WO2016043011A1 - Dispositif d'entraînement de moteur placé dans la roue - Google Patents

Dispositif d'entraînement de moteur placé dans la roue Download PDF

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Publication number
WO2016043011A1
WO2016043011A1 PCT/JP2015/074241 JP2015074241W WO2016043011A1 WO 2016043011 A1 WO2016043011 A1 WO 2016043011A1 JP 2015074241 W JP2015074241 W JP 2015074241W WO 2016043011 A1 WO2016043011 A1 WO 2016043011A1
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WO
WIPO (PCT)
Prior art keywords
wheel
bearing
drive device
input shaft
motor drive
Prior art date
Application number
PCT/JP2015/074241
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English (en)
Japanese (ja)
Inventor
鈴木　稔
朋久 魚住
Original Assignee
Ntn株式会社
鈴木　稔
朋久 魚住
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Application filed by Ntn株式会社, 鈴木　稔, 朋久 魚住 filed Critical Ntn株式会社
Publication of WO2016043011A1 publication Critical patent/WO2016043011A1/fr

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    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
    • 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
    • F16C33/34—Rollers; Needles
    • 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
    • F16C33/62—Selection of substances
    • 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
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • 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
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/64—Electric machine technologies in electromobility

Definitions

  • the present invention relates to an in-wheel motor drive device.
  • the size of the in-wheel motor drive device affects the size of the cabin space because the entire device is housed inside the wheel or disposed near the wheel. Moreover, since the in-wheel motor drive device becomes the unsprung weight of the vehicle, the weight affects the riding comfort of the vehicle. For this reason, the in-wheel motor drive device needs to be as light and compact as possible. On the other hand, the in-wheel motor drive device requires a large torque to drive the wheels. In order to satisfy these requirements at the same time, for example, in Patent Document 1 below, a high-rotation type motor that rotates at a rotational speed of, for example, about 15000 min ⁇ 1 is adopted as a motor unit that generates a driving force. There has been proposed an in-wheel motor drive device that employs a cycloid reducer that is compact and can provide a high reduction ratio in a reduction part that reduces rotation and transmits it to a wheel bearing part.
  • the speed reduction part to which the cycloid reduction gear is applied mainly has an eccentric part, and is held rotatably on the outer periphery of the eccentric part via a reduction gear input shaft that rotates by receiving the driving force of the motor part and a rolling bearing.
  • the output of the reducer connected to the wheel bearing section is the curved plate that performs the revolving motion centered on the rotation axis as the reducer input shaft rotates, and the rotational motion that occurred on the curved plate during the revolving motion.
  • a motion conversion mechanism that converts the rotational motion of the shaft.
  • the reduction gear input shaft rotates at a high speed as described above, and accordingly, between the reduction gear input shaft and the curved plate.
  • the provided rolling bearing also rotates at high speed.
  • a large load mainly radial load
  • the reduction gear input shaft of the speed reduction portion is driven to rotate by receiving the output of the motor portion, and if a curved plate or the like rotates accordingly, even if a lubrication mechanism for supplying lubricating oil to the speed reduction portion is provided, the speed reducer In the rolling bearing provided between the input shaft and the curved plate, the temperature rise of the entire bearing and the temperature difference between the inner raceway surface and the outer raceway surface become larger than expected. Under such conditions, not only the radial internal clearance (initial clearance) of the rolling bearing itself decreases due to the engagement with the reducer input shaft (clearance after assembly), but the clearance further increases due to the temperature factors described above. Decrease (driving clearance).
  • the present invention has been proposed in view of the above points, and it is an object of the present invention to improve the durability of an in-wheel motor drive device and prevent the occurrence of vibration and abnormal noise.
  • the present invention proposed to achieve the above-described object includes a motor unit, a reduction unit, and a wheel bearing unit, and the rotational driving force of the motor unit is decelerated by the reduction unit and the wheel bearing unit is provided.
  • An in-wheel motor drive device for transmitting to the motor wherein the speed reduction part has an eccentric part, a speed reducer input shaft connected to the rotating shaft of the motor part, and a speed reducer connected to the wheel bearing part
  • a structure characterized in that the initial
  • the initial radial internal clearance is set to 15 ⁇ m or more, so that the temperature rise of the entire bearing and the inner raceway surface of the bearing Even considering the temperature difference on the outer raceway surface, the radial internal clearance (operational clearance) during operation does not become negative, and early peeling and seizure can be prevented. Further, in the above-described rolling bearing, the initial radial internal clearance is set to 60 ⁇ m or less, so that the generation of sound and vibration due to an excessive positive clearance can be suppressed.
  • the initial radial internal clearance of the rolling bearing means the radial internal clearance (diameter clearance) of the rolling bearing alone before assembling other members at room temperature.
