WO2013047695A1 - Dispositif de palier pour roue doté d'un moteur intégré dans la roue - Google Patents

Dispositif de palier pour roue doté d'un moteur intégré dans la roue Download PDF

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Publication number
WO2013047695A1
WO2013047695A1 PCT/JP2012/074959 JP2012074959W WO2013047695A1 WO 2013047695 A1 WO2013047695 A1 WO 2013047695A1 JP 2012074959 W JP2012074959 W JP 2012074959W WO 2013047695 A1 WO2013047695 A1 WO 2013047695A1
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WO
WIPO (PCT)
Prior art keywords
wheel
bearing device
motor
wheel bearing
rolling
Prior art date
Application number
PCT/JP2012/074959
Other languages
English (en)
Japanese (ja)
Inventor
小森　和雄
峻介 森田
Original Assignee
Ntn株式会社
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 JP2011212161A external-priority patent/JP2013071599A/ja
Priority claimed from JP2011250571A external-priority patent/JP5913925B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2013047695A1 publication Critical patent/WO2013047695A1/fr

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    • 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
    • B60B27/0073—Hubs characterised by sealing means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0078—Hubs characterised by the fixation of bearings
    • B60B27/0089—Hubs characterised by the fixation of bearings caulking to fix outer race
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
    • B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • B60K7/0007—Disposition of motor in, or adjacent to, traction wheel the motor being electric
    • C—CHEMISTRY; METALLURGY
    • C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
    • C22F—CHANGING THE PHYSICAL STRUCTURE OF NON-FERROUS METALS AND NON-FERROUS ALLOYS
    • C22F1/00—Changing the physical structure of non-ferrous metals or alloys by heat treatment or by hot or cold working
    • C22F1/04—Changing the physical structure of non-ferrous metals or alloys by heat treatment or by hot or cold working of aluminium or alloys based thereon
    • C22F1/043—Changing the physical structure of non-ferrous metals or alloys by heat treatment or by hot or cold working of aluminium or alloys based thereon of alloys with silicon as the next major constituent
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7873—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section
    • F16C33/7876—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section with sealing lips
    • 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
    • B60B27/0031—Hubs for driven wheels characterised by torque transmission means from drive axle of the axial type, e.g. front teeth
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • B60K2007/0038—Disposition of motor in, or adjacent to, traction wheel the motor moving together with the wheel axle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • B60K2007/0092—Disposition of motor in, or adjacent to, traction wheel the motor axle being coaxial to the wheel axle
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D6/00—Heat treatment of ferrous alloys
    • C21D6/02—Hardening by precipitation
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction 

Definitions

  • the present invention relates to a wheel bearing device for rotatably supporting a wheel, and an in-wheel motor built-in wheel bearing device in an electric vehicle in which the wheel bearing device, a speed reducer, and a motor are combined.
  • an in-wheel type motor-integrated wheel bearing device in which a wheel bearing, a reduction gear, and a motor are combined is attracting attention as a wheel bearing device for an electric vehicle.
  • the in-wheel type motor-equipped wheel bearing device is used as a driving wheel of an electric vehicle, each wheel can be individually driven to rotate, so that a large-scale power transmission mechanism such as a conventional propeller shaft or a differential is not required. Can be made lighter and more compact.
  • This in-wheel type motor-equipped wheel bearing device includes a wheel bearing device 101 that rotatably supports a wheel (not shown), a motor 102 as a rotation drive source, and a hub that decelerates the rotation of the motor 102 to reduce the rotation of the motor 102.
  • the speed reducer 103 that transmits to the wheel is disposed on the central axis O of the wheel.
  • the motor 102 is configured by a radial gap type motor in which a radial gap is provided between a stator 105 fixed to a cylindrical motor casing 104 and a rotor 107 attached to an output shaft 106.
  • the output shaft 106 is rotatably supported by the rolling bearings 108 and 108 including a pair of deep groove ball bearings with respect to the motor casing 104.
  • the opening on the inner side of the motor casing 104 is closed with a cap 109.
  • the reduction gear 103 is a cycloid reduction gear, and includes an input shaft 111 having an eccentric shaft 110, a plurality of outer pins 113 passed between the reduction gear casing 112 and the motor casing 104, and a drive shaft (output member).
  • 114 includes a plurality of inner pins 115 and two curved plates 118 and 119 that are rotatably supported on the eccentric shaft 110 via rolling bearings 116 and 117 formed of cylindrical roller bearings.
  • the curved plates 118 and 119 are formed in a wavy trochoid curve having a gentle outer shape, and are attached to the eccentric shaft 110.
  • the outer pin 113 is rotatably supported by rolling bearings 120 and 120 including a pair of needle roller bearings, and the outer pin 113 guides the eccentric motion of the curved plates 118 and 119 on the outer peripheral side.
  • the input shaft 111 is coupled to the output shaft 106 of the motor 102 via the spline 111a and is integrally rotated.
  • the eccentric shaft 110 attached to the input shaft 111 that rotates integrally therewith rotates, and the curved plates 118 and 119 engaged with the eccentric shaft 110 perform an eccentric motion.
  • the rotation of the rotor 107 is smoothly and efficiently transmitted as a rotational movement of the drive shaft 114 with a large reduction ratio.
  • the two curved plates 118 and 119 are mounted on the eccentric shaft 110 of the input shaft 111 with a phase difference of 180 ° so that the eccentric motion is canceled out, and on each side of the eccentric shaft 110, the curved plates 118 and 119 are mounted.
  • Counterweights 121 and 121 that are eccentric in the direction opposite to the eccentric direction of the eccentric shaft 110 are mounted so as to cancel the vibration caused by the eccentric motion.
  • the input shaft 111 is rotatably supported by a rolling bearing 122 formed of a deep groove ball bearing with respect to a drive shaft 114 described later.
  • the wheel bearing device 101 is externally inserted through an inner member 125 including a hub wheel 123 and an inner ring 124 press-fitted into the hub wheel 123, and the inner member 125 via double rows of balls 126 and 126.
  • the outer member 127 is provided.
  • the hub wheel 123 integrally has a wheel mounting flange 128 for mounting a wheel at one end, and has an inner rolling surface 123a on the outer periphery and a small-diameter stepped portion 123b extending in the axial direction from the inner rolling surface 123a.
  • a serration 123c for torque transmission is formed on the inner periphery.
  • the inner ring 124 is formed with the other inner rolling surface 124a on the outer periphery, and is press-fitted into the small-diameter step portion 123b of the hub ring 123 via a predetermined squeeze.
  • the outer member 127 integrally has a vehicle body mounting flange 127b attached to the reduction gear casing 112 via a fixing bolt 112a on the outer periphery, and a plurality of outer members 127 facing the inner rolling surfaces 123a and 124a of the inner member 125 on the inner periphery.
  • the outer rolling surfaces 127a and 127a of the row are integrally formed. Between these rolling surfaces 127a, 123a and 127a, 124a, double rows of balls 126, 126 held in a cage 129 are accommodated so as to roll freely.
  • the drive shaft 114 constituting the speed reducer 103 includes a flange portion 130 to which the inner pin 115 is attached, a cylindrical shoulder portion 131 extending in the axial direction from the flange portion 130, and a shaft extending in the axial direction from the shoulder portion 131.
  • the part 132 is integrally formed.
  • a serration 132a meshing with the serration 123c of the hub wheel 123 is formed on the outer periphery of the shaft portion 132, and a male screw is formed at this end portion.
  • the drive shaft 114 is brought into contact with the hub wheel 123 until the shoulder portion 131 abuts the end surface of the inner ring 124.
  • the drive shaft 114 and the hub wheel 123 are coupled to each other in the axial direction so as to transmit torque (fixed torque 133 is fixed by a fixed nut 133 fitted inside and screwed to the male screw) (see, for example, Patent Document 1). ).
  • an oil seal 134 is mounted in an annular space formed between the outer member 127 of the wheel bearing device 101 and the shoulder 131 of the drive shaft 114, and the gear enclosed in the speed reducer 103. Sealed so that oil does not leak into the bearing.
  • a mounting space is required in the axial direction. For this reason, the whole apparatus enlarges and a weight increases. In order to avoid this, it is conceivable to reduce the size of the wheel bearing device 101.
  • the rolling bearing 122 becomes the original axis of the input shaft 111 and the output shaft 106.
  • the motor casing 104 is hardly affected by the load from the wheels, and the coaxiality of the two rolling bearings 108 and 122 is deteriorated and tilted. For this reason, an uneven load is likely to act on these rolling bearings 108 and 122, not only lowering the durability and noise of the rolling bearings 108 and 122 but also lowering the rotational accuracy of the input shaft 111 and the output shaft 106. There was a problem such as.
  • the present invention has been made in view of such a conventional problem, and while ensuring the rigidity of the wheel bearing device, it is lightweight and compact, and the rotational accuracy of the input shaft and the durability of the bearing that supports the input shaft are achieved. It is an object of the present invention to provide an in-wheel type motor-equipped wheel bearing device with improved performance.
  • the present invention provides a wheel bearing device for rotatably supporting a wheel, a motor arranged coaxially with respect to the central axis of the wheel, and an input driven by the output of the motor.
