WO2012128243A1 - Dispositif d'entraînement de moteur pour véhicule, et automobile - Google Patents

Dispositif d'entraînement de moteur pour véhicule, et automobile Download PDF

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Publication number
WO2012128243A1
WO2012128243A1 PCT/JP2012/056977 JP2012056977W WO2012128243A1 WO 2012128243 A1 WO2012128243 A1 WO 2012128243A1 JP 2012056977 W JP2012056977 W JP 2012056977W WO 2012128243 A1 WO2012128243 A1 WO 2012128243A1
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WO
WIPO (PCT)
Prior art keywords
speed
gear
clutch
clutch gear
friction plate
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2012/056977
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English (en)
Japanese (ja)
Inventor
山本　憲
慶宜 板倉
磯部　史浩
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of WO2012128243A1 publication Critical patent/WO2012128243A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
    • F16D41/066—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical
    • F16D41/067—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical and the members being distributed by a separate cage encircling the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/08—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action
    • F16D41/086—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate members being of circular cross-section and wedging by rolling
    • F16D41/088—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface with provision for altering the freewheeling action the intermediate members being of circular cross-section and wedging by rolling the intermediate members being of only one size and wedging by a movement not having an axial component, between inner and outer races, one of which is cylindrical
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds

Definitions

  • the present invention relates to a vehicle motor drive device that shifts the rotation of an electric motor and transmits it to wheels, and an automobile equipped with the motor drive device.
  • this vehicle motor drive device When this vehicle motor drive device is used, it is possible to use the electric motor in a highly efficient rotational speed and torque region during driving and regeneration by switching the transmission gear ratio according to the running conditions. .
  • the rotational speed of the rotating member of the transmission during high-speed traveling can be reduced, and the power loss of the transmission can be reduced to improve the energy efficiency of the vehicle.
  • Patent Document 1 discloses a vehicle transmission having the following configuration.
  • the 2-speed input gear and 3-speed input gear are rotatably supported by the input shaft through bearings, 2-speed 2-way roller clutch that switches between transmission and cutoff of torque between the 2-speed input gear and the input shaft, and torque transmission and switching between 3-speed input gear and the input shaft 3
  • a vehicle transmission provided with a transmission actuator that selectively engages a high-speed 2-way roller clutch, a 2-speed 2-way roller clutch, and a 3-speed 2-way roller clutch.
  • the 2-speed 2-way roller clutch is incorporated in the cylindrical surface provided on the inner periphery of the 2-speed input gear, the cam surface provided on the outer periphery of the input shaft, and the cam surface and the cylindrical surface.
  • the roller can be rotated relative to the input shaft between an engaging position for holding the roller and engaging the roller between the cam surface and the cylindrical surface and a neutral position for releasing the engagement of the roller.
  • a 2-speed switch spring that elastically holds the 2-speed retainer in the neutral position.
  • the 2-speed retainer is arranged between the engagement position and the neutral position. By moving in the direction, torque transmission and interruption can be switched.
  • the 3-speed 2-way roller clutch has the same configuration as the 2-speed 2-way roller clutch.
  • the speed change actuator includes a two-speed friction plate integrally formed at the end of the two-speed cage so as to face the side surface of the two-speed input gear, and a direction in which the second speed friction plate is separated from the side surface of the two-speed input gear.
  • a two-speed separation spring urging the three-speed friction plate integrally formed at the end of the three-speed cage so as to face the side surface of the three-speed input gear, and the three-speed friction plate on the side surface of the three-speed input gear
  • a third speed separating spring that urges in a direction away from the second speed shift position that presses the second speed friction plate to contact the side surface of the second speed input gear and a side surface of the third speed input gear by pressing the third speed friction plate
  • a shift ring provided so as to be movable in the axial direction between the third-speed shift position and the shift mechanism for moving the shift ring in the axial direction.
  • the transmission then disengages the 2-speed 2-way roller clutch and engages the 3-speed 2-way roller clutch by moving the shift ring in the axial direction from the 2-speed shift position to the 3-speed shift position. Can be combined. This operation will be described below.
  • the 2-speed friction plate is separated from the 2-speed cage, the 2-speed friction plate is prevented from rotating with respect to the 2-speed cage, and the 2-speed input is performed. It is conceivable to change the design so that the second-speed cage is supported so as to be movable in the axial direction between a position where it contacts the side surface of the gear and a position where it separates.
  • the second-speed friction plate can move in the axial direction with respect to the second-speed retainer. Therefore, when the second-speed friction plate is pressed by the shift ring and moves in the axial direction, the second-speed retainer It does not move in the direction, and the attitude of the second speed cage is stabilized.
  • the posture of the second-speed friction plate that is separate from the second-speed cage is likely to be unstable, and when the second-speed friction plate is pressed by the shift ring and contacts the side surface of the second-speed input gear. The contact timing may become unstable.
  • the problem to be solved by the present invention is to improve the reliability of the operation of the vehicle motor drive device using the 2-way roller clutch.