  • the bearing ring (member having a raceway surface) constituting the rolling bearing is made of bearing steel or carburized steel, is subjected to carbonitriding, has a surface austenite of 25 to 50%, and has a core.
  • the residual austenite in the part is preferably 15 to 20%. In this way, it is possible to improve the rolling fatigue life and to suppress the generation and development of cracks due to retained austenite, thereby improving the durability (longer life) of the in-wheel motor drive device. be able to. Further, in order to ensure the same life, it is possible to reduce the thickness of the bearing ring as compared to the case where the bearing ring not having the above configuration is employed.
  • the in-wheel motor drive device can be reduced in size and weight through, for example, downsizing the rolling bearing in the radial direction.
  • the surface layer is a region obtained by nitriding to the depth affected by the surface pressure of the rolling element on the surface of the race (the raceway surface), and the core portion is formed with a nitride layer deeper than the surface layer. Say no area.
  • the bearing ring constituting the rolling bearing is made of bearing steel containing Si of 0.35 wt% or more and Mn of 0.50 wt% or more.
  • Si contributes to the improvement of the amount of retained austenite in the surface layer part by increasing the stability of austenite and Mn ensuring the hardenability.
  • the rolling elements constituting the rolling bearing are preferably made of bearing steel, subjected to carbonitriding, and the amount of retained austenite in the surface layer portion is preferably 20 to 35%.
  • FIG. 2 is a cross-sectional view taken along line ZZ in FIG. 1. It is explanatory drawing which shows the load which acts on a curve board. It is sectional drawing of a rotary pump. It is a schematic plan view of an electric vehicle. It is the schematic sectional drawing which looked at the electric vehicle of Drawing 6 from back.
  • the electric vehicle 11 is configured to drive an chassis 12, a pair of front wheels 13 that function as steering wheels, a pair of rear wheels 14 that function as drive wheels, and a left and right rear wheel 14.
  • a wheel motor drive device 21 As shown in FIG. 7, the rear wheel 14 is accommodated in the wheel housing 12a of the chassis 12, and is fixed to the lower portion of the chassis 12 via a suspension device (suspension) 12b.
  • the suspension device 12b supports the rear wheel 14 by a suspension arm extending left and right, and suppresses vibration of the chassis 12 by absorbing vibration received by the rear wheel 14 from the road surface by a strut including a coil spring and a shock absorber. Furthermore, a stabilizer that suppresses the inclination of the vehicle body during turning or the like is provided at a connecting portion of the left and right suspension arms.
  • the suspension device 12b is an independent suspension type in which the left and right wheels can be moved up and down independently in order to improve the followability to the road surface unevenness and efficiently transmit the driving force of the rear wheel 14 to the road surface. desirable.
  • an in-wheel motor drive device 21 that rotates each of the left and right rear wheels 14 is incorporated in the left and right wheel housings 12 a, so that a motor, a drive shaft, a differential gear mechanism, and the like are mounted on the chassis 12. There is no need to provide it. Therefore, the electric vehicle 11 has an advantage that a large cabin space can be secured and the rotation of the left and right rear wheels 14 can be controlled.
  • an in-wheel motor drive device 21 according to an embodiment of the present invention is employed.
  • the in-wheel motor drive device 21 includes a motor unit A that generates a driving force, a deceleration unit B that decelerates and outputs the rotation of the motor unit A, and outputs from the deceleration unit B to the rear wheels. 14 (see FIGS. 6 and 7), and a wheel bearing portion C that is transmitted to 14 (see FIGS. 6 and 7).
  • the in-wheel motor drive device 21 has a lubrication mechanism that supplies lubricating oil to the motor part A and the speed reduction part B.
  • the motor part A and the speed reduction part B are mounted in the wheel housing 12a (see FIG.
  • the casing 22 of this embodiment is comprised by fastening the part which accommodated the motor part A, and the part which accommodated the deceleration part B with the volt
  • the motor part A includes a stator 23a fixed to the casing 22, a rotor 23b disposed opposite to the inside of the stator 23a via a radial gap, and a hollow rotating shaft (motor) mounted with a rotor 23b on the outer periphery.
  • the rotary shaft 24 is capable of rotating at a rotational speed of about 15000 min ⁇ 1 .
  • the motor rotating shaft 24 has ends on one side in the axial direction (right side in FIG. 1, hereinafter also referred to as “inboard side”) and the other side (left side in FIG. 1 and hereinafter also referred to as “outboard side”).
  • the bearings are rotatably supported with respect to the casing 22 by rolling bearings (deep groove ball bearings in the illustrated example) 36, 36 disposed in the respective portions.
  • the wheel bearing portion C includes a hub ring 32 having a hollow structure and a wheel bearing 33 that rotatably supports the hub ring 32 with respect to the casing 22.