  • a planetary gear reducer provided with a shaft, a cylindrical portion, and a front end portion whose central portion is opened at an end portion on the outer side thereof, and a housing in which the planetary gear reducer and a motor are accommodated.
  • the wheel bearing device is fastened to the opening of the front end portion of the housing by a fixing bolt, and the input shaft is supported by a pair of rolling bearings on both axial sides of the planetary gear reducer.
  • a wheel bearing device wherein the wheel bearing device has an outer member having a vehicle body mounting flange on an outer periphery and a double row outer rolling surface formed on an inner periphery, and the wheel is attached to one end.
  • a hub ring integrally having a wheel mounting flange and having a 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 wheel.
  • An inner member in which a double row of inner rolling surfaces facing the outer rolling surface is formed, and a double row of rolling members housed between the inner member and the outer member so as to roll freely.
  • an output that constitutes the planetary gear speed reducer such that a large end surface of the inner ring overlaps with an insertion hole of a pinion pin that constitutes the planetary gear speed reducer. It is in contact with the side surface of the holding portion of the member in abutment state.
  • a planetary gear reducer provided with a wheel bearing device for rotatably supporting a wheel, a motor arranged coaxially with respect to the central axis of the wheel, and an input shaft driven by the output of the motor And a cylindrical portion, and a front end portion whose central portion is open at an end portion on the outer side thereof, and a planetary gear reducer and a housing that accommodates a motor, the opening portion of the front end portion of the housing
  • An in-wheel type motor-equipped wheel bearing device in which a wheel bearing device is fastened by a fixing bolt and an input shaft is supported by a pair of rolling bearings on both axial sides of a planetary gear reducer, the wheel bearing device Has a body mounting flange on the outer periphery, an outer member having a double row outer raceway formed on the inner periphery, and a wheel mounting flange for mounting the wheel on one end, and Axially A hub ring formed with a small-diameter stepped portion and at least one inner ring
  • an in-wheel type motor built-in wheel bearing device comprising an inner member formed and a double row rolling element that is rotatably accommodated between both rolling surfaces of the inner member and the outer member. Since the large end surface of the inner ring is in contact with the side surface of the holding portion of the output member constituting the planetary gear speed reducer so as to overlap with the insertion hole of the pinion pin constituting the planetary gear speed reducer, Compared to the device, the diameter of the inner ring can be increased so that it can be abutted against the output member at the position of one step larger diameter, and the space is effectively utilized and the axial space is shortened while ensuring the rigidity of the wheel bearing device. The rotation accuracy of the input shaft and It is possible to provide an in-wheel type motor built wheel bearing apparatus with improved durability of the bearing for supporting the input shaft.
  • the wheel bearing device has an outer member integrally including the vehicle body mounting flange on the outer periphery, and a double row outer rolling surface formed integrally on the inner periphery, and one end portion. And a hub having an inner rolling surface facing one of the double-row outer rolling surfaces and a small-diameter step portion extending in the axial direction from the inner rolling surface.
  • the wheel bearing device has a hub wheel integrally having the wheel mounting flange at one end and a small-diameter step portion extending in the axial direction on the outer periphery, and a small diameter of the hub wheel.
  • the wheel bearing comprises a stepped portion and a bearing case integrally having the vehicle body mounting flange on the outer periphery, and this wheel bearing is formed integrally with a double row outer rolling surface on the inner periphery.
  • the rolling element may be provided.
  • the planetary gear reducer includes a sun gear provided on an outer periphery of the input shaft, a ring gear fixed to the housing and disposed coaxially with the sun gear, and the ring gear and the sun gear. It consists of pinion gears that are equally disposed at a plurality of locations at equal intervals in the circumferential direction and are rotatably supported by the holding portion.
  • the output member constituting the planetary gear speed reducer includes a coupling shaft portion fitted into the hub wheel on the outer periphery, and an annular shape formed on the inner side of the coupling shaft portion with a large diameter.
  • a shaft hole coaxial with the coupling shaft portion is formed on the inner end surface of the holding portion, and the shaft hole has a depth reaching the annular base portion, and the shaft hole
  • the annular base portion of the output member is fitted and inserted into the small diameter step portion of the hub wheel via an elastic member, leakage of the lubricating oil in the reduction gear to the outside can be prevented, The environment can be prevented from being polluted.
  • the outer member is fitted and inserted into the front end portion of the housing via an elastic member, rain water and the like can be prevented from entering from the outside, and the lubricating oil in the speed reducer can be moved outside. Leakage can be prevented.
  • the output member is fixed to the hub wheel so that torque can be transmitted by a fixing nut screwed to an end of the coupling shaft portion.
  • the hub wheel and the bearing case are made of an aluminum alloy and are subjected to a precipitation hardening treatment that is hardened by heat treatment, the strength is increased and the amount of aluminum used is reduced to achieve weight reduction. be able to.
  • the planetary gear speed reducer is disposed on the inner diameter side of the motor, and the planetary gear speed reducer and the motor accommodating portion are partitioned by a partition wall provided in the housing.
  • a partition base formed coaxially with the opening and a cup-shaped partition member fixed to the partition base may be formed inside the front end of the housing.
  • the partition base and the partition member are formed integrally with the housing, the number of parts can be reduced, the assembly process can be simplified, and the cost can be reduced.
  • the aluminum alloy bearing case is made of a steel outer ring, inner ring and output member.
  • the linear expansion coefficient is large, if the temperature rises while the vehicle is running, the amount of expansion of the bearing case may increase and the internal clearance of the wheel bearing may increase, but the internal clearance is reduced by a light alloy washer. Can be prevented from increasing.
  • an oil seal is attached to an opening of an annular space formed between the front end portion of the housing or the outer member and the inner ring, the outer side of the wheel bearing device is removed.
  • the axial space can be further reduced, and lubrication enclosed within the bearing by a single seal Since it is possible to prevent grease from leaking to the outside and intrusion of lubricating oil, contamination, and the like from the reducer side into the bearing, it is possible to reduce rotational torque due to seal sliding contact.
  • the bearing space is effectively utilized.
  • the life of the bearing can be extended.
  • the diameter of the inner ring can be increased and abutted against the output member at the position of one step larger diameter, and the axial space can be shortened while ensuring the rigidity of the wheel bearing device.
  • the bearing life can be increased.
  • the bearing rigidity can be increased, and the bearing can be increased in rigidity.
  • the rolling element is made of ceramic, it is possible to reduce the weight, increase the rigidity, and improve the wear resistance, as well as the outer rolling surface of the outer member and the inner ring.
  • the area of the contact ellipse that makes contact with the inner rolling surface is reduced, and torque loss and dynamic friction that occur when the rolling element rolls between the rolling surfaces can be suppressed. Torque can be reduced.
  • a bolt hole is formed at a circumferentially equidistant position of the wheel mounting flange of the hub wheel, and the wheel is fixed to the wheel mounting flange by a wheel bolt screwed into the bolt hole. If there is a defect such as a scratch on the threaded part of the wheel bolt, not only can it be easily replaced on the market, but it is also possible to mount the wheel to replace the bolt on the market as before. It is not necessary to secure a space on the inner side of the flange, and repairability is improved, and the axial space can be reduced by that amount, so that lightweight and compactness can be achieved while securing rigidity.
  • An in-wheel motor-equipped wheel bearing device includes a wheel bearing device for rotatably supporting a wheel, a motor arranged coaxially with respect to the central axis of the wheel, and an output of the motor.
  • a planetary gear speed reducer having an input shaft to be driven, a cylindrical portion, and a housing that houses the planetary gear speed reducer and a motor, having a front end portion whose central portion is opened at an outer end portion thereof.
  • the wheel bearing device is fastened to the opening at the front end of the housing by a fixing bolt, and the input shaft is supported by a pair of rolling bearings on both sides in the axial direction of the planetary gear reducer.
  • a wheel-type motor-equipped wheel bearing device wherein the wheel bearing device has an outer member having a vehicle body mounting flange on the outer periphery and a double row outer rolling surface formed on the inner periphery, and one end portion.
  • Said A hub wheel having a wheel mounting flange for mounting a wheel integrally, a hub wheel having a 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 wheel.
  • An inner member formed with a double-row inner rolling surface opposite to the double-row outer rolling surface, and is accommodated in a freely rollable manner between both rolling surfaces of the inner member and the outer member.
  • the planetary gear reduction so that a large end surface of the inner ring overlaps with an insertion hole of a pinion pin constituting the planetary gear reducer. Since it is in contact with the side surface of the holding portion of the output member constituting the machine in abutting state, the diameter of the inner ring can be increased compared to the conventional device, and it can be abutted against the output member at a position with a larger diameter, Yes while ensuring the rigidity of the wheel bearing device
  • the present invention provides an in-wheel type motor-equipped wheel bearing device that can reduce space in the axial direction and improve the rotational accuracy of the input shaft and the durability of the bearing that supports the input shaft. be able to.
  • FIG. 1 is the principal part enlarged view which shows the wheel bearing apparatus and reduction gear of FIG. 1
  • (b) is the principal part enlarged view which shows one seal part of (a)
  • (c) is (a). It is a principal part enlarged view which shows the other seal part of this.
