WO2022215449A1 - 差動装置 - Google Patents

差動装置 Download PDF

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Publication number
WO2022215449A1
WO2022215449A1 PCT/JP2022/011343 JP2022011343W WO2022215449A1 WO 2022215449 A1 WO2022215449 A1 WO 2022215449A1 JP 2022011343 W JP2022011343 W JP 2022011343W WO 2022215449 A1 WO2022215449 A1 WO 2022215449A1
Authority
WO
WIPO (PCT)
Prior art keywords
input member
case member
input
clutch
case
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/JP2022/011343
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
明弘 山本
英司 井上
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.)
NSK Ltd
Original Assignee
NSK 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 NSK Ltd filed Critical NSK Ltd
Priority to US18/027,276 priority Critical patent/US11852228B2/en
Priority to EP22784434.7A priority patent/EP4321773A4/en
Priority to CN202280025979.0A priority patent/CN117157477A/zh
Priority to KR1020237033984A priority patent/KR102873965B1/ko
Priority to JP2022560888A priority patent/JP7211572B1/ja
Publication of WO2022215449A1 publication Critical patent/WO2022215449A1/ja
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
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/24—Arrangements for suppressing or influencing the differential action, e.g. locking devices using positive clutches or brakes
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/26—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of freewheel device
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/348—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed
    • B60K17/35—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches
    • B60K17/3505—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches with self-actuated means, e.g. by difference of speed
    • 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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/12—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members
    • 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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0483—Axle or inter-axle differentials
    • 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H2048/202—Arrangements for suppressing or influencing the differential action, e.g. locking devices using freewheel clutches
    • 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
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H2048/385—Constructional details of the ring or crown gear
    • 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

Definitions

  • the present invention relates to a differential for distributing the power of a drive source to a pair of drive wheels.
  • the torque of a drive source such as an engine or a drive motor is transmitted to a differential gear via a speed reduction mechanism including a transmission or a power transmission mechanism such as a propeller shaft. , distributed to a pair of drive wheels.
  • the automotive drive system described above has room for improvement in terms of improving fuel efficiency or electricity efficiency. That is, if the accelerator is turned off while the vehicle equipped with the automotive drive device is running, and the vehicle tries to coast, loss occurs at the meshing portion of the speed reduction mechanism, the drive source, etc., and the running distance due to coasting is shortened. It may get lost.
  • Japanese Patent Application Laid-Open No. 2020-46065 describes a differential device including a clutch device between a differential case and a side gear. According to such a differential, by disengaging the clutch device and disconnecting the drive wheels from the power transmission mechanism during inertia, the traveling distance during inertia can be increased. As a result, it is possible to improve the fuel consumption performance or the electricity consumption performance of the vehicle.
  • the clutch device when the clutch device is to be engaged in a state in which the relative rotational speed between the differential case and the side gear is higher than a predetermined speed, the protrusions forming one of the engagement unevenness portions will be displaced from the other engagement unevenness portion. is repelled by the convex portion forming the , and the engagement with the concave portion of the other engaging concave-convex portion is hindered.
  • An object of the present invention is to provide a differential that can easily switch whether or not to transmit torque between the drive wheels and the power transmission mechanism.
  • a differential device includes an input member, a case member, a one-way clutch, at least one pinion gear, and a pair of side gears.
  • the input member has a torque input portion.
  • the torque input section can be configured by a ring gear that meshes with a gear, a pulley for running a belt, or a sprocket for running a chain.
  • the case member is arranged coaxially with the input member and rotatable relative to the input member.
  • the one-way clutch is arranged between the input member and the case member, and only when the input member tends to rotate relative to the case member in the normal rotation direction, the one-way clutch engages the input member and the case member. transmit torque between The forward rotation direction refers to the rotation direction of the input member with respect to the case member when torque is transmitted from the drive source to the drive wheels in order to move the vehicle forward.
  • the one-way clutch can be configured by a roller clutch, a cam clutch, a sprag clutch, a ratchet type clutch, or the like.
  • the pinion gear is supported by the case member so as to be rotatable about an axis perpendicular to the central axis of the case member.
  • the pair of side gears are supported coaxially with the central axis of the input member so as to be rotatable relative to the input member and the case member, and mesh with the pinion gear.
  • a differential device is arranged between the input member and the case member, and switches a connection/disconnection state (torque transmission availability) between the input member and the case member.
  • a clutch device may further be provided.
  • the clutch device has an actuator and switches the connection/disengagement state based on the operation of the actuator.
  • the clutch device may have a first clutch member and a second clutch member.
  • the first clutch member has, on the first side surface facing the axial direction, first engaging uneven portions formed by alternately arranging concave portions and convex portions in the circumferential direction, and the input member and the It is supported by one member of the case member so as to be axially displaceable based on the operation of the actuator.
  • the second clutch member has, on a second side surface axially opposite to the first side surface, a second engagement concave/convex portion formed by alternately arranging concave portions and convex portions in a circumferential direction, and Either the input member or the case member is integrally formed with the other member, or supported and fixed to the other member.
  • the clutch device includes an electric motor having an output shaft, and a linear motion mechanism that converts rotation of the output shaft into axial motion of the first clutch member. can be done.
  • the linear motion mechanism can be composed of, for example, a slide screw type or ball type feed screw mechanism, or a cam device.
  • the one-way clutch has an outer diameter side engaging surface provided directly or via another member on the inner peripheral surface of the input member, and an outer peripheral surface provided directly or via another member on the outer peripheral surface of the case member. It can have an inner diameter side engaging surface and an engaging element arranged between the outer diameter side engaging surface and the inner diameter side engaging surface.
  • the case member can be rotatably supported radially inward of the input member, and the input member supplies lubricant to the one-way clutch.
  • the end portion of the oil hole on the side closer to the one-way clutch can be opened radially inward from the inner diameter engaging surface.
  • differential device According to the differential device according to one aspect of the present invention, it is possible to easily switch whether or not to transmit torque between the drive wheels and the power transmission mechanism.
  • FIG. 1 is a schematic diagram showing an electric vehicle drive system incorporating a differential gear of a first embodiment of the invention.
  • FIG. 2 is a cross-sectional view showing the differential gear of the first example.
  • 3(A) is an enlarged view of the X section in FIG. 2 showing a state in which the clutch device is connected
  • FIG. 3(B) is an enlarged view of the X section in FIG. 2 showing a state in which the clutch device is disconnected.
  • FIG. 4 is a diagram for showing a torque transmission path during non-inerturing in the forward direction.
  • FIG. 5 is a diagram showing a torque transmission path when the vehicle is traveling backward.
  • FIG. 6 is an enlarged cross-sectional view of a main part of an electric vehicle drive system incorporating a differential gear of a second embodiment of the invention.
  • FIG. 7 is a perspective view showing the second element for the second example.
  • FIG. 1 shows an electric vehicle driving device 2 incorporating a differential device 1 of this embodiment.
  • the electric vehicle drive device 2 increases the output torque of the drive motor 3 by the power transmission mechanism 4 , transmits it to the differential device 1 , and distributes it to a pair of drive shafts 5 by the differential device 1 .
  • the drive wheels 6 supported by the leading ends of the pair of drive shafts 5 via suspensions (not shown) are rotationally driven.
  • the power transmission mechanism 4 is composed of a gear-type speed reducer.
  • the power transmission mechanism 4 includes a drive gear 4a, an intermediate shaft 4b, an intermediate gear 4c, and a final gear 4d.
  • the drive gear 4 a is supported and fixed to the output shaft 3 a of the drive motor 3 .
  • the intermediate shaft 4