  • an electric motor an input shaft to which rotation of the electric motor is input, an output shaft disposed in parallel to the input shaft at an interval, A first input gear and a second input gear provided on the input shaft; a first output gear and a second output gear provided on the output shaft and meshing with the first input gear and the second input gear, respectively; A differential gear that distributes rotation of the output shaft to left and right wheels; One of the set of the first input gear, the second input gear, and the input shaft, the set of the first output gear, the second output gear, and the output shaft, and the first clutch gear, the second clutch gear, and the like.
  • a clutch gear support shaft that rotatably supports the clutch gear via a bearing, Transmission of torque between the first clutch gear and the clutch gear support shaft; and transmission of torque between the second clutch gear and the clutch gear support shaft.
  • a second two-way roller clutch that performs switching of shut-off, and a transmission actuator that selectively engages the first two-way roller clutch and the second two-way roller clutch,
  • the first two-way roller clutch includes a cylindrical surface provided on one of the inner periphery of the first clutch gear and the outer periphery of the clutch gear support shaft, a cam surface provided on the other, the cam surface, and the cylinder.
  • a roller incorporated between the surfaces, and the clutch gear between an engagement position for holding the roller and engaging the roller between the cam surface and the cylindrical surface and a neutral position for releasing the engagement of the roller.
  • a first retainer provided to be rotatable relative to the support shaft, and a first switch spring that elastically retains the first retainer in the neutral position;
  • the second two-way roller clutch includes a cylindrical surface provided on one of the inner periphery of the second clutch gear and the outer periphery of the clutch gear support shaft, a cam surface provided on the other, the cam surface, and the cylinder.
  • a roller incorporated between the surfaces, and the clutch gear between an engagement position for holding the roller and engaging the roller between the cam surface and the cylindrical surface and a neutral position for releasing the engagement of the roller.
  • a second retainer provided so as to be rotatable relative to the support shaft, and a second switch spring for elastically retaining the second retainer in the neutral position
  • the speed change actuator is provided so as to be axially movable with respect to the first retainer between a position where it is prevented from rotating with respect to the first retainer and is in contact with a side surface of the first clutch gear and a position where it is separated from the first retainer.
  • the first friction plate, the first separation spring for urging the first friction plate in the direction away from the side surface of the first clutch gear, and the second retainer, and the second retainer.
  • a second friction plate provided so as to be movable in the axial direction with respect to the second retainer between a position contacting the side surface of the clutch gear and a position separating the clutch gear; and the second friction plate is connected to the second clutch gear.
  • a second separation spring that urges in a direction away from the side surface, a first shift position that presses the first friction plate to contact the side surface of the first clutch gear, and presses the second friction plate to 2nd shift contacted with side surface of second clutch gear Consists of a shift ring which is movable axially between a position, a shift mechanism for moving the shift ring in the axial direction,
  • the first friction plate is formed to protrude in the axial direction from the flange portion toward the shift ring from the flange portion disposed to face the side surface of the first clutch gear, and in the circumferential direction in the shift ring And a guide boss that fits slidably on the
  • the second friction plate is formed to protrude in the axial direction from the flange
  • the first friction plate when the shift ring is in the first shift position, the first friction plate is pressed by the shift ring and comes into contact with the side surface of the first clutch gear. Since the first friction plate rotates relative to the clutch gear support shaft by the frictional force, the first cage that is prevented from rotating by the first friction plate moves from the neutral position to the engagement position, and the first two-way roller The clutch is engaged.
  • the vehicle motor drive device disengages the first two-way roller clutch by moving the shift ring in the axial direction from the first shift position to the second shift position, and thereby the second two-way roller.
  • the clutch can be engaged. This operation will be described below.
  • the second friction plate When the shift ring reaches the second shift position, the second friction plate is pressed by the shift ring and comes into contact with the side surface of the second clutch gear, so that the second friction plate is brought into contact with the clutch gear support shaft by the frictional force between the contact surfaces.
  • the second cage which rotates relative to the second friction plate and is prevented from rotating by the second friction plate, moves from the neutral position to the engaged position, and the second two-way roller clutch is engaged by the movement of the second cage. It becomes a state.
  • a first separation spring that accommodates the first separation spring on the opposite side of the guide boss portion of the first friction plate so that the flange portion of the first friction plate and the first separation spring overlap each other in the direction perpendicular to the axis.
  • a second separating spring is provided so that a spring accommodating recess is provided, and the flange portion of the second friction plate and the second separating spring are arranged in the direction perpendicular to the axis on the opposite side of the guide boss portion of the second friction plate. It is preferable to provide a second separating spring accommodating recess that accommodates.
  • the axial length around the first friction plate is shortened by the amount of the first separation spring entering the first separation spring accommodation recess compared to the case where there is no first separation spring accommodation recess,
  • the axial length around the second friction plate is also shortened by the amount that the second separation spring enters the second separation spring accommodating recess. Therefore, the axial length of the entire apparatus can be shortened to make it compact.