  • (A) is a principal part enlarged view which shows the motor part of FIG. 1
  • (b) is a principal part enlarged view which shows the seal part of (a).
  • (b) is a principal part enlarged view which shows one seal part of (a). It is a principal part enlarged view which shows the wheel bearing apparatus and output member of FIG. It is a principal part enlarged view which shows the modification of FIG. It is a principal part enlarged view which shows the modification of the wheel bearing apparatus of FIG. It is a principal part enlarged view which shows the modification of the wheel bearing apparatus of FIG. It is a principal part enlarged view which shows the other modification of the wheel bearing apparatus of FIG. It is a longitudinal cross-sectional view which shows the conventional bearing apparatus for in-wheel type motor built-in wheels.
  • a wheel bearing device for rotatably supporting a wheel, a motor arranged coaxially with respect to the central axis of the wheel, a planetary gear reducer having an input shaft driven by the output of the motor, and a cylinder And an outer end of the front end of which the central portion is opened, and a housing that houses the planetary gear reducer and a motor.
  • the wheel is provided at the opening of the front end of the housing.
  • An in-wheel type motor in which an outer member of a bearing device is fitted and fastened to the front end portion by a fixing bolt, and the input shaft is supported by a pair of rolling bearings on both axial sides of the planetary gear reducer
  • An internal wheel bearing device wherein the wheel bearing device has a body mounting flange integrally on the outer periphery, and an outer member integrally formed with a double row outer rolling surface on the inner periphery, and one end portion Take the wheel to A wheel mounting flange is integrally formed, and an inner rolling surface facing one of the double-row outer rolling surfaces and a small-diameter step portion extending in the axial direction from the inner rolling surface are formed on the outer periphery.
  • a hub ring an inner member formed of an inner ring press-fitted into a small-diameter step portion of the hub ring and formed with an inner rolling surface facing the other of the double-row outer rolling surfaces, and the inner member and the A double row rolling element housed between both rolling surfaces of the outer member so as to be freely rollable, and a seal attached to both end openings of an annular space formed between the outer member and the inner member
  • the planetary gear speed reducer is fixed to the housing and arranged coaxially with the sun gear.
  • Ring gear and circumferential direction between the ring gear and the sun gear It is composed of planetary gears composed of pinion gears arranged at equal intervals through pinion pins at equal intervals, and an output member constituting the planetary gear speed reducer is fitted on the outer periphery via serrations on the hub wheel.
  • the fixed end is in contact with the side surface of the holding portion of the output member so as to overlap with the insertion hole of the pinion pin, and is screwed to the end portion of the coupling shaft portion.
  • the output member is fixed to the hub wheel so as to transmit torque.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of an in-wheel motor-equipped wheel bearing device according to the present invention
  • FIG. 2A is a main portion showing the wheel bearing device and the speed reducer of FIG. Enlarged view
  • (b) is an enlarged view of the main part showing one seal part of (a)
  • (c) is an enlarged view of the main part showing the other seal part of (a)
  • FIG. 1 is an enlarged view of the main part showing the motor part of FIG. 1
  • FIG. 4B is an enlarged view of the main part showing the seal part of FIG. 1
  • FIG. 4 is an enlarged view of the main part showing the wheel bearing device and output member of FIG.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of an in-wheel motor-equipped wheel bearing device according to the present invention
  • FIG. 2A is a main portion showing the wheel bearing device and the speed reducer of FIG. Enlarged view
  • (b) is an enlarged view of the main part showing one seal part of
  • FIG. 5 is an enlarged view of a main part showing a modification of FIG.
  • the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as the outer side (left side in FIG. 1), and the side closer to the center is referred to as the inner side (right side in FIG. 1).
  • the in-wheel motor-equipped wheel bearing device includes a wheel bearing device 1 that rotatably supports a wheel (not shown), a motor 2 that serves as a rotational drive source, and a motor 2 that decelerates rotation of the motor 2 to be described later.
  • the reduction gear 3 that transmits to the hub wheel 13 and the housing 4 that accommodates the reduction gear 3 and the motor 2 are the main components and are arranged on the central axis O of the wheel.
  • the hub wheel 13 of the wheel bearing device 1 is rotated by an output member 6 coaxial with the input shaft 5 of the speed reducer 3.
  • the housing 4 includes a cylindrical portion 7 and a front end portion 8 at an end on the outer side thereof, the center portion is opened, and an outer member 17 of the wheel bearing device 1 is fitted into the opening portion 9 so that the vehicle body is attached.
  • a flange 17b is fastened to the front end 8 by a fixing bolt 17c.
  • a partition base 8a having a larger diameter is formed coaxially with the opening 9 inside the front end 8 of the housing 4, and a cup-shaped partition member 10 is fixed to the partition base 8a with bolts (not shown). ing.
  • a center hole 11 is formed at the center of the partition wall member 10, and this center hole 11 faces an outer diameter surface of a rotor support member 41 described later via an annular space.
  • a partition wall 12 is configured by the partition wall base portion 8a and the partition wall member 10 connected to the partition wall base portion 8a. The partition wall 12 has a function of partitioning the housing 4 into a housing space for the motor 2 on the outer diameter side and a housing space for the reduction gear 3 on the inner diameter side.
  • the wheel bearing device 1 is called the third generation for driving wheels, and as shown in an enlarged view in FIG. 2 (a), an inner side composed of a hub wheel 13 and an inner ring 14 press-fitted into the hub wheel 13. A member 15 and an outer member 17 externally inserted into the inner member 15 via double-row rolling elements (balls) 16 and 16 are provided.
  • the hub wheel 13 integrally has a wheel mounting flange 18 for mounting a wheel (not shown) at an end portion on the outer side, one (outer side) inner rolling surface 13a on the outer periphery, and this inner rolling.
  • a small diameter step portion 13b extending in the axial direction from the surface 13a is formed, and a serration (or spline) 13c for torque transmission is formed on the inner periphery.
  • the inner ring 14 is formed with the other (inner side) inner rolling surface 14a on the outer periphery, and is press-fitted into the small-diameter step portion 13b of the hub ring 13 through a predetermined squeeze.
  • hub bolts 18 a are implanted at equidistant positions in the circumferential direction of the wheel mounting flanges 18.
  • the hub wheel 13 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and includes an inner rolling surface 13a and an inner side of a wheel mounting flange 18 serving as a seal land portion of a seal 20 described later.
  • the surface is hardened in the range of 58 to 64 HRC by induction hardening from the base portion 18b to the small diameter step portion 13b.
  • the inner ring 14 is made of high carbon chrome steel such as SUJ2, and is hardened in the range of 58 to 64 HRC up to the core part by quenching.
  • the outer member 17 integrally has a vehicle body mounting flange 17b attached to the front end 8 of the housing 4 via a fixing bolt 17c on the outer periphery, and is opposed to the inner rolling surfaces 13a and 14a of the inner member 15 on the inner periphery.
  • Double row outer rolling surfaces 17a, 17a are integrally formed. Between these rolling surfaces 17a, 13a and 17a, 14a, double row rolling elements 16, 16 are accommodated in a cage 19 so as to roll freely.
  • the outer member 17 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 17a and 17a are hardened in the range of 58 to 64 HRC by induction hardening. Has been processed.
  • the rolling element 16 is formed of ceramic made of silicon nitride. Since the rolling element 16 is made of ceramics having a Young's modulus approximately 1.5 times that of steel, the amount of deformation due to load is reduced. For this reason, high rigidity can be achieved, and the area of the contact ellipse that contacts the outer rolling surface 17a of the outer member 17 and the inner rolling surface 14a of the inner ring 14 can be reduced. Torque loss (hysteresis loss) and dynamic friction that occur when rolling between the rolling surfaces can be suppressed, and the rotational torque of the bearing can be reduced.
  • seals 20 and 21 are attached to the opening of the annular space formed between the outer member 17 and the inner member 15, and leakage of the lubricating grease sealed inside the bearing to the outside is reduced. Prevents lubricating oil, contamination, etc. from entering the bearing from the side.
  • the outer seal 20 is an integral type comprising a cored bar 22 fitted in the outer member 17 and a seal member 23 joined to the cored bar 22. It is composed of a seal.
  • the cored bar 22 is formed by pressing a steel plate such as an austenitic stainless steel plate (JIS standard SUS304) or a cold rolled steel plate (JIS standard SPCC), and has an inner peripheral end on the outer side of the outer member 17. It is press-fitted through a predetermined scissors.
  • the seal member 23 is made of synthetic rubber such as NBR (acrylonitrile-butadiene rubber) and is integrally joined to the core metal 22 by vulcanization adhesion.
  • the seal member 23 includes a side lip 23a extending obliquely outward in the radial direction, a dust lip 23b extending obliquely outward in the radial direction on the inner diameter side of the side lip 23a, and a bearing inner side (inner side). And a grease lip 23c extending in an inclined manner.
  • a base portion 18b on the inner side of the wheel mounting flange 18 is formed in a curved surface having an arc-shaped cross section, and a side lip 23a and a dust lip 23b are slidably contacted with the base portion 18b with a predetermined axial squeeze, and a grease lip 23c is predetermined.