  • the hub wheel 32 extends radially outward from the cylindrical hollow portion 32a connected to the shaft portion 28b of the reduction gear output shaft 28 constituting the speed reduction portion B, and the end portion on the outboard side of the hollow portion 32a.
  • the flange portion 32b is integrally provided.
  • the rear wheel 14 (see FIGS. 6 and 7) is connected and fixed to the flange portion 32b by a bolt 32c. Accordingly, when the hub wheel 32 rotates, the rear wheel 14 rotates integrally with the hub wheel 32.
  • the wheel bearing 33 is a double row angular contact ball bearing. Specifically, one inner raceway surface 33 f is directly formed on the outer peripheral surface of the hub wheel 32, and the other inner side is formed on the outer peripheral surface of the inner ring 33 a fitted to the small diameter step portion of the outer peripheral surface of the hub wheel 32. A raceway surface is formed. A double-row outer raceway surface is formed on the inner peripheral surface of the outer ring 33 b fitted and fixed to the inner peripheral surface of the casing 22. A plurality of balls 33c are arranged between the double row inner raceway surface and the double row outer raceway surface. The balls 33c in each row are held in a state of being separated in the circumferential direction by a holder 33d. Both end portions in the axial direction of the wheel bearing 33 are sealed with seal members 33e.
  • the speed reduction unit B is decelerated by the speed reducer input shaft 25 that is rotationally driven by the motor unit A, a speed reduction mechanism that decelerates the rotation of the speed reducer input shaft 25, and a speed reduction mechanism.
  • a reduction gear output shaft 28 for transmitting the rotation of the reduction gear input shaft 25 to the hub wheel 32 of the wheel bearing portion C.
  • the reduction gear input shaft 25 and the reduction gear output shaft 28 are arranged coaxially.
  • the reduction gear input shaft 25 has a spline 25g (including serrations; the same applies hereinafter) formed on the outer periphery of the end portion on the inboard side.
  • a spline 25g (including serrations; the same applies hereinafter) formed on the outer periphery of the end portion on the inboard side.
  • the speed reducer input shaft 25 is rotatably supported with respect to the speed reducer output shaft 28 by rolling bearings 37a and 37b that are spaced apart from each other in two axial directions.
  • One rolling bearing 37a supports a substantially central portion of the reduction gear input shaft 25 in the axial direction
  • the other rolling bearing 37b supports an end portion of the reduction gear input shaft 25 on the outboard side.
  • Eccentric portions 25 a and 25 b whose shaft centers are eccentric with respect to the rotational axis of the speed reducer input shaft 25 are provided at two locations in the axial direction of the speed reducer input shaft 25.
  • the eccentric portions 25a and 25b are formed in a disc shape whose center is offset from the rotation center of the speed reducer input shaft 25 (see FIG. 3).
  • the eccentric portions 25 a and 25 b are provided integrally with the speed reducer input shaft 25.
  • the eccentric portions 25a and 25b are provided with a phase difference of 180 ° in order to cancel the centrifugal force due to the eccentric motion.
  • the counterweight 29 is fixed to the speed reducer input shaft 25 (see FIG. 2).
  • the counterweight 29 has a substantially fan shape and is fixed to the outer peripheral surface of the speed reducer input shaft 25.
  • the counterweight 29 changes the phase of the eccentric portions 25a, 25b and 180 ° to positions adjacent to the eccentric portions 25a, 25b in order to cancel out the unbalanced inertial couple (unbalance) caused by the rotation of the curved plates 26a, 26b. Arranged.
  • the reduction gear output shaft 28 has a shaft portion 28b and a flange portion 28a.
  • the flange portion 28a has a hole portion (through hole in the illustrated example) in which an end portion on the outboard side of the inner pin 31 described later is fitted and fixed.
  • the hole portion serves as a rotational axis of the speed reducer output shaft 28.
  • a plurality are formed at equal intervals on the circumference of the center.
  • the shaft portion 28b is connected to the hub wheel 32 constituting the wheel bearing portion C by spline fitting.
  • the reduction gear output shaft 28 is rotatably supported by the outer pin housing 60 via rolling bearings 48 and 48 that are spaced apart from each other in two axial directions.
  • the speed reduction mechanism rotates on the outer periphery of the eccentric portions 25a and 25b via the rolling bearings 40 and 40 disposed on the outer periphery of the eccentric portions 25a and 25b of the speed reducer input shaft 25.
  • Curved plates 26a and 26b that are freely held, a plurality of outer pins 27 fixed to the outer pin housing 60, and a motion conversion mechanism that converts the rotational motion of the curved plates 26a and 26b to the rotational motion of the reducer output shaft 28.
  • the outer peripheral surface of the curved plate 26a has a corrugated shape composed of a trochoidal curve such as an epitrochoid.