  • the shift mechanism includes a shift sleeve that rotatably supports the shift ring via a rolling bearing, a bifurcated shift fork that engages with an annular groove provided on the outer periphery of the shift sleeve, and the shift fork.
  • the thing of the structure which has the shift motor driven to an axial direction is employable.
  • an axially compressible preload spring is incorporated in the axial clearance on both sides between the shift fork and the annular groove.
  • the spring force of the preload spring is adjusted by adjusting the axial relative position of the shift fork with respect to the shift sleeve.
  • the frictional force between the contact surfaces of the first friction plate and the first clutch gear can be adjusted. . Therefore, it becomes possible to adjust the engagement timing of the two-way roller clutch of the next shift stage with high accuracy.
  • the first retainer has a cylindrical portion in which a plurality of pockets for accommodating the rollers are formed at intervals in the circumferential direction, and an inward flange portion that extends radially inward from one end of the cylindrical portion.
  • a first cage guide for supporting the radially inner end of the inward flange portion of the first cage so as to be slidable in the circumferential direction.
  • a surface can be formed.
  • the second cage includes a cylindrical portion in which a plurality of pockets for accommodating the rollers are formed at intervals in the circumferential direction, and an inward flange portion that extends radially inward from one end of the cylindrical portion.
  • a second inner end that supports the radially inner end of the inward flange portion of the second retainer is slidable in the circumferential direction.
  • a cage guide surface can be formed.
  • an oil supply passage that passes through the inside of the clutch gear support shaft is provided, and an oil outlet of the oil supply passage is connected to the first cage guide surface and the second cage. It is preferable to open each of the guide surfaces.
  • the first cage guide surface When opening the oil outlet of the oil supply passage to the first cage guide surface and the second cage guide surface, respectively, the first cage guide surface is connected to the roller of the first 2-way roller clutch and the first clutch gear. It is preferable that the second retainer guide surface is disposed between the supporting bearing and the second retainer guide surface between the roller of the second two-way roller clutch and the bearing supporting the second clutch gear. If it does in this way, the roller of the 1st 2 way roller clutch and the bearing which supports the 1st clutch gear will be lubricated simultaneously with the lubricating oil which flows out from the oil outlet of the oil supply passage opened to the 1st maintenance machine guide surface. be able to. Further, the lubricant of the second two-way roller clutch and the bearing supporting the second clutch gear can be simultaneously lubricated with the lubricating oil flowing out from the oil outlet of the oil supply passage that opens to the second cage guide surface. .
  • the first switch spring employs a C-shaped annular portion obtained by winding a steel wire in a C-shape and a pair of extending portions extending radially outward from both ends of the C-shaped annular portion,
  • the cam surface of the first two-way roller clutch is formed as an annular first cam member that is prevented from rotating around the outer periphery of the clutch gear support shaft, and the first switch is formed on the axial end surface of the first cam member.
  • a circular switch spring housing recess into which a C-shaped annular portion of the spring fits, and a radial groove into which a pair of extending portions of the first switch spring are inserted in a radial direction, and the first cage A notch into which a protruding portion from the radial groove of the pair of extending portions of the first switch spring is inserted can be provided.
  • the first switch spring extends to the axial end surface of the first cam member.
  • an annular first washer that covers the radial groove is provided on the axial end surface of the first cam member, and the first separation spring is connected to the first cam through the first washer. It is preferable that the cam member is supported on the end surface in the axial direction.
  • the first separation spring is supported over the entire circumference via the first washer, the distribution of the spring force of the first separation spring becomes uniform in the circumferential direction, and as a result, the first friction plate is the first friction plate.
  • the frictional force between the contact surfaces when contacting the side surface of the clutch gear is also uniform in the circumferential direction, and the engagement timing of the two-way roller clutch at the next shift stage is stabilized.
  • the second switch spring includes a C-shaped annular portion in which a steel wire is wound in a C shape, and a pair of extending portions extending radially outward from both ends of the C-shaped annular portion.
  • the cam surface of the second two-way roller clutch is formed on an annular second cam member that is prevented from rotating around the outer periphery of the clutch gear support shaft, and the axial end surface of the second cam member has the A circular switch spring housing recess into which a C-shaped annular portion of the second switch spring fits, and a radial groove into which a pair of extending portions of the second switch spring are inserted in a radial direction; Even when the two cages are provided with notches into which the protruding portions from the radial grooves of the pair of extending portions of the second switch spring are inserted, the radial direction is provided on the axial end surface of the second cam member.
  • An annular second washer is provided to cover the groove, and the second washer Preferably the second separating spring to be supported by the axial end surface of said second cam member.
  • the second separation spring is supported over the entire circumference via the second washer, the distribution of the spring force of the second separation spring becomes uniform in the circumferential direction, and as a result, the second friction plate becomes the second friction plate.
  • the frictional force between the contact surfaces when contacting the side surface of the clutch gear is also uniform in the circumferential direction, and the engagement timing of the two-way roller clutch at the next shift stage is stabilized.