  • the material of the seal member 23 is excellent in heat resistance and chemical resistance, such as HNBR (hydrogenated acrylonitrile butadiene rubber), EPDM (ethylene propylene rubber), etc., which are excellent in heat resistance. Examples thereof include ACM (polyacrylic rubber), FKM (fluororubber), and silicon rubber.
  • the inner-side seal 21 is an integral type comprising a cored bar 24 fitted into the outer member 17 and a seal member 25 joined to the cored bar 24. It is composed of a seal.
  • the core metal 24 is formed by pressing from a steel plate such as an austenitic stainless steel plate or a cold rolled steel plate, and is press-fitted into the inner periphery of the outer side end portion of the outer member 17 via a predetermined squeeze.
  • the seal member 25 is made of synthetic rubber such as ACM and is integrally joined to the cored bar 24 by vulcanization adhesion.
  • the seal member 25 integrally includes a main lip 25a that is slidably contacted with the outer diameter surface of the inner ring 14 and a grease lip 25b that is inclined and extended toward the bearing inner side (outer side).
  • a garter spring 25c is externally fitted to ensure a predetermined lip tension.
  • synthetic rubber such as ACM having excellent heat resistance and chemical resistance is used for the seal member 25
  • compatibility with the lubricating oil is good and oil leakage can be prevented over a long period of time.
  • the material of the seal member 25 include HNBR, EPDM, and the like having excellent heat resistance, FKM, silicon rubber, and the like other than ACM.
  • the 3rd generation structure was illustrated here as the wheel bearing apparatus 1, this invention is not restricted to this,
  • the second generation structure may be formed of a pair of inner rings in which the inner member is fitted onto the hub ring.
  • the wheel bearing device constituted by the double row angular contact ball bearing using balls as the rolling elements 16 is exemplified, the present invention is not limited to this, and it is constituted by a double row tapered roller bearing using tapered rollers. May be.
  • the reduction gear 3 is of a planetary gear type. As shown in FIG. 2A, the input shaft 5 and the output member 6, a sun gear 26 integrally formed on the outer diameter surface of the input shaft 5, and the sun gear 26 On the outer periphery, the ring gear 27 is disposed along the inner diameter surface of the boundary portion between the partition wall base 8 a and the partition wall member 10, and is fixed via the knock pin 27 a, and the ring gear 27 and the sun gear 26 are equally spaced in the circumferential direction. And the pinion gear 28 arranged in the same manner. The pinion gear 28 is supported by a pinion pin 30 via a needle roller bearing 29.
  • the output member 6 is integrally provided with a coupling shaft portion 31 at the outer end portion.
  • the coupling shaft portion 31 has a serration (or spline) 31 a engaged with the serration 13 c of the hub wheel 13 on the outer periphery, and a male screw 31 b formed at an end portion of the serration 31 a and is fastened by a fixing nut 32.
  • annular base portion 33 On the inner side of the coupling shaft portion 31, an annular base portion 33 having a one-step larger diameter is formed, and a pair of flanges 34 and 35 project from the annular base portion 33 radially outward.
  • the pair of flanges 34 and 35 are arranged to face each other in the axial direction with a space slightly larger than the width dimension of the pinion gear 28, and a bridge 36 for connecting the pair of flanges 34 and 35 in the axial direction is a circumference. It is provided in the direction equidistant position.
  • the pair of flanges 34 and 35 have a carrier function in the planetary gear type reduction gear 3.
  • the output member 6 can be smoothly rotated. As a result, the rotation accuracy of the rotor 42 of the motor 2 described later can be improved through the output member 6 and the input shaft 5. .
  • a shaft hole 37 coaxial with the coupling shaft portion 31 is formed on the end face of the inner flange 35 of the pair of flanges 34 and 35.
  • the shaft hole 37 has a depth that reaches the annular base 33.
  • the input shaft 5 is inserted into the shaft hole 37 and is supported by a pair of rolling bearings 39 and 39 made of deep groove ball bearings.
  • a pair of flanges 34 and 35 and a bridge 36 are provided with pinion gear accommodating portions partitioned in the circumferential direction.
  • the pinion gear 28 is accommodated in these accommodating portions and is integrated with the pair of flanges 34 and 35 via the pinion pin 30.
  • a locking hole 30a that penetrates in the radial direction is formed at the end of the pinion pin 30, and is fixed by a set screw (not shown) that is screwed into a screw hole 35a formed in the flange 35 on the inner side. Yes.
  • Thrust plates 38 and 38 are interposed between the side surfaces of each pinion gear 28 and the pair of flanges 34 and 35 in order to ensure smooth rotation of the pinion gear 28.
  • a pair of rolling bearings 39 and 39 are mounted in an annular space formed between the inner diameter surfaces of the pair of flanges 34 and 35 and the outer diameter surface of the input shaft 5 facing the inner diameter surfaces. It is supported by the member 6.
  • the support structure can be simplified, and vibrations and impacts transmitted from the wheel to the output member 6 can be detected by both rolling bearings 39. , 39 are simultaneously loaded in the same manner, so that it is possible to prevent an unbalanced load from acting on either of the rolling bearings 39, 39, and to improve rotational accuracy and durability. In addition, the generation of rotating noise can be suppressed.
  • the motor 2 is a radial gap type in which a radial gap is provided between a stator 40 fixed to the cylindrical portion 7 of the housing 4 and a rotor 42 attached by a rotor support member 41.
  • This is a brushless DC motor.
  • the rotor support member 41 includes a cylindrical support portion 41a fitted to the inner diameter portion of the rotor 42, a disk portion 41b extending radially inward from the cylindrical support portion 41a along the partition wall 12, and the disk portion 41b.
  • a cylindrical fixing portion 41c formed at the inner end of the cylinder is provided. The rotor support member 41 is fixed to the input shaft 5 via a key 41d locked to the cylindrical fixing portion 41c.
  • An oil seal 43 is mounted in an annular space formed between the center hole 11 of the partition wall member 10 and the cylindrical fixing portion 41c of the rotor support member 41. As shown in an enlarged view in FIG. 3B, the oil seal 43 is constituted by an integral oil seal including a cored bar 44 and a seal member 45 joined to the cored bar 44.
  • the core metal 44 is formed by pressing from a steel plate such as an austenitic stainless steel plate or a cold rolled steel plate.
  • the seal member 45 is made of synthetic rubber such as ACM and is integrally joined to the cored bar 44 by vulcanization adhesion.
  • the seal member 45 integrally includes a main lip 45a slidably in contact with the outer diameter surface of the cylindrical fixing portion 41c, and a sub lip 45b extending obliquely toward the inner side.
  • the main lip 45a includes a predetermined lip tightness.
  • a garter spring 45c is externally fitted to ensure the force.
  • the oil seal 43 prevents the lubricating oil on the speed reducer 3 side from moving to the motor 2 side, and the motor 2 side is maintained in a dry state, so that the lubricating oil may hinder the rotation of the rotor 42. Avoided.
  • examples of the material of the seal member 45 include HNBR, EPDM, and the like that are excellent in heat resistance, FKM, silicon rubber, and the like.
  • the motor 2 and the speed reducer 3 are within the range of the axial length of the cylindrical portion 7 of the housing 4 except for the rear end portion (end portion on the inner side) of the input shaft 5. Therefore, it is closed by a cover 47 attached to the rear end portion of the cylindrical portion 7 via an O-ring 46.
  • the O-ring 46 is made of a synthetic rubber such as ACM.
  • a rotation sensor 48 is disposed at the center of the cover 47.
  • the rotation sensor 48 is a resolver, the sensor stator 48 a is fixed to the cover 47, and the sensor rotor 48 b is attached to the input shaft 5.
  • the lead wire (not shown) of the sensor stator 48a is connected to a connector insertion portion (not shown) provided outside.
  • a Hall element or the like can be used in addition to the resolver.
  • the rotation angle of the input shaft 5 detected by the rotation sensor 48 is input to a control circuit via a signal line cable (not shown) and used for rotation control of the motor 2.
  • the output member 6 has a coupling shaft portion 31 formed on the outer end portion and a large diameter on the inner side of the coupling shaft portion 31.
  • An annular base 33 formed and a pair of flanges 34 and 35 projecting radially outward from the annular base 33 are provided.
  • the annular base 33 of the output member 6 is an ACM.
  • the hub ring 13 is fitted into the small-diameter step portion 13b through an O-ring 49 made of synthetic rubber or the like.
  • the side surface 50a of the holding part 50 which consists of a pair of flanges 34 and 35 and the bridge 36 which connects the pair of flanges 34 and 35 in the axial direction is brought into contact with the large end surface 14b of the inner ring 14 in abutment.
  • the large end surface 14 b of the inner ring 14 is in contact with the side surface 50 a of the holding portion 50 of the output member 6 so as to overlap with the insertion hole of the pinion pin 30.
  • the diameter of the inner ring 14 can be increased and abutted against the output member 6 at a position where the diameter of the inner ring 14 is one step larger, and the space is effectively utilized while ensuring the rigidity of the wheel bearing apparatus 1.
  • it is possible to provide an in-wheel motor-equipped wheel bearing device that can shorten the axial space and improve the rotational accuracy of the input shaft 5 and the durability of the bearing that supports the input shaft 5. .