  • a plurality of axial through holes 30a are formed in the curved plate 26a.
  • the plurality of through holes 30a are provided at equal intervals on a circumference centered on the rotation axis of the curved plate 26a (centers of the eccentric portions 25a and 25b).
  • One inner pin 31 is inserted into each through-hole 30a.
  • An axial through hole 30b is formed in the axial center of the curved plate 26a.
  • a rolling bearing 40 and an eccentric portion 25a are disposed on the inner periphery of the through hole 30b.
  • the rolling bearing 40 includes an inner raceway surface 42, an outer raceway surface 43, and a plurality of cylindrical rollers as rolling elements disposed between the raceway surfaces 42 and 43. 44 and a cylindrical roller bearing provided with a retainer 45 for holding a plurality of cylindrical rollers 44.
  • the inner raceway surface 42 is formed on the outer circumference surface of the inner ring 41 fitted and fixed to the outer circumference surface of the eccentric portion 25a, and the outer raceway surface 43 is directly on the inner circumference surface of the through hole 30b of the curved plate 26a. It is formed.
  • the inner ring 41 has flange portions 46 and 46 that protrude from the both end portions in the axial direction of the inner raceway surface 42 toward the outer diameter side.
  • the curved plate 26b has a structure similar to that of the curved plate 26a, and an eccentric portion via a rolling bearing 40 similar to the rolling bearing 40 that supports the curved plate 26a. 25b is rotatably held.
  • each outer pin 27 is rotatably held by an outer pin housing 60 fixed to the casing 22 via a pair of needle roller bearings 61, 61 disposed at both ends in the axial direction. Has been.
  • the motion conversion mechanism includes a plurality of inner pins 31 fixed to the flange portion 28a of the reduction gear output shaft 28, and a plurality of through holes 30a provided in the curved plates 26a and 26b. Consists of.
  • the inner pins 31 are arranged at equal intervals on the circumference centering on the rotational axis of the reduction gear output shaft 28, and the end portion on the outboard side is provided on the flange portion 28 a of the reduction gear output shaft 28. It is fixed to the hole.
  • a needle roller bearing 31a is provided on the outer periphery of the inner pin 31.
  • the inner diameter dimension of the through hole 30a refers to the outer diameter dimension of the inner pin 31 ("maximum outer diameter including the needle roller bearing 31a") so that the revolving motion of the curved plates 26a and 26b is not hindered by the inner pin 31. It is set larger than the same).
  • the deceleration unit B further includes a stabilizer 31 b.
  • the stabilizer 31b integrally includes an annular ring portion 31c and a cylindrical portion 31d extending from the inner peripheral end of the annular portion 31c to the inboard side.
  • the end portion on the inboard side of each inner pin 31 is fixed to the annular portion 31c.
  • the axis O 2 of the eccentric portion 25 a provided on the speed reducer input shaft 25 is eccentric from the axis O of the speed reducer input shaft 25 by the amount of eccentricity e.
  • Eccentric portion 25a so that rotatably holds the curved plate 26a via a rolling bearing 40, the axis O 2 is also the axis of the curved plate 26a.
  • the outer periphery of the curved plate 26a is formed in a corrugated curve, and has corrugated recesses 34 that are recessed toward the inner diameter side at equal intervals in the circumferential direction.
  • a plurality of outer pins 27 that engage with the recesses 34 are arranged in the circumferential direction with the axis O as the center.
  • the speed reducer output shaft 28 has a higher torque and a lower rotational speed than the speed reducer input shaft 25, and the curved plate 26a receives a load Fj as indicated by arrows in the figure from the plurality of inner pins 31.
  • a resultant force Fs of the plurality of loads Fi and Fj is applied to the reduction gear input shaft 25.
  • the direction of the resultant force Fs varies depending on geometrical conditions such as the waveform shape of the outer peripheral portion of the curved plate 26a, the number of the concave portions 34, and the influence of centrifugal force. Specifically, the angle ⁇ between the reference line X perpendicular to the straight line Y connecting the rotation axis O 2 and the axis O and passing through the axis O 2 and the resultant force Fs varies in a range of approximately 30 ° to 60 °. .
  • the directions and magnitudes of the loads Fi and Fj fluctuate while the reduction gear input shaft 25 makes one rotation (360 °), and as a result, the direction and magnitude of the resultant force Fs acting on the reduction gear input shaft 25 also fluctuates. To do.
  • the rolling bearing (cylindrical roller bearing) 40 that supports the curved plates 26a and 26b receives a radial load and a moment load that vary in the direction and size of the load in addition to the high-speed rotation. Will be loaded.
  • the temperature difference between the inner and outer rings of the rolling bearing 40 in this embodiment, the inner ring 41 and the curved plates 26a and 26b
  • the initial clearance ⁇ 0 of the rolling bearing 40 is set, if the amount of the initial clearance ⁇ 0 is as small as possible, the operating clearance becomes negative and heat is generated, resulting in early separation and seizure. There was found.