  • the cam surface of the first cam member and the cam surface of the second cam member have the same number and the same phase, and the rotation prevention of the first cam member and the second cam member with respect to the clutch gear support shaft is performed by spline fitting. It can be. If it does in this way, a cam surface can be processed with high precision on the basis of a spline.
  • the first clutch gear is preferably formed such that the meshing tooth width thereof overlaps with the bearing supporting the first clutch gear in the direction perpendicular to the axis. In this way, when the first clutch gear idles with the first two-way roller clutch disengaged, a moment load that tilts the bearing acts on the bearing that supports the first clutch gear. It is possible to suppress the power loss of the bearing. The same applies to the second clutch gear.
  • At least one of a pair of left and right front wheels and a pair of left and right rear wheels is driven by the vehicle motor drive device. I will provide a.
  • one of the pair of left and right front wheels and the pair of left and right rear wheels is driven by the engine, and the other is driven by the vehicle motor drive device.
  • a hybrid vehicle designed to be provided is provided.
  • the first friction plate is pressed by the shift ring and brought into contact with the side surface of the first clutch gear. Sometimes, the first friction plate contacts the side surface of the first clutch gear in a stable posture. The same applies to the second friction plate. Therefore, it is possible to engage the two-way roller clutch of the next shift stage with stable timing.
  • FIG. 3 is an enlarged sectional view of the vicinity of the first-speed output gear and the second-speed output gear.
  • Sectional view along line VV in FIG. Sectional view along line VI-VI in FIG.
  • Sectional view along line VII-VII in FIG. Sectional drawing which shows the shift mechanism which moves the shift ring of FIG. 4 to an axial direction
  • FIG. 4 is an enlarged sectional view in the vicinity of the shift ring.
  • wearing with the vehicle motor drive device shown in FIG. 4 is an exploded perspective view of the 2-speed cam member, 2-speed switch spring, 2-speed washer, and 2-speed release spring shown in FIG.
  • FIG. 1 shows an electric vehicle EV in which a pair of left and right front wheels 1 are drive wheels driven by a vehicle motor drive device A according to the present invention, and a pair of left and right rear wheels 2 are driven wheels.
  • FIG. 2 shows a hybrid vehicle HV in which a pair of left and right front wheels 1 are main drive wheels driven by an engine E, and a pair of left and right rear wheels 2 are auxiliary drive wheels driven by a vehicle motor drive device A according to the present invention. Indicates.
  • the hybrid vehicle HV is provided with a transmission T that shifts the rotation of the engine E and a differential gear D that distributes the rotation output from the transmission T to the left and right front wheels 1.
  • a vehicle motor drive device A according to the present invention incorporated in the electric vehicle EV and the hybrid vehicle HV will be described below.
  • the vehicle motor drive device A includes an electric motor 3, a transmission 4 that shifts and outputs the rotation of the rotation shaft 3 a of the electric motor 3, and the rotation output from the transmission 4. It consists of a differential gear 5 distributed to a pair of left and right front wheels 1 of the electric vehicle EV shown in FIG. 1 or distributed to a pair of left and right rear wheels 2 of a hybrid vehicle shown in FIG.
  • the transmission 4 includes an input shaft 6 to which the rotation of the rotating shaft 3 a of the electric motor 3 is input, an output shaft 7 that is disposed in parallel to the input shaft 6 at an interval, A first speed input gear 8A and a second speed input gear 8B provided on the input shaft 6 and a first speed output gear 9A and a second speed output gear 9B provided on the output shaft 7 are provided.
  • the input shaft 6 is rotatably supported by a pair of opposed bearings 11 incorporated in the housing 10, and one end of the input shaft 6 is connected to the rotating shaft 3 a of the electric motor 3.
  • the output shaft 7 is also rotatably supported by a pair of opposed bearings 12 incorporated in the housing 10.
  • the first-speed input gear 8A and the second-speed input gear 8B are arranged at an interval in the axial direction, and are fixed to the input shaft 6 so as to rotate integrally with the input shaft 6 around the input shaft 6.
  • the first-speed output gear 9A and the second-speed output gear 9B are also arranged at intervals in the axial direction.
  • the first-speed output gear 9 ⁇ / b> A is formed in an annular shape that penetrates the output shaft 7, and is supported by the output shaft 7 through a bearing 14 ⁇ / b> A. And can be rotated.
  • the second-speed output gear 9B is also rotatably supported by the output shaft 7 via the bearing 14B.
  • the first speed input gear 8A and the first speed output gear 9A mesh with each other, and rotation is transmitted between the first speed input gear 8A and the first speed output gear 9A.
  • the second-speed input gear 8B and the second-speed output gear 9B are also engaged, and rotation is transmitted between the second-speed input gear 8B and the second-speed output gear 9B by the engagement.
  • the reduction ratio between the second speed input gear 8B and the second speed output gear 9B is smaller than the reduction ratio between the first speed input gear 8A and the first speed output gear 9A.