  • the pinion pin 30 that supports the pinion gear 28 is fitted on the same surface or slightly recessed so as not to protrude from the end surface of the flange 34. Thereby, the contact
  • the seal 21 is slidably contacted with the outer diameter of the inner ring 14.
  • the axial space can be further shortened, and the lubricating grease sealed inside the bearing by the single seal 21 can be leaked to the outside. Can be prevented from entering, so that the rotational torque due to the seal sliding contact can be reduced.
  • the annular base portion 33 of the output member 6 is fitted and inserted into the small diameter step portion 13 b of the hub wheel 13 through the O-ring 49, and the outer member 17 is attached to the front end portion 8 of the housing 4 through the O-ring 51. Since it is inserted, it is possible to prevent rainwater and the like from entering from the outside, to prevent the lubricating oil in the speed reducer 3 from leaking to the outside, and to prevent the surrounding environment from being contaminated.
  • These O-rings 49 and 51 are made of synthetic rubber such as ACM.
  • an O-ring 49 may be interposed between the corner portion of the annular base portion 33 of the output member 6 and the end portion of the small diameter step portion 13 b of the hub wheel 13.
  • the process of the annular groove which mounts the O-ring 49 on the outer peripheral surface of the annular base 33 can be omitted, and the assembly process can be simplified and the cost can be reduced along with the simplification of the process process. it can.
  • the in-wheel type motor-equipped wheel bearing device according to the present invention is configured as described above, and the operation thereof will be described with reference to FIG.
  • the input shaft 5 is rotated integrally with the rotation of the rotor 42, and the motor output is input to the speed reducer 3.
  • the speed reducer 3 revolves while the pinion gear 28 rotates.
  • the output member 6 is rotated at a deceleration output having a predetermined reduction ratio. Then, the inner member 15 of the wheel bearing device 1 is rotated integrally with the coupling shaft portion 31 of the output member 6, and the wheel attached to the hub wheel 13 is driven.
  • the input shaft 5 is supported and rotated by a pair of rolling bearings 39 and 39 on both sides of the pinion gear 28, respectively. Since these rolling bearings 39 and 39 are both attached to the flanges 34 and 35 integral with the output member 6, as described above, the radial transmission from the wheel to the output member 6 through the wheel bearing device 1 is performed. Directional vibrations and shocks are simultaneously applied to both rolling bearings 39 and 39 in the same manner, and any rolling bearings 39 and 39 can be prevented from applying an unbalanced load.
  • both ends of the pinion pin 30 of the pinion gear 28 are supported by the pair of flanges 34 and 35, the support rigidity becomes high, and good engagement between the pinion gear 28, the ring gear 27, and the sun gear 26 can be obtained. And durability can be improved.
  • FIG. 6 is a longitudinal sectional view showing a second embodiment of the in-wheel motor-equipped wheel bearing device according to the present invention
  • FIG. 7 is an enlarged view of a main part showing a modification of the speed reducer in FIG.
  • FIG. 9 is an enlarged view of a main part showing a modification of the wheel bearing device in FIG. 6,
  • FIG. 9 is an enlarged view of a main part showing a modification of the wheel bearing device in FIG. 8
  • FIG. 10 is a wheel bearing in FIG. It is a principal part enlarged view which shows the modification of an apparatus.
  • the wheel bearing device and the housing are basically partially different from the embodiment described above, and the same reference numerals are given to the same parts or parts having the same function. Detailed description will be omitted.
  • This in-wheel type motor-equipped wheel bearing device includes a wheel bearing device 52 that rotatably supports a wheel (not shown), a motor 2 as a rotational drive source, and a motor 2 that decelerates rotation of the motor 2 to be described later.
  • the reduction gear 3 that transmits to the hub wheel 13 and the housing 53 that accommodates the reduction gear 3 and the motor 2 are the main constituent elements, and are arranged on the central axis O of the wheel.
  • the hub wheel 13 of the wheel bearing device 52 is rotated by the output member 6 coaxial with the input shaft 5 of the speed reducer 3.
  • the housing 53 includes a cylindrical portion 7 and a front end portion 54 at an outer end portion thereof, a center portion thereof is opened, and an outer member 56 of the wheel bearing device 52 is fitted into the opening portion 55 so that the vehicle body is attached.
  • the flange 56a is fastened to the front end portion 54 by the fixing bolt 17c.
  • a partition wall base 54a is formed coaxially with the opening 55 inside the front end portion 54 of the housing 53, and a cup-shaped partition wall member 10 is formed integrally with the partition wall base 54a. Thereby, the number of parts can be reduced, the assembly process can be simplified, and the cost can be reduced.
  • a center hole 11 is formed at the center of the partition member 10, and this center hole 11 faces the outer diameter surface of the support cylindrical portion 41 c of the rotor support member 41 through an annular space.
  • a partition wall 12 ′ is configured by the partition base 54 a and the partition member 10 formed integrally with the partition base 54 a.
  • the partition wall 12 ′ has a function of dividing the inside of the housing 53 into an accommodation space for the motor 2 on the outer diameter side and an accommodation space for the reduction gear 3 on the inner diameter side.
  • the wheel bearing device 52 is referred to as a third generation for driving wheels, and includes an inner member 15 including a hub wheel 13 and an inner ring 14 press-fitted into the hub wheel 13. And an outer member 56 inserted through the rolling elements 16 and 16.
  • the outer member 56 integrally has a vehicle body mounting flange 56a attached to the front end portion 54 of the housing 53 via a fixing bolt 17c on the outer periphery, and double row outer rolling surfaces 17a and 17a are integrally formed on the inner periphery.
  • This outer member 56 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 17a and 17a have a surface in the range of 58 to 64HRC by induction hardening. It has been cured.
  • seals 20 and 21 are attached to the opening of the annular space formed between the outer member 56 and the inner member 15, and leakage of the lubricating grease sealed inside the bearing to the outside is reduced. Prevents lubricating oil, contamination, etc. from entering the bearing from the side.
  • the speed reducer 3 is of a planetary gear type, and includes an input shaft 5 and an output member 6, a sun gear 26 integrally formed on the outer diameter surface of the input shaft 5, and a partition wall base portion on the outer periphery of the sun gear 26.
  • the ring gear 27 is disposed along the inner diameter surface of the boundary portion between the ring member 54 a and the partition wall member 10, and is fixed by a knock pin (not shown) and a retaining ring 57.
  • the ring gear 27 and the sun gear 26 are equally spaced in the circumferential direction.
  • the pinion gear 28 arranged in the above.
  • the outer member 56 constituting the wheel bearing device 52 is different from that of the above-described embodiment in that the vehicle body mounting flange 56a is increased in diameter radially outward, and the pilot portion 58 is provided at the outer diameter portion. Is formed.
  • the outer diameter d0 of the pilot portion 58 is set larger than the inner diameter d1 of the partition wall base portion 54a of the front end portion 54 in the housing 53 or the outer diameter of the ring gear 27. Then, the opening portion 55 of the front end portion 54 of the housing 53 is fitted to the pilot portion 58 via the O-ring 51.
  • FIG. 7 shows a modification of the speed reducer 3 in FIG. Similar to the above-described embodiment, a pilot portion 58 is formed on the outer diameter portion of the vehicle body mounting flange 56 a, and the opening portion 55 of the front end portion 54 of the housing 53 is fitted to the pilot portion 58 via the O-ring 51. .
  • the retaining ring 57 for preventing the ring gear 27 from coming off is abolished, and the ring gear 27 is in contact with the inner side surface 59 of the vehicle body mounting flange 56a of the outer member 56.
  • the ring gear 27 when the ring gear 27 or the pinion gear 28 is twisted, the ring gear 27 can be prevented from being pulled out by the side surface 59 of the vehicle body mounting flange 56a when the ring gear 27 is pulled out by the thrust component force. Therefore, at the time of assembly, the side surface 59 of the vehicle body mounting flange 56a does not necessarily have to contact the ring gear 27, and may face each other through a slight gap.
  • FIG. 8 shows a modification of the wheel bearing device 52 shown in FIG. Note that this embodiment is basically different from the above-described embodiment only in the specifications of the left and right rolling elements, and other parts and parts having the same parts or parts having the same functions are denoted by the same reference numerals. The detailed explanation is omitted.
  • the wheel bearing device 60 is referred to as a third generation for driving wheels.
  • An inner member 62 including a hub wheel 13 and an inner ring 61 press-fitted into the hub wheel 13, and the inner member 62 are arranged in a double row.
  • the hub wheel 13 integrally has a wheel mounting flange 18 at an end portion on the outer side, and has one inner rolling surface 13a and a small-diameter step portion 13b extending in the axial direction from the inner rolling surface 13a on the outer periphery.
  • a serration 13c for torque transmission is formed on the inner periphery.
  • the inner ring 61 is formed with the other inner rolling surface 61a on the outer periphery, and is press-fitted into the small-diameter step portion 13b of the hub ring 13 via a predetermined shimiro.
  • the inner ring 61 is made of a high carbon chrome steel such as SUJ2, and is hardened in the range of 58 to 64 HRC up to the core part by quenching.