  • the value of the initial clearance ⁇ 0 of the rolling bearing 40 may be increased.
  • various values arranged in the speed reduction portion B are used. Vibration due to the rotation of the rotating body may occur, or abnormal noise or vibration may occur due to the contact between the curved plates 26a and 26b and the outer pin 27 and the inner pin 31. It has been found that the in-wheel motor drive device 21 equipped with the cycloid reduction gear is sensitive to these abnormal sounds and vibrations.
  • the rolling bearing 40 of the in-wheel motor drive device 21 of the present embodiment is used in a special environment involving various factors. Therefore, in the present embodiment, the initial radial internal clearance (initial clearance ⁇ 0) of the rolling bearing 40 is set to 15 to 60 ⁇ m, preferably 15 to 45 ⁇ m, in the speed reduction portion B of the in-wheel motor drive device 21.
  • the initial radial internal clearance (initial clearance ⁇ 0) of the rolling bearing 40 is set to 15 to 60 ⁇ m, preferably 15 to 45 ⁇ m, in the speed reduction portion B of the in-wheel motor drive device 21.
  • heat generation and seizure of the rolling bearing 40 can be prevented even under conditions such as fitting (press fitting) with the speed reducer input shaft 25, temperature rise, and temperature difference between the inner and outer rings, and noise and vibration can be prevented. It is possible to minimize the degradation of the NVH characteristics due to the influence of the effect within the processable range.
  • the rolling bearing 40 includes an outer ring (curved plates 26 a and 26 b), an inner ring 41, a cylindrical roller 44, and a cage 45, and the speed reducer input shaft 25 is inserted into the inner periphery of the inner ring 41.
  • the radial internal clearance of the previous rolling bearing 40 alone at room temperature is the initial clearance ⁇ 0.
  • the bearing rings (inner ring 41 and curved plates 26a and 26b) of the rolling bearing 40 are made of bearing steel or carburized steel.
  • the bearing steel for example, a high carbon chromium bearing steel specified in JIS G 4805 can be used, and in particular, SUJ3 and SUJ5 containing 0.35 wt% or more of Si and 0.50 wt% or more of Mn are preferable. Can be used.
  • carburized steel SCM415, SCM420, SCr420 etc. can be used, for example.
  • the inner ring 41 and the curved plates 26a and 26b are made of SUJ3.
  • the cylindrical roller 44 of the rolling bearing 40 is made of bearing steel and subjected to carbonitriding treatment, and nitrogen is diffused in these surface layers to stably retain the retained austenite.
  • Specific examples of the bearing steel that can be used as the material of the cylindrical roller 44 are the same as those described above, and thus a duplicate description is omitted.
  • the cylindrical roller 44 is made of SUJ3. Further, by making the heat treatment condition after the carbonitriding treatment of the cylindrical roller 44 different from the heat treatment condition after the carbonitriding treatment of the raceway ring, the ratio of retained austenite in the surface layer portion of the cylindrical roller 44 is slightly lowered (20 to 35%). ).
  • the bearing ring (inner ring 41) is made thinner and the rolling bearing 40 has a diameter compared to the case where a rolling bearing (race ring or rolling element) not having the above-described configuration is employed. It can be downsized in the direction. In this way, through the improvement and miniaturization of the rolling bearing 40, the in-wheel motor drive device 21 that is rich in durability and that is small and light can be realized.
  • the bearing ring by forming the bearing ring with a high carbon chromium bearing steel containing 0.35 wt% or more of Si and 0.50 wt% or more of Mn, the hardenability is improved, so that retained austenite is easily obtained.
  • the material and heat treatment method of the inner ring 41, the curved plates 26a and 26b, and the cylindrical roller 44 constituting the rolling bearing 40 are not limited to the above.
  • the cylindrical roller 44 may be heat-treated under the same conditions as the race.
  • some members of the inner ring 41, the curved plates 26a and 26b, and the cylindrical roller 44 constituting the rolling bearing 40 are made of bearing steel, and the amount of retained austenite in the surface layer portion is set in the above range by carbonitriding. It is good also as a structure.
  • the lubricating mechanism supplies lubricating oil to various parts of the motor part A and the speed reducing part B. As shown in FIGS. 1 and 2, the lubricating oil paths 24a and 24b provided on the motor rotating shaft 24, and the speed reducing part are provided.
  • the white arrow shown in FIG. 1 indicates the direction in which the lubricating oil flows.
  • the lubricating oil passage 24a extends along the axial direction inside the motor rotating shaft 24.
  • a lubricating oil passage 25c extending in the axial direction inside the reduction gear input shaft 25 is connected to the lubricating oil passage 24a.