  • the first-speed output gear 9A is formed so that the tooth width meshed with the first-speed input gear 8A overlaps with the bearing 14A supporting the first-speed output gear 9A in the direction perpendicular to the axis.
  • the second-speed output gear 9B is formed so that the tooth width meshed with the second-speed input gear 8B overlaps the bearing 14B supporting the second-speed output gear 9B in the direction perpendicular to the axis.
  • a first-speed two-way roller clutch 15A for switching between torque transmission and interruption between the first-speed output gear 9A and the output shaft 7 is incorporated.
  • a second speed two-way roller clutch 15B for switching between transmission of torque and switching between the second speed output gear 9B and the output shaft 7 is incorporated.
  • the second-speed two-way roller clutch 15B Since the first-speed two-way roller clutch 15A and the second-speed two-way roller clutch 15B have the same configuration, the second-speed two-way roller clutch 15B will be described below.
  • the parts corresponding to the 2-speed 2-way roller clutch 15B are denoted by the same reference numerals or the reference numerals in which the alphabet B at the end is replaced with A, and the description thereof is omitted.
  • the two-speed two-way roller clutch 15B includes a cylindrical surface 16 provided on the inner periphery of the second-speed output gear 9B and an annular second gear that is prevented from rotating on the outer periphery of the output shaft 7. It comprises a cam surface 18 formed on the cam member 17B, a roller 19 incorporated between the cam surface 18 and the cylindrical surface 16, a 2-speed retainer 20B for holding the roller 19, and a 2-speed switch spring 21B.
  • the cam surface 18 is a surface that forms a wedge-shaped space that gradually narrows from the center in the circumferential direction toward both ends in the circumferential direction with the cylindrical surface 16.
  • the cam surface 18 faces the cylindrical surface 16 as shown in the figure. It is a flat surface.
  • the two-speed cage 20B includes a cylindrical portion 23 in which a plurality of pockets 22 for accommodating the rollers 19 are formed at intervals in the circumferential direction, and radially inward from one end of the cylindrical portion 23. And an inward flange portion 24 that extends.
  • the radially inner end of the inward flange portion 24 is supported so as to be slidable in the circumferential direction by a cylindrical second-speed cage guide surface 25B formed on the outer periphery of the second-speed cam member 17B.
  • the 2-speed retainer 20B can rotate relative to the output shaft 7 between an engagement position where the roller 19 is engaged between the cam surface 18 and the cylindrical surface 16 and a neutral position where the engagement of the roller 19 is released. It has become. Further, the second-speed cage 20B is restricted from moving in the axial direction of the inward flange portion 24 and is not movable in the axial direction.
  • an oil supply passage 26 for introducing lubricating oil from an oil pump (not shown) is provided in the output shaft 7.
  • the oil outlet of the oil supply passage 26 opens to the second-speed cage guide surface 25B.
  • the second-speed cage guide surface 25B is disposed between the roller 19 of the second-speed two-way roller clutch 15B and the bearing 14B that supports the second-speed output gear 9B.
  • the roller 19 and the bearing 14B are lubricated simultaneously by the lubricating oil that flows out.
  • the two-speed switch spring 21 ⁇ / b> B includes a C-shaped annular portion 27 in which a steel wire is wound in a C shape, and a pair extending radially outward from both ends of the C-shaped annular portion 27. Extending portions 28, 28.
  • the C-shaped annular portion 27 is fitted into a circular switch spring accommodating recess 29 formed on the axial end surface of the second speed cam member 17B, and the pair of extending portions 28 and 28 are axial end surfaces of the second speed cam member 17B. It is inserted in the radial groove 30 formed in.
  • the radial groove 30 is formed so as to extend radially outward from the inner peripheral edge of the switch spring accommodating recess 29 and reach the outer periphery of the second speed cam member 17B.
  • the extension portion 28 of the second speed switch spring 21B protrudes from the radially outer end of the radial groove 30, and the protruding portion of the extension portion 28 from the radial groove 30 is the cylindrical portion of the second speed retainer 20B.
  • 23 is inserted into a notch 31 formed at the end of the axial direction.
  • the radial groove 30 and the notch 31 are formed to have the same width.
  • the extending portion 28 is in contact with the inner surface facing in the circumferential direction of the radial groove 30 and the inner surface facing in the circumferential direction of the notch 31, and the circumference acting on the contact surface.
  • the second-speed cage 20B is elastically held in the neutral position by the force in the direction.
  • the first-speed cam member 17A and the second-speed cam member 17B are prevented from rotating with respect to the output shaft 7 by spline fitting.
  • the cam surface 18 of the first speed cam member 17A and the cam surface 18 of the second speed cam member 17B have the same number and the same phase.
  • the cam surface 18 of the first speed cam member 17A and the cam surface 18 of the second speed cam member 17B are processed so as to have the same phase with reference to the inner peripheral splines of the cam members 17A and 17B.
  • the first speed cam member 17 ⁇ / b> A and the second speed cam member 17 ⁇ / b> B are non-movable in the axial direction by a locking nut 32 fitted to the outer periphery of the output shaft 7.
