coût est réduit en améliorant l’aptitude au façonnage dans le démontage et le montage du dispositif, et le jeu périphérique dans une section d’accouplement est éliminé pour augmenter l’efficacité et la stabilité de la conduite La solution proposée consiste à prévoir un dispositif de roulement d’une roue motrice, dans lequel une bague de moyeu (24), un roulement à deux rangées de rouleaux cylindriques (25), et un joint homocinétique (26) sont unitisés, une bague interne (5) est fixée au niveau d’une section de matage (28) d’une section à gradin de petit diamètre (1b), et une section d’arbre (30) d’un élément de raccord externe (33) est montée sur la bague du moyeu (24). Sur la périphérie interne de la bague de moyeu (24), vers le côté extérieur, des indentations sont formées (13) sur une section de petit diamètre formée par des génératrices coniques. De plus, des indentations (21) s’engageant dans les indentations (13) sont formées sur la périphérie externe de la section d’arbre (30). Un espace axial (δ) est formé entre la section de matage (28) et un épaulement (34) avec la bague de moyeu (24) et l’élément de raccord externe (33) couplés. Une bague élastique (35) s’intercale entre la section de matage (28) et l’épaulement (34).
PCT/JP2006/313402 2005-08-10 2006-07-05 Dispositif de roulement d’une roue motrice WO2007018001A1 (fr)

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JP2005-231924 2005-08-10
JP2005231924A JP2007046703A (ja) 2005-08-10 2005-08-10 駆動車輪用軸受装置

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009038102A1 (fr) * 2007-09-18 2009-03-26 Ntn Corporation Dispositif de palier pour roue
US8360655B2 (en) 2007-10-15 2013-01-29 Ntn Corporation Bearing device for wheel
US8944694B2 (en) 2007-03-07 2015-02-03 Ntn Corporation Bearing device for driving wheel, and its assembling method

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008078511A1 (fr) 2006-12-27 2008-07-03 Ntn Corporation Dispositif de roulement pour roue
JP5117128B2 (ja) * 2007-07-02 2013-01-09 Ｎｔｎ株式会社 車輪用軸受装置
JP5323338B2 (ja) * 2007-10-17 2013-10-23 Ｎｔｎ株式会社 車輪用軸受装置
JP5323337B2 (ja) * 2007-10-15 2013-10-23 Ｎｔｎ株式会社 車輪用軸受装置
JP5323339B2 (ja) * 2007-10-17 2013-10-23 Ｎｔｎ株式会社 車輪用軸受装置
JP5304113B2 (ja) * 2008-09-02 2013-10-02 株式会社ジェイテクト 車軸用軸受の締結構造
KR102614131B1 (ko) * 2018-05-17 2023-12-13 현대자동차주식회사 등속조인트 허브 결합구조

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JPS6150831A (ja) * 1984-08-16 1986-03-13 レ−ル・ウント・ブロンカンプ・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング 継手軸
JPS63110001A (ja) * 1986-10-27 1988-05-14 Ntn Toyo Bearing Co Ltd 自動車の駆動車輪用軸受装置
JP2002002210A (ja) * 2000-06-21 2002-01-08 Nsk Ltd 車輪駆動用軸受ユニット
JP2002029207A (ja) * 2000-07-17 2002-01-29 Koyo Seiko Co Ltd 車両用軸受装置
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

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JPS6150831A (ja) * 1984-08-16 1986-03-13 レ−ル・ウント・ブロンカンプ・ゲゼルシヤフト・ミツト・ベシユレンクテル・ハフツング 継手軸
JPS63110001A (ja) * 1986-10-27 1988-05-14 Ntn Toyo Bearing Co Ltd 自動車の駆動車輪用軸受装置
JP2002002210A (ja) * 2000-06-21 2002-01-08 Nsk Ltd 車輪駆動用軸受ユニット
JP2002029207A (ja) * 2000-07-17 2002-01-29 Koyo Seiko Co Ltd 車両用軸受装置
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

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8944694B2 (en) 2007-03-07 2015-02-03 Ntn Corporation Bearing device for driving wheel, and its assembling method
WO2009038102A1 (fr) * 2007-09-18 2009-03-26 Ntn Corporation Dispositif de palier pour roue
US8801294B2 (en) 2007-09-18 2014-08-12 Ntn Corporation Bearing device for a wheel
US9308777B2 (en) 2007-09-18 2016-04-12 Ntn Corporation Bearing device for a wheel
US8360655B2 (en) 2007-10-15 2013-01-29 Ntn Corporation Bearing device for wheel

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