  • the lubricating oil passage 25d extends radially from the lubricating oil passage 25c toward the outer peripheral surface of the speed reducer input shaft 25, and the outer diameter end of the lubricating oil passage 25d in the illustrated example is the outer peripheral surface of the eccentric portions 25a and 25b. Is open.
  • the lubricating oil passage 25e extends in the axial direction from the end portion on the outboard side of the lubricating oil passage 25c, and opens to the end face on the outboard side of the reduction gear input shaft 25.
  • the formation position of the lubricating oil passage 25d extending in the radial direction is not limited to this, and can be provided at any position in the axial direction of the reduction gear input shaft 25.
  • the lubricating oil discharge port 22b provided in the casing 22 discharges the lubricating oil in the speed reduction part B, and is provided in at least one location of the casing 22 at the position of the speed reduction part B.
  • the lubricating oil discharge port 22b and the lubricating oil path 24a of the motor rotating shaft 24 are connected via a lubricating oil reservoir 22d, a lubricating oil path 22e, and a lubricating oil path 49. Therefore, the lubricating oil discharged from the lubricating oil discharge port 22b returns to the lubricating oil path 24a of the motor rotating shaft 24 through the lubricating oil path 22e, the lubricating oil path 49, and the like.
  • the lubricating oil reservoir 22d has a function of temporarily storing the lubricating oil.
  • the lubricating oil passage 49 is connected to the axial oil passage 49a extending in the axial direction inside the casing 22 and the end portions on the outboard side and the inboard side of the axial oil passage 49a and extends in the radial direction. It is composed of paths 49b and 49c.
  • the rotary pump 51 is provided between the lubricating oil passage 22e and the lubricating oil passage 49 connected to the lubricating oil reservoir 22d. By disposing the rotary pump 51 in the casing 22, it is possible to prevent the in-wheel motor drive device 21 from being enlarged as a whole.
  • the rotary pump 51 includes an inner rotor 52 that rotates using the rotation of the reducer output shaft 28, an outer rotor 53 that rotates following the rotation of the inner rotor 52, both rotors 52, 53 is a cycloid pump including a plurality of pump chambers 54 provided in a space between 53, a suction port 55 communicating with the lubricating oil passage 22e, and a discharge port 56 communicating with the radial oil passage 49b of the lubricating oil passage 49. .
  • the inner rotor 52 rotates around the rotation center c 1
  • the outer rotor 53 rotates around a rotation center c 2 different from the rotation center c 1 of the inner rotor 52. Therefore, the volume of the pump chamber 54 changes continuously.
  • the lubricating oil flowing into the pump chamber 54 from the suction port 55 is pumped from the discharge port 56 to the radial oil passage 49 b of the lubricating oil passage 49.
  • the lubrication mechanism mainly has the above configuration, and lubricates and cools each part of the motor part A and the reduction part B as follows.
  • a part of the lubricating oil flowing through the lubricating oil passage 24 a of the motor rotating shaft 24 is affected by the centrifugal force generated by the rotation of the motor rotating shaft 24 and the pressure of the rotary pump 51. It is discharged from the outer diameter side opening of the lubricating oil passage 24b.
  • This lubricating oil is supplied to the rotor 23b and the stator 23a in the motor part A. Further, a part of the lubricating oil flowing through the lubricating oil passage 49 oozes out from between the casing 22 and the motor rotating shaft 24, and this lubricating oil supports the inboard side end of the motor rotating shaft 24. 36.
  • a part of the lubricating oil discharged from the lubricating oil passage 24 b travels down the inner wall surface on the outboard side of the portion of the casing 22 in which the motor part A is accommodated, and this lubricating oil passes through the motor rotating shaft 24. It is supplied to a rolling bearing 36 that supports the end on the outboard side.
  • the lubricating oil that has flowed into the lubricating oil passage 25c of the reduction gear input shaft 25 via the lubricating oil passage 24a of the motor rotation shaft 24 is subjected to centrifugal force and pressure of the rotary pump 51 accompanying the rotation of the reduction gear input shaft 25.
  • the oil is discharged from the openings of the lubricating oil passages 25d and 25e (see FIG. 2) and is supplied to various places in the speed reduction portion B mainly by centrifugal force.
  • attained the inner wall surface of the casing 22 is discharged
  • the lubricating oil reservoir 22d is provided between the lubricating oil discharge port 22b and the lubricating oil passage 22e connected to the rotary pump 51, it can be completely discharged by the rotary pump 51 especially during high-speed rotation. Even if no lubricating oil is temporarily generated, the lubricating oil can be stored in the lubricating oil storage unit 22d. As a result, it is possible to prevent an increase in heat generation and torque loss at various portions of the deceleration portion B. On the other hand, the amount of lubricating oil reaching the lubricating oil discharge port 22b decreases particularly during low-speed rotation.