  • a spacer 33 is incorporated between the first speed cam member 17A and the second speed cam member 17B.
  • the first-speed two-way roller clutch 15A and the second-speed two-way roller clutch 15B can be selectively engaged by the transmission actuator 34.
  • the speed change actuator 34 includes a shift ring 35 movably provided in the axial direction between the first speed output gear 9A and the second speed output gear 9B, and the first speed output gear 9A and the shift ring 35.
  • a first-speed friction plate 36A incorporated in between, and a second-speed friction plate 36B incorporated between the second-speed output gear 9B and the shift ring 35 are provided.
  • the second speed friction plate 36B includes a flange portion 37 disposed to face the side surface of the second speed output gear 9B, and a guide boss portion 38 formed to project from the flange portion 37 toward the shift ring 35 in the axial direction.
  • the guide boss portion 38 is formed so as to have a cylindrical outer periphery, and is fitted in the shift ring 35 so as to be slidable in the circumferential direction.
  • the second-speed friction plate 36B is provided with an arc-shaped opening 39 that engages with the end of the cylindrical portion 23 of the second-speed cage 20B.
  • the arc-shaped opening 39 and the end of the cylindrical portion 23 are provided.
  • the second-speed friction plate 36B is prevented from rotating by the second-speed retainer 20B.
  • the opening 39 accommodates the end of the cylindrical portion 23 of the second-speed cage 20B so as to be slidable in the axial direction, and the second-speed friction plate 36B is prevented from rotating by the second-speed cage 20B by this sliding. In the state, it can move in the axial direction with respect to the second-speed retainer 20B between a position contacting the side surface of the second-speed output gear 9B and a position separating from the position. Further, the end portion of the cylindrical portion 23 of the second-speed cage 20B is positioned in the radial direction by slidingly contacting the peripheral edge of the arc-shaped opening 39 of the second-speed friction plate 36B.
  • a second speed separation spring 40B is incorporated in a state compressed in the axial direction, and the second speed friction plate is generated by the elastic restoring force of the second speed separation spring 40B.
  • 36B is biased in a direction away from the side surface of the second-speed output gear 9B.
  • the second speed separating spring 40B is a coil spring wound along the outer periphery of the spacer 33, and one end thereof is supported by the end face in the axial direction of the second speed cam member 17B via the second speed washer 41B.
  • the second speed washer 41B is formed in an annular shape so as to cover the radial groove 30 on the axial end surface of the second speed cam member 17B (see FIG. 11).
  • the second-speed separation spring 40B is accommodated in an annular two-speed separation spring accommodating recess 42B formed on the opposite side of the guide boss portion 38 of the second-speed friction plate 36B.
  • the flange portion 37 of the plate 36B and the second speed separation spring 40B are arranged so as to overlap in the direction perpendicular to the axis.
  • the shift ring 35 presses the first speed friction plate 36A to contact the side surface of the first speed output gear 9A, and the shift ring 35 presses the second speed friction plate 36B to contact the side surface of the second speed output gear 9B. It is supported so as to be movable in the axial direction between the speed shift position.
  • a shift mechanism 43 that moves the shift ring 35 in the axial direction between the first-speed shift position and the second-speed shift position is provided.
  • the shift mechanism 43 is related to a shift sleeve 45 that rotatably supports the shift ring 35 via a rolling bearing 44, and an annular groove 46 provided on the outer periphery of the shift sleeve 45.
  • the shift rod 48 is arranged parallel to the output shaft 7 at a distance and is supported by a pair of sliding bearings 51 incorporated in the housing 10 so as to be slidable in the axial direction.
  • the rolling bearing 44 incorporated between the shift ring 35 and the shift sleeve 45 is assembled so as to be immovable in the axial direction with respect to both the shift ring 35 and the shift sleeve 45.
  • the rotation of the shift motor 49 is converted into a linear motion by the motion conversion mechanism 50 and transmitted to the shift fork 47, and the linear motion of the shift fork 47 is transmitted to the shift ring 35 via the rolling bearing 44.
  • the shift ring 35 is moved in the axial direction.
  • a preload spring 52 that is compressible in the axial direction is incorporated in the axial clearance between both sides of the shift fork 47 and the annular groove 46.
  • a differential drive gear 53 that transmits the rotation of the output shaft 7 to the differential gear 5 is fixed to the output shaft 7.
  • the differential gear 5 includes a differential case 55 rotatably supported by a pair of bearings 54, a ring gear 56 that is fixed to the differential case 55 coaxially with the rotational center of the differential case 55, and meshes with the differential drive gear 53, and the rotational center of the differential case 55.
  • the pinion shaft 57 is fixed to the differential case 55 in a direction perpendicular to the pinion shaft 57, a pair of pinions 58 rotatably supported by the pinion shaft 57, and a pair of left and right side gears 59 that mesh with the pair of pinions 58.
  • the left side gear 59 is connected to the shaft end portion of the axle 60 connected to the left wheel
  • the right side gear 59 is connected to the shaft end portion of the axle 60 connected to the right wheel.