  • the outer member 63 integrally has a vehicle body mounting flange 56a attached to the front end 54 of the housing 53 via a fixing bolt 17c on the outer periphery, and faces the inner rolling surfaces 13a and 61a of the inner member 62 on the inner periphery.
  • Double row outer rolling surfaces 17a and 63a are integrally formed. Between these rolling surfaces 17a, 13a and 63a, 61a, double-row rolling elements 16, 16a are accommodated in the cages 19, 19a so as to roll freely.
  • the outer member 63 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 17a and 63a are hardened in the range of 58 to 64HRC by induction hardening. Has been processed.
  • seals 20 and 21 ′ are attached to the opening portion of the annular space formed between the outer member 63 and the inner member 62, and leakage of the lubricating grease sealed inside the bearing is reduced. Lubricating oil, contamination, and the like are prevented from entering the bearing from the third side.
  • the inner-side seal 21 ' basically has the same specifications as the internal structure and the like, except that the above-described seal 21 has a large diameter.
  • the pitch circle diameter PCDi of the inner side rolling elements 16a among the double row rolling elements 16, 16a is set larger than the pitch circle diameter PCDo of the outer side rolling elements 16. (PCDi> PCDo). Due to the difference in pitch circle diameter PCDo, PCDi, the number of the left and right rolling elements 16, 16a is the same, but the diameter di of the inner rolling element 16a is larger than the diameter do of the outer rolling element 16. The diameter is set.
  • the pitch circle diameter PCDi of the inner-side rolling element 16a is set larger than the pitch circle diameter PCDo of the outer-side rolling element 16, and accordingly, the rolling elements 16 and 16a
  • the diameter di of the inner side rolling element 16a is set to be larger than the diameter do of the outer side rolling element 16, so that the bearing space is effectively utilized and the inner side is compared with the inner side.
  • the bearing life on the side can be increased, and the life of the bearing can be extended.
  • the diameter of the inner ring 61 can be increased and abutted against the output member 6 at a position where the diameter is one step larger, and the axial space can be shortened while ensuring the rigidity of the wheel bearing device 60.
  • FIG. 9 is a modification of the wheel bearing device 60 of FIG.
  • the wheel bearing device 64 is referred to as a third generation for driving wheels, and includes an inner member 66 composed of a hub wheel 13, an inner ring 65 press-fitted into the hub wheel 13, and a double row on the inner member 66. And an outer member 67 inserted through the rolling elements 16 and 16.
  • the hub wheel 13 integrally has a wheel mounting flange 18 at an end portion on the outer side, and has one inner rolling surface 13a and a small-diameter step portion 13b extending in the axial direction from the inner rolling surface 13a on the outer periphery.
  • a serration 13c for torque transmission is formed on the inner periphery.
  • the inner ring 65 is formed with the other inner rolling surface 65a on the outer periphery, and is press-fitted into the small-diameter step portion 13b of the hub ring 13 through a predetermined shimiro.
  • the inner ring 65 is made of high carbon chrome steel such as SUJ2, and is hardened in the range of 58 to 64 HRC up to the core part by quenching.
  • the outer member 67 integrally has a vehicle body mounting flange 56a attached to the front end 54 of the housing 53 via a fixing bolt 17c on the outer periphery, and faces the inner rolling surfaces 13a and 65a of the inner member 66 on the inner periphery.
  • Double row outer rolling surfaces 17a and 67a are integrally formed. Between these rolling surfaces 17a, 13a and 67a, 65a, double-row rolling elements 16, 16 are accommodated in the cages 19, 19b so as to roll freely.
  • the outer member 67 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 17a and 67a are hardened in the range of 58 to 64HRC by induction hardening. Has been processed.
  • seals 20 and 21 ′ are attached to the opening of the annular space formed between the outer member 67 and the inner member 66, leakage of the lubricating grease enclosed in the bearing inside, and reduction gears. Lubricating oil, contamination, and the like are prevented from entering the bearing from the third side.
  • the pitch circle diameter PCDi of the inner side rolling elements 16 of the double row rolling elements 16 and 16 is set to be larger than the pitch circle diameter PCDo of the outer side rolling elements 16. (PCDi> PCDo). Due to the difference in pitch circle diameters PCDo and PCDi, the size of the left and right rolling elements 16 and 16 is the same, but the number of inner side rolling elements 16 is set to be larger than the number of outer side rolling elements 16. ing.
  • the pitch circle diameter PCDi of the inner-side rolling element 16 is set to be larger than the pitch circle diameter PCDo of the outer-side rolling element 16.
  • the number of the inner side rolling elements 16 is set to be larger than the number of the outer side rolling elements 16, so that the bearings in the inner side portion are effectively utilized compared with the outer side by utilizing the bearing space.
  • the rigidity can be increased, and the rigidity of the bearing can be increased.
  • FIG. 10 is a modification of the wheel bearing device 64 of FIG.
  • the wheel bearing device 68 is referred to as a third generation for driving wheels, and includes an inner member 70 including a hub wheel 69, an inner ring 65 press-fitted into the hub wheel 69, and a double row of the inner member 70. And an outer member 67 inserted through the rolling elements 16 and 16.
  • the hub wheel 69 integrally has a wheel mounting flange 18 at an end portion on the outer side, and an inner rolling surface 13a and a small-diameter step portion 13b extending in the axial direction from the inner rolling surface 13a are formed on the outer periphery.
  • a serration 13c for torque transmission is formed on the inner periphery.
  • the hub wheel 69 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and includes the inner rolling surface 13a and the base portion 18b on the inner side of the wheel mounting flange 18 to the small diameter step portion 13b. As a result, the surface is hardened in the range of 58 to 64 HRC by induction hardening.
  • bolt holes 71a to which the wheel bolts 71 are fastened are formed at the circumferentially equidistant positions of the wheel mounting flanges 18. Then, after the brake rotor 72 and the wheel 73 are mounted on the wheel mounting flange 18 of the hub wheel 69, they are fixed by the wheel bolts 71.
  • a defect such as a scratch is generated in the threaded portion of the wheel bolt 71, not only can it be easily replaced on the market, but the wheel can be replaced for bolt replacement on the market as in the past. It is no longer necessary to secure a space on the inner side of the mounting flange 18, and repairability is improved, and the axial space can be reduced by that amount, and light weight and compactness can be achieved while securing rigidity.
  • FIG. 11 is a longitudinal sectional view showing a third embodiment of the in-wheel motor-equipped wheel bearing device according to the present invention
  • FIG. 12A is a main portion showing the wheel bearing device and the speed reducer of FIG.
  • FIG. 13 is an enlarged view of a main part showing one seal part of FIG. 13A
  • FIG. 13 is an enlarged view of a main part showing a wheel bearing device and an output member of FIG. 12, and
  • FIG. It is a principal part enlarged view which shows the modification of this.
  • This embodiment is basically the same as the first embodiment (FIG. 1) described above, except that the wheel bearing device and the housing are partially different, and other parts having the same parts or the same functions. The same reference numerals are given to the parts and the detailed description is omitted.
  • the in-wheel motor-equipped wheel bearing device includes a wheel bearing device 74 that rotatably supports a wheel (not shown), a motor 2 as a rotational drive source, and a motor 2 that decelerates the rotation of the motor 2 to be described later.
  • the reduction gear 3 that transmits to the hub wheel 75 and the housing 76 that accommodates the reduction gear 3 and the motor 2 are the main constituent elements, and are arranged on the central axis O of the wheel.
  • the hub wheel 75 of the wheel bearing device 74 is rotated by the output member 6 coaxial with the input shaft 5 of the speed reducer 3.
  • the housing 76 is made of an aluminum alloy such as A6063TE or ADC12, and includes a cylindrical portion 7 and a front end portion 8 at an outer end portion thereof. The central portion is opened, and a wheel bearing device is provided in the opening portion 9 ′. 74 bearing cases 77 are fitted, and a vehicle body mounting flange 77b is fastened to the front end 8 by a fixing bolt 17c.
  • a center hole 11 is formed at the center of the partition member 10, and this center hole 11 faces an outer diameter surface of a rotor support member 41 described later via an annular space.
  • a partition wall 12 is constituted by the partition wall base portion 8a and the partition wall member 10 connected to the partition wall base portion 8a.
  • the partition wall 12 has a function of dividing the housing 4 into a housing space for the motor 2 on the outer diameter side and a housing space for the speed reducer 3 on the inner diameter side. If the partition base 8a and the partition member 10 are formed integrally with the housing 75, the number of parts can be reduced, the assembly process can be simplified, and the cost can be reduced.
  • the wheel bearing device 74 is called the first generation for driving wheels, and as shown in an enlarged view in FIG. 12 (a), the hub wheel 75 and a bearing case (for example, a knuckle case) 77 and a fitting between them are fitted. And a combined wheel bearing 78.
  • a bearing case for example, a knuckle case
  • the hub wheel 75 integrally has a wheel mounting flange 16 for mounting a wheel (not shown) at an end portion on the outer side, and is formed with a small-diameter step portion 75b extending in the axial direction via a shoulder portion 75a.
  • a serration (or spline) 13c for torque transmission is formed around the circumference.
  • hub bolts 16 a are planted at the circumferentially equidistant positions of the wheel mounting flanges 16.