  • the lubricating oil stored in the lubricating oil reservoir 22d is used as the lubricating oil. Since it can recirculate
  • the in-wheel motor drive device 21 is attached to the electric vehicle 11 so that the lubricating oil reservoir 22d is positioned below the in-wheel motor drive device 21.
  • the rotor 23b made of a permanent magnet or a magnetic material rotates by receiving an electromagnetic force generated by supplying an alternating current to the coil of the stator 23a. Accordingly, when the speed reducer input shaft 25 connected to the motor rotating shaft 24 rotates, the curved plates 26 a and 26 b revolve around the rotational axis of the speed reducer input shaft 25. At this time, the outer pin 27 engages with the curved waveform provided on the outer periphery of the curved plates 26a and 26b in the circumferential direction, and the curved plates 26a and 26b are opposite to the rotation direction of the speed reducer input shaft 25. Rotate to
  • the inner pin 31 inserted through the through hole 30a comes into contact with the inner wall surface of the through hole 30a as the curved plates 26a and 26b rotate.
  • the revolving motion of the curved plates 26 a and 26 b is not transmitted to the inner pin 31, and only the rotational motion of the curved plates 26 a and 26 b is transmitted to the wheel bearing portion C via the reduction gear output shaft 28.
  • the speed reducer input shaft 25 is decelerated by the speed reducing portion B and then transmitted to the speed reducer output shaft 28, even when the low torque, high speed type motor portion A is employed, the drive wheels ( The required torque can be transmitted to the (rear wheel) 14.
  • the speed reduction ratio of the speed reduction portion B having the above-described configuration is (Z A ⁇ Z B ), where Z A is the number of outer pins 27 and Z B is the number of waveforms (concave portions 34) provided on the outer periphery of the curved plates 26a and 26b. ) / is calculated by Z B.
  • the in-wheel motor drive device 21 having a compact and high reduction ratio can be obtained. Further, by providing rolling bearings (needle roller bearings) 61 and 31a that rotatably support the outer pin 27 and the inner pin 31, friction between the curved plates 26a and 26b and the outer pin 27 and the inner pin 31 is achieved. Since the resistance is reduced, the power transmission efficiency in the speed reduction portion B is also improved from this point.
  • the in-wheel motor drive device 21 of the present embodiment is lightweight and compact as a whole device. Therefore, if the in-wheel motor drive device 21 is mounted on the electric vehicle 11, the unsprung weight can be suppressed, so that the electric vehicle 11 excellent in running stability and NVH characteristics can be realized.
  • the in-wheel motor driving device 21 As described above, the in-wheel motor driving device 21 according to the embodiment of the present invention has been described. However, the in-wheel motor driving device 21 can be variously modified without departing from the gist of the present invention. is there.
  • the inner race surface 42 of the rolling bearing (cylindrical roller bearing) 40 that rotatably holds the curved plates 26 a and 26 b is fixed to the eccentric portions 25 a and 25 b of the speed reducer input shaft 25.
  • the case where it provided in the outer peripheral surface of 41 was shown, it does not restrict to this, For example, you may abbreviate
  • the outer raceway surface 43 of the rolling bearing 40 is directly provided on the inner peripheral surface of the through hole 30b of the curved plates 26a and 26b. May be provided separately, and the outer peripheral surface of the outer ring may be fixed to the inner peripheral surface of the through hole 30b of the curved plates 26a, 26b.
  • the rotary pump 51 was shown as the rotary pump 51, not only this but the rotary pump driven using the rotation of the reduction gear output shaft 28 is employable. . Furthermore, the rotary pump 51 may be omitted, and the lubricating oil may be circulated only by centrifugal force.
  • the motion conversion mechanism is configured by the inner pin 31 fixed to the reduction gear output shaft 28 and the through hole 30a provided in the curved plates 26a and 26b.
  • any configuration capable of transmitting the rotation of the speed reduction portion B to the hub wheel 32 can be employed.
  • it may be a motion conversion mechanism composed of an inner pin fixed to a curved plate and a hole formed in a reduction gear output shaft.
  • a radial gap motor is adopted as the motor unit A
  • the present invention is not limited to this, and a motor having an arbitrary configuration can be applied.
  • an axial gap motor in which a stator and a rotor are opposed to each other via an axial gap may be employed.
  • the electric vehicle 11 shown in FIG. 6 showed the example which used the rear wheel 14 as the driving wheel, it is not restricted to this,
  • the front wheel 13 may be used as a driving wheel and may be a four-wheel driving vehicle.