  • the first speed holding is performed. Is held in the neutral position by the spring force of the first speed switch spring 21A, and the second speed retainer 20B is also held in the neutral position by the spring force of the second speed switch spring 21B. 19 is disengaged, and the 2-speed 2-way roller clutch 15B is also disengaged from the roller 19.
  • the first-speed friction plate 36A comes into contact with the side surface of the first-speed output gear 9A, and the contact is made. Since the first speed friction plate 36A rotates relative to the output shaft 7 by the frictional force between the surfaces, the first speed retainer 20A, which is prevented from rotating by the first speed friction plate 36A, moves from the neutral position to the engagement position. The roller 19 held by the speed holder 20A is pushed into the narrow portion of the wedge-shaped space between the cylindrical surface 16 and the cam surface 18, and the first speed two-way roller clutch 15A is engaged.
  • the vehicle motor drive device A can engage the two-way roller clutch 15A (or 15B) of the next shift stage at a stable timing.
  • the vehicle motor drive device A has an arrangement in which the flange portion 37 of the second speed friction plate 36B and the second speed separation spring 40B overlap each other on the opposite side of the guide boss portion 38 of the second speed friction plate 36B. Since the second-speed separation spring accommodating recess 42B for accommodating the two-speed separation spring 40B is provided, the second-speed separation spring 40B is compared with the case where the second-speed separation spring accommodation recess 42B is not provided. The axial length around the second-speed friction plate 36B is short as much as it enters 42B. Similarly, the axial length around the first-speed friction plate 36A is also short because the first-speed separation spring 40A enters the first-speed separation spring accommodating recess 42A. For this reason, the axial length of the entire apparatus is short and compact.
  • this vehicle motor drive device A incorporates preload springs 52 that are compressible in the axial direction in the axial clearances on both sides between the shift fork 47 and the annular groove 46, the shift ring 35 causes the first speed friction.
  • the spring force of the preload spring 52 is adjusted by adjusting the relative position of the shift fork 47 in the axial direction with respect to the shift sleeve 45, and the first-speed friction It is possible to adjust the frictional force between the contact surfaces of the plate 36A and the first-speed output gear 9A.
  • the second-speed separating spring 40B can be directly supported by the axial end surface of the second-speed cam member 17B without using the second-speed washer 41B shown in FIG. Since there is a radial groove 30 into which the extension portions 28 and 28 of the two-speed switch spring 21B are inserted in the axial end surface of the member 17B, the second-speed separation spring 40B is not supported at the position of the radial groove 30. The distribution of the spring force of the second-speed separation spring 40B becomes non-uniform in the circumferential direction. As a result, the frictional force between the contact surfaces when the second-speed friction plate 36B contacts the side surface of the second-speed output gear 9B is also not uniform in the circumferential direction. There is a possibility that the engagement timing of the two-way roller clutch 15A (or 15B) at the next shift stage becomes unstable.
  • the vehicle motor drive device A is provided with the 2-speed washer 41B on the axial end surface of the 2-speed cam member 17B, the 2-speed separation spring 40B is supported over the entire circumference via the 2-speed washer 41B.
  • the distribution of the spring force of the second speed separating spring 40B is uniform in the circumferential direction, and as a result, the friction force between the contact surfaces when the second speed friction plate 36B contacts the side surface of the second speed output gear 9B is also uniform in the circumferential direction. It becomes.
  • the first-speed washer 41A provided on the axial end surface of the first-speed cam member 17A. For this reason, the engagement timing of the two-way roller clutch 15A (or 15B) at the next shift stage becomes stable.
  • this vehicle motor drive device A is arranged so that the portion of the first-speed output gear 9A that actually meshes with the first-speed input gear 8A overlaps the bearing 14A in the direction perpendicular to the shaft, the first-speed two-way roller clutch 15A is engaged.
  • the first-speed output gear 9A idles in the released state, a moment load that tilts the bearing 14A is difficult to act, and the power loss of the bearing 14A is low.
  • the portion of the second speed output gear 9B that actually meshes with the second speed input gear 8B overlaps the bearing 14B in the direction perpendicular to the axis, the power loss of the bearing 14B that supports the second speed output gear 9B is low.
  • the second-speed cage 20B is supported at both ends in the axial direction. That is, the inward flange portion 24 at one end of the second-speed retainer 20B is supported by the second-speed retainer guide surface 25B, and the other end of the second-speed retainer 20B is the peripheral edge of the arc-shaped opening 39 of the second-speed friction plate 36B. It is supported by. Therefore, when the second-speed cage 20B moves in the circumferential direction between the neutral position and the engagement position, the second-speed cage 20B moves smoothly without being twisted. The same applies to the first-speed cage 20A.
  • each component (first speed output gear 9A, second speed output gear 9B, etc.) on the output shaft 7 is assembled to the output shaft 7 in advance.