  • the hub wheel 75 is formed by die casting from an aluminum alloy such as A6061 or ADC12, and is heated to a high temperature to form a solid solution, followed by a quenching process in which it is rapidly cooled in water, and then kept at room temperature or at a low temperature (A precipitation hardening treatment is performed in which a large lattice strain is generated in the precipitated phase and hardened by a heat treatment composed of an age hardening treatment (tempering treatment) that is heated to 100 to 200 ° C. for precipitation.
  • Tempering treatment age hardening treatment
  • the strength can be increased to reduce the amount of aluminum used, and the weight can be reduced.
  • the bearing case 77 is formed by die casting from an aluminum alloy such as A6061 or ADC12, and is attached to the front end 8 of the housing 76 via a fixing bolt 17c on the outer periphery, and the flange 77a on the outer end. And an annular groove 77c is formed at the inner end of the inner periphery.
  • An outer ring 79 of a wheel bearing 78 (described later) is internally fitted until it abuts against the flange 77a, and is positioned and fixed in the axial direction by a retaining ring 80 attached to the annular groove 77c.
  • the bearing case 77 is formed by die casting from an aluminum alloy such as A6061 or ADC12, and is subjected to precipitation hardening, as with the hub wheel 75.
  • the wheel bearing 78 includes an outer ring 79 in which double row outer rolling surfaces 79a and 79a are integrally formed on the inner periphery, and an inner rolling surface 81a facing the double row outer rolling surfaces 79a and 79a on the outer periphery.
  • a pair of inner rings 81, 82 formed with 81 a and double row rolling elements 16, 16 accommodated in the cages 19, 19 between the rolling surfaces 79 a, 81 a are provided.
  • the outer ring 79 and the inner rings 81 and 82 are made of high carbon chrome steel such as SUJ2, and are hardened in the range of 58 to 64 HRC to the core part by quenching.
  • seals 83 and 21 are attached to openings of annular spaces formed between the outer ring 79 and the inner ring 81 on the outer side and between the front end 8 of the housing 76 and the inner ring 82 on the inner side, respectively. Leakage of the lubricating grease enclosed inside is prevented, and lubricating oil, contamination, etc. from the reduction gear 3 side are prevented from entering the bearing.
  • the outer side seal 83 is an integral seal composed of a cored bar 84 fitted into the outer ring 79 and a seal member 85 joined to the cored bar 84. It consists of The cored bar 84 is formed by press working from a steel plate such as an austenitic stainless steel plate or a cold rolled steel plate, and is press-fitted into the inner periphery of the outer side end portion of the outer ring 79 via a predetermined squeezing.
  • a steel plate such as an austenitic stainless steel plate or a cold rolled steel plate
  • the seal member 85 is made of synthetic rubber such as NBR and is integrally joined to the cored bar 84 by vulcanization adhesion.
  • the seal member 85 is formed in a bifurcated shape, and integrally includes a main lip 85a and a grease lip 85b that are slidably contacted with the outer diameter surface of the inner ring 81 via a predetermined radial shimoshiro.
  • examples of the material for the seal member 85 include HNBR, EPDM, etc., which are excellent in heat resistance, ACM, FKM, silicon rubber, etc., which are excellent in heat resistance and chemical resistance. Can do.
  • the inner-side seal 21 is fitted into the front end 8 of the housing 76, and is in sliding contact with the outer peripheral surface of the inner-side inner ring 82 via a predetermined shimiro. This seal 21 can prevent oil leakage over a long period of time.
  • wheel bearing 78 comprised by the double row angular contact ball bearing which used the ball for the rolling element 16 was illustrated here, not only this but the double row tapered roller bearing which uses the tapered roller for the rolling element. It may be configured.
  • the reduction gear 3 is of a planetary gear type. As shown in FIG. 12A, the input shaft 5 and the output member 6, a sun gear 26 integrally formed on the outer diameter surface of the input shaft 5, On the outer periphery, the ring gear 27 is disposed along the inner diameter surface of the boundary portion between the partition wall base portion 8a and the partition wall member 10 and fixed via the knock pin 27a. And pinion gears 28 arranged at three locations. The pinion gear 28 is supported by a pinion pin 30 via a needle roller bearing 29.
  • the output member 6 is integrally provided with a coupling shaft portion 31 at the outer end portion.
  • the coupling shaft portion 31 has a serration (or spline) 31a engaged with the serration 13c of the hub wheel 75 on the outer periphery, and a male screw 31b formed at the end of the serration 31a, and is fastened by a fixing nut 32.
  • annular base portion 33 On the inner side of the coupling shaft portion 31, an annular base portion 33 having a one-step larger diameter is formed, and a pair of flanges 34 and 35 project from the annular base portion 33 radially outward.
  • the pair of flanges 34 and 35 are arranged to face each other in the axial direction with a space slightly larger than the width dimension of the pinion gear 28, and a bridge 36 for connecting the pair of flanges 34 and 35 in the axial direction is a circumference. It is provided at three locations with equal orientation.
  • the pair of flanges 34 and 35 have a carrier function in the planetary gear type reduction gear 3.
  • the output member 6 can be smoothly rotated. As a result, the rotation accuracy of the rotor 41 of the motor 2 described later can be improved through the output member 6 and the input shaft 5. .
  • a shaft hole 37 coaxial with the coupling shaft portion 31 is formed on the end face of the inner flange 35 of the pair of flanges 34 and 35.
  • the shaft hole 37 has a depth that reaches the annular base 33.
  • the input shaft 5 is inserted into the shaft hole 37 and is supported by a pair of rolling bearings 39 and 39 made of deep groove ball bearings.
  • a pair of flanges 34 and 35 and three bridges 36 in the circumferential direction are provided with circumferentially defined pinion gear accommodating portions, in which the pinion gear 28 is accommodated and a pair of pinion gears 28 are interposed via the pinion pins 28.
  • the flanges 34 and 35 are integrally coupled.
  • a locking hole 30a that penetrates in the radial direction is formed at the end of the pinion pin 28, and is fixed by a set screw (not shown) that is screwed into a screw hole 35a formed in the flange 35 on the inner side. Yes.
  • the output member 6 has a coupling shaft portion 31 formed on the outer end portion and a large diameter on the inner side of the coupling shaft portion 31.
  • the formed annular base 33 and a pair of flanges 34 and 35 projecting radially outward from the annular base 33 are provided.
  • a small diameter step 75b of the hub wheel 75 is inserted through a seal ring 49 made of synthetic rubber or the like.
  • the side surface 50a of the holding portion 50 (34) including the pair of flanges 34 and 35 and the bridge 36 that connects the pair of flanges 34 and 35 in the axial direction is directly on the large end surface 82a of the inner ring 82 on the inner side.
  • the large end surface 82a of the inner ring 82 on the inner side of the wheel bearing 78 is abutted against the side surface 50a of the holding portion 50 so as to overlap with the hole into which the pinion pin 30 is inserted.
  • the diameter of the inner ring 82 on the inner side can be increased and abutted against the output member 6 at a position where the diameter is one step larger than that of the conventional device, and the axial space is secured while ensuring the rigidity of the wheel bearing device 74.
  • the pinion pin 30 that supports the pinion gear 28 is inserted so as not to protrude from the end face of the flange 34. Thereby, the contact
  • the seal 21 slides with the outer diameter of the inner ring 82.
  • the axial space can be further shortened, and the lubricating grease sealed inside the bearing by the single seal 21 can be leaked to the outside. Can be prevented from entering, so that the rotational torque due to the seal sliding contact can be reduced.
  • annular base portion 33 of the output member 6 is fitted into the small diameter step portion 75 b of the hub wheel 75 via the seal ring 49, and the bearing case 77 is fitted to the front end portion 8 of the housing 76 via the seal ring 51. Since it is inserted, it is possible to prevent rainwater and the like from entering from the outside, to prevent the lubricating oil in the speed reducer 3 from leaking to the outside, and to prevent the surrounding environment from being contaminated.
  • a seal ring 49 may be interposed between the corner of the annular base 33 of the output member 6 and the end of the small diameter step 75 b of the hub wheel 75.
  • the in-wheel type motor-equipped wheel bearing device according to the present invention is configured as described above, and the operation thereof will be described with reference to FIG.
  • the input shaft 5 is rotated integrally with the rotation of the rotor 41, and the motor output is input to the speed reducer 3.
  • the speed reducer 3 revolves while the pinion gear 28 rotates.
  • the output member 6 is rotated at a deceleration output having a predetermined reduction ratio. Then, the hub wheel 75 of the wheel bearing device 74 is rotated integrally with the coupling shaft portion 31 of the output member 6, and the wheel attached to the wheel mounting flange 16 of the hub wheel 75 is driven.
  • the input shaft 5 is supported and rotated by a pair of rolling bearings 39 and 39 on both sides of the pinion gear 28, respectively. Since these rolling bearings 39 and 39 are both attached to the flanges 34 and 35 integral with the output member 6, as described above, the radial is transmitted from the wheel to the output member 6 via the wheel bearing device 74. Directional vibrations and shocks are simultaneously applied to both rolling bearings 39 and 39 in the same manner, and any rolling bearings 39 and 39 can be prevented from applying an unbalanced load.