  • “electric vehicle” is a concept including all vehicles that obtain driving force from electric power, and should be understood as including, for example, a hybrid vehicle.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Retarders (AREA)
  • Rolling Contact Bearings (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Abstract

La présente invention concerne un dispositif d'entraînement de moteur placé dans la roue, comprenant une unité de moteur (A), une unité de décélérateur (B) et une unité de palier de roue (C). L'unité de décélérateur (B) comporte: un arbre d'entrée (25) de décélérateur comportant des éléments excentriques (25a, 25b) et qui est couplé à un arbre rotatif (24) de l'unité de moteur (A) ; un arbre de sortie (28) de décélérateur couplé à l'unité de palier de roue (C); des paliers à roulements (40) prévus sur la périphérie extérieure des parties excentriques (25a, 25b) de l'arbre d'entrée (25) du décélérateur; et des plaques courbes (26a, 26b) qui sont maintenues de manière rotative sur les périphéries externes des parties excentriques (25a, 25b) avec les paliers à roulement (40) situés entre eux, et qui effectuent un mouvement orbital centré autour de l'axe de rotation de l'arbre d'entrée (25) de décélérateur en conjonction avec la rotation de celui-ci. L'entrefer radial initial dans le palier à roulement (40) mesure entre 15 et 60 µm.
PCT/JP2015/074241 2014-09-19 2015-08-27 Dispositif d'entraînement de moteur placé dans la roue WO2016043011A1 (fr)

Applications Claiming Priority (2)

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JP2014191483A JP2016061403A (ja) 2014-09-19 2014-09-19 インホイールモータ駆動装置
JP2014-191483 2014-09-19

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WO2016043011A1 true WO2016043011A1 (fr) 2016-03-24

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109070729A (zh) * 2016-10-17 2018-12-21 Ntn株式会社 轮内电动机驱动装置

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JPH07190072A (ja) * 1993-12-27 1995-07-28 Ntn Corp 転がり軸受の熱処理方法
JPH11101247A (ja) * 1997-09-29 1999-04-13 Ntn Corp 転がり軸受部品
JP2000018256A (ja) * 1998-07-02 2000-01-18 Ntn Corp 車両用差動装置の歯車軸支持装置
JP2000233656A (ja) * 1998-12-18 2000-08-29 Ntn Corp 車両用差動装置の歯車軸支持装置
JP2003056315A (ja) * 2001-08-22 2003-02-26 Ntn Corp ローラ付きカムフォロア
JP2004060015A (ja) * 2002-07-30 2004-02-26 Koyo Seiko Co Ltd 摺動部品およびその製造方法
JP2005214390A (ja) * 2004-02-02 2005-08-11 Nsk Ltd ニードル軸受、遊星歯車機構及びピニオンシャフト
JP2008201353A (ja) * 2007-02-22 2008-09-04 Ntn Corp インホイールモータ駆動装置
JP2010032038A (ja) * 2008-07-02 2010-02-12 Ntn Corp サイクロイド減速機、インホイールモータ駆動装置、および車両用モータ駆動装置
JP2013228031A (ja) * 2012-04-25 2013-11-07 Nsk Ltd 遊星歯車機構
JP2014020394A (ja) * 2012-07-12 2014-02-03 Nsk Ltd プラネタリギヤ装置

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07190072A (ja) * 1993-12-27 1995-07-28 Ntn Corp 転がり軸受の熱処理方法
JPH11101247A (ja) * 1997-09-29 1999-04-13 Ntn Corp 転がり軸受部品
JP2000018256A (ja) * 1998-07-02 2000-01-18 Ntn Corp 車両用差動装置の歯車軸支持装置
JP2000233656A (ja) * 1998-12-18 2000-08-29 Ntn Corp 車両用差動装置の歯車軸支持装置
JP2003056315A (ja) * 2001-08-22 2003-02-26 Ntn Corp ローラ付きカムフォロア
JP2004060015A (ja) * 2002-07-30 2004-02-26 Koyo Seiko Co Ltd 摺動部品およびその製造方法
JP2005214390A (ja) * 2004-02-02 2005-08-11 Nsk Ltd ニードル軸受、遊星歯車機構及びピニオンシャフト
JP2008201353A (ja) * 2007-02-22 2008-09-04 Ntn Corp インホイールモータ駆動装置
JP2010032038A (ja) * 2008-07-02 2010-02-12 Ntn Corp サイクロイド減速機、インホイールモータ駆動装置、および車両用モータ駆動装置
JP2013228031A (ja) * 2012-04-25 2013-11-07 Nsk Ltd 遊星歯車機構
JP2014020394A (ja) * 2012-07-12 2014-02-03 Nsk Ltd プラネタリギヤ装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109070729A (zh) * 2016-10-17 2018-12-21 Ntn株式会社 轮内电动机驱动装置
CN109070729B (zh) * 2016-10-17 2022-08-30 Ntn株式会社 轮内电动机驱动装置

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