  • the output shaft unit 61 is formed, shipping and transporting are performed in the state of the output shaft unit 61, and the output shaft unit 61 is assembled to the housing 10 in the final process, the assembly workability is improved.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Structure Of Transmissions (AREA)

Abstract

Afin d'augmenter la fiabilité du fonctionnement d'un dispositif d'entraînement de moteur de véhicule à l'aide d'une roue libre à rouleaux bidirectionnelle, l'invention concerne un dispositif d'entraînement de moteur de véhicule ayant une structure qui est pourvue : d'une roue libre à rouleaux bidirectionnelle de pignon de première vitesse (15A), disposée entre un engrenage de sortie de pignon de première vitesse (9A) et un arbre de sortie (7) ; d'une roue libre à rouleaux bidirectionnelle de pignon de deuxième vitesse (15B), disposé entre un engrenage de sortie de pignon de deuxième vitesse (9B) et l'arbre de sortie (7) ; d'une plaque de frottement de pignon de première vitesse (36A), qui est disposée de manière à pouvoir se déplacer dans la direction axiale entre une position qui vient en contact avec l'engrenage de sortie de pignon de première vitesse (9A) et une position qui est séparée de celui-ci ; d'une plaque de frottement de pignon de deuxième vitesse (36B), qui est disposée de manière à pouvoir se déplacer dans la direction axiale entre une position qui vient en contact avec l'engrenage de sortie de pignon de deuxième vitesse (9B) et une position qui est séparée de celui-ci. Ainsi, la plaque de frottement de pignon de première vitesse (36A) comporte une section de bride (37) qui est dirigée vers la surface latérale de l'engrenage de sortie de pignon de première vitesse (9A), une section de bossage de guidage (38) qui se verrouille avec l'intérieur d'une bague de changement de vitesse (35) ; la plaque de frottement de pignon de deuxième vitesse (36B) comporte également une section de bride (37) qui fait face à la surface latérale de l'engrenage externe de pignon de deuxième vitesse (9B), et une section de bossage de guidage (38) qui se verrouille avec l'intérieur de la bague de changement de vitesse (35).
PCT/JP2012/056977 2011-03-23 2012-03-19 Dispositif d'entraînement de moteur pour véhicule, et automobile Ceased WO2012128243A1 (fr)

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JP2011063868A JP2012197912A (ja) 2011-03-23 2011-03-23 車両用モータ駆動装置および自動車
JP2011-063868 2011-03-23

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Cited By (2)

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CN111577788A (zh) * 2020-05-07 2020-08-25 深圳市兆威机电股份有限公司 离合组件和控制箱
CN115990951A (zh) * 2023-02-17 2023-04-21 成都尖端高新技术产业有限公司 集成房屋构件切割机刀片移动转位装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112572129B (zh) * 2019-09-27 2025-05-06 株式会社爱信 车辆用驱动装置
CN110701301B (zh) * 2019-11-12 2024-07-09 玉环县东方汽车制动器厂 双向自动变速装置的倒车传动机构
CN112343981A (zh) * 2020-09-17 2021-02-09 燕山大学 一种纯电动汽车无动力中断两挡变速器

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JPH0419462A (ja) * 1990-05-11 1992-01-23 Honda Motor Co Ltd 電子制御変速機
JP2000274450A (ja) * 1999-03-24 2000-10-03 Ntn Corp 動力断続装置
JP2004211834A (ja) * 2003-01-07 2004-07-29 Jatco Ltd 多段変速機及びその変速制御装置
JP2005233343A (ja) * 2004-02-20 2005-09-02 Ntn Corp 回転伝達装置
JP2005299708A (ja) * 2004-04-06 2005-10-27 Jatco Ltd 平行軸変速装置
JP2008045601A (ja) * 2006-08-11 2008-02-28 Hitachi Ltd 動力伝達装置
JP2008202687A (ja) * 2007-02-20 2008-09-04 Ntn Corp 回転伝達装置

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Publication number Priority date Publication date Assignee Title
JPH0419462A (ja) * 1990-05-11 1992-01-23 Honda Motor Co Ltd 電子制御変速機
JP2000274450A (ja) * 1999-03-24 2000-10-03 Ntn Corp 動力断続装置
JP2004211834A (ja) * 2003-01-07 2004-07-29 Jatco Ltd 多段変速機及びその変速制御装置
JP2005233343A (ja) * 2004-02-20 2005-09-02 Ntn Corp 回転伝達装置
JP2005299708A (ja) * 2004-04-06 2005-10-27 Jatco Ltd 平行軸変速装置
JP2008045601A (ja) * 2006-08-11 2008-02-28 Hitachi Ltd 動力伝達装置
JP2008202687A (ja) * 2007-02-20 2008-09-04 Ntn Corp 回転伝達装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111577788A (zh) * 2020-05-07 2020-08-25 深圳市兆威机电股份有限公司 离合组件和控制箱
CN115990951A (zh) * 2023-02-17 2023-04-21 成都尖端高新技术产业有限公司 集成房屋构件切割机刀片移动转位装置

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