  • both ends of the pinion pin 30 of the pinion gear 28 are supported by the pair of flanges 34 and 35, the support rigidity becomes high, and good engagement between the pinion gear 28, the ring gear 27, and the sun gear 26 can be obtained. And durability can be improved.
  • FIG. 15 is a modification of the wheel bearing device (FIG. 11) described above. Note that this embodiment is basically different from the third embodiment described above only in the configuration of the wheel bearing device, and the same reference numerals are used for the same parts and parts having the same functions or the same functions. The detailed description is omitted.
  • the output member 6 is fitted and inserted into the hub wheel 75 constituting the wheel bearing device 74 via the serration 31a.
  • the holding portion 50 of the output member 6 is in contact with the large end surface 82 a of the inner ring 82 on the inner side via a washer 86.
  • the fixing nut 32 is screwed to the threaded portion 31 b of the coupling shaft portion 31 of the output member 6 with a predetermined torque via a washer 87.
  • Washers 86 and 87 are made of a light alloy such as an aluminum alloy. Since the aluminum alloy bearing case 77 has a larger linear expansion coefficient than the steel outer ring 79, inner rings 81 and 82 and the output member 6, when the temperature rises while the vehicle is running, the amount of expansion of the bearing case 77 is large. Thus, the internal clearance (axial clearance) of the wheel bearing 78 may be increased, but the increase of the internal clearance can be suppressed by these washers 86 and 87.
  • FIG. 16 shows a modification of the wheel bearing device 74 shown in FIG.
  • This embodiment basically differs from the above-described embodiment only in the specifications of the left and right rolling elements of the wheel bearing, and the same reference numerals are given to the same parts or parts having the same function. Detailed description will be omitted.
  • the wheel bearing device 88 is referred to as a first generation for driving wheels, and includes a hub wheel 75, a bearing case 77, and a wheel bearing 89 fitted therebetween.
  • This wheel bearing 89 includes an outer ring 90 in which double-row outer rolling surfaces 90a and 79a are integrally formed on the inner periphery, and an inner rolling surface 91a facing the double-row outer rolling surfaces 90a and 79a on the outer periphery. , 81a, a pair of inner rings 91, 82, and double-row rolling elements 16a, 16 accommodated between the rolling surfaces 90a, 91a and 79a, 81a in the cages 19a, 19 so as to roll freely. It has.
  • the outer ring 90, the inner ring 91 and the rolling element 19a are made of high carbon chrome steel such as SUJ2, and are hardened in the range of 58 to 64 HRC up to the core part by quenching.
  • seals 83 and 21 are attached to the openings of the annular spaces formed between the outer ring 90 and the outer side inner ring 91 and between the front end 8 of the housing 76 and the inner side inner ring 82, respectively. Leakage of the lubricating grease enclosed inside is prevented, and lubricating oil, contamination, etc. from the reduction gear 3 side are prevented from entering the bearing.
  • the pitch circle diameters of the double row rolling elements 16a, 16 are the same, but the diameter do of the outer side rolling element 16a is larger than the diameter di of the inner side rolling element 16.
  • the number Zi of the inner side rolling elements 16 is set to be larger (Zi> Zo) than the number Zo of the outer side rolling elements 16a.
  • the pitch circle diameters of the double row rolling elements 16a, 16 are the same, but the diameter do of the outer rolling element 16a is larger than the diameter di of the inner rolling element 16. Since the number Zi of the inner side rolling elements 16 is set to be larger than the number Zo of the outer side rolling elements 16a, the life of the outer side bearing row can be effectively utilized by utilizing the bearing space.
  • the bearing rigidity of the inner side portion can be increased as compared with the outer side.
  • FIG. 17 shows another modification of the wheel bearing device 74 shown in FIG.
  • the wheel bearing device 92 is called a first generation for driving wheels, and includes a hub wheel 93, a bearing case 77, and a wheel bearing 78 fitted therebetween.
  • the hub wheel 93 integrally has a wheel mounting flange 16 at an end portion on the outer side, a small diameter step portion 75b extending in the axial direction via a shoulder portion 75a is formed, and a serration 13c for torque transmission is formed on the inner periphery.
  • the hub wheel 93 is formed by die casting from an aluminum alloy such as A6061 or ADC12 and subjected to precipitation hardening.
  • bolt holes 71a to which the wheel bolts 71 are fastened are formed at the circumferentially equidistant positions of the wheel mounting flanges 16. Then, after the brake rotor 72 and the wheel 73 are mounted on the wheel mounting flange 94 of the hub wheel 93, they are fixed by the wheel bolts 71.
  • a defect such as a scratch is generated in the threaded portion of the wheel bolt 71, not only can it be easily replaced on the market, but the wheel can be replaced for bolt replacement on the market as in the past. It is no longer necessary to secure a space on the inner side of the mounting flange 94, repairability is improved, and the axial space can be reduced by that amount, so that lightweight and compactness can be achieved while securing rigidity.
  • the wheel bearing device with a built-in in-wheel motor is a combination of a wheel bearing device, a speed reducer, and a motor, and the wheel bearing device becomes an inner member serving as a rotating member and a stationary member.
  • the present invention can be applied to first generation to third generation structures provided with outer members.

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Abstract

La présente invention a pour objectif un dispositif de palier destiné à une roue dotée d'un moteur intégré dans la roue, le dispositif de palier ayant une rigidité, étant léger et compact, et améliorant la précision de rotation d'un arbre d'entrée. Pour ce faire, un réducteur de vitesse (3) est configuré à partir d'un satellite comprenant un planétaire (26) qui est disposé sur la périphérie extérieure d'un arbre d'entrée (5), d'une couronne dentée (27) qui est fixée à un carter (4) et d'engrenages à pignons (28) qui sont disposées à intervalles égaux dans la direction circonférentielle. Un organe de sortie (6) est doté : d'une section arbre de raccordement (31) qui est introduite dans une bague de moyeu (13) et qui a une périphérie extérieure installée sur la bague de moyeu (13); d'une section base annulaire (33) qui est formée pour avoir un grand diamètre sur l'intérieur de la section arbre de raccordement (31); de deux brides (34, 35) qui font saillie vers l'extérieur dans la direction radiale depuis la section base annulaire (33) de manière à se faire mutuellement face dans la direction axiale et qui contiennent les engrenages à pignons (28) situées entre les deux brides (34, 35); et d'une section de maintien (50) qui comprend un élément de liaison (36) destiné à relier les deux brides l'une à l'autre dans la direction axiale. Une surface latérale (50a) de la section de maintien (50) est créée pour être en contact avec la surface de grande extrémité (14b) d'une bague intérieure (14) de manière à être contiguë à celle-ci, et l'organe de sortie (6) est fixé à la bague de moyeu (13) par un écrou de fixation (32) de sorte qu'un couple puisse être transmis entre l'organe de sortie (6) et la bague de moyeu (13).
PCT/JP2012/074959 2011-09-28 2012-09-27 Dispositif de palier pour roue doté d'un moteur intégré dans la roue WO2013047695A1 (fr)

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JP2011212161A JP2013071599A (ja) 2011-09-28 2011-09-28 インホイール型モータ内蔵車輪用軸受装置
JP2011-212161 2011-09-28
JP2011250571A JP5913925B2 (ja) 2011-11-16 2011-11-16 インホイール型モータ内蔵車輪用軸受装置
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CN105270161A (zh) * 2015-10-28 2016-01-27 湖北航天技术研究院特种车辆技术中心 一种轮边电机驱动装置
CN107117005A (zh) * 2017-04-27 2017-09-01 北京理工大学 一种动力传动一体化电动轮
CN108128143A (zh) * 2017-08-28 2018-06-08 泰安航天特种车有限公司 一种集成式电动轮及车辆
EP3398835A1 (fr) * 2017-05-03 2018-11-07 ArvinMeritor Technology, LLC Ensemble d'extrémité de roue ayant une bague de compression et procédé d'assemblage
CN109689396A (zh) * 2016-09-12 2019-04-26 Ntn株式会社 车轮用轴承装置
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CN110254219A (zh) * 2018-03-12 2019-09-20 舍弗勒技术股份两合公司 法兰轴、法兰轴组件和轮毂驱动系统
CN111376706A (zh) * 2018-12-28 2020-07-07 沈阳新松机器人自动化股份有限公司 一种轮毂转接结构
FR3097289A1 (fr) * 2019-06-11 2020-12-18 Ntn-Snr Roulements Module de transmission d’un couple moteur tournant
US10899174B2 (en) 2018-03-15 2021-01-26 Arvinmeritor Technology, Llc Wheel end assembly having a compression ring and method of assembly
EP4147896A1 (fr) * 2021-09-10 2023-03-15 Hyundai Mobis Co., Ltd. Dispositif d'entraînement de roue

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CN109689396B (zh) * 2016-09-12 2022-07-29 Ntn株式会社 车轮用轴承装置
CN107117005A (zh) * 2017-04-27 2017-09-01 北京理工大学 一种动力传动一体化电动轮
CN107117005B (zh) * 2017-04-27 2019-06-14 北京理工大学 一种动力传动一体化电动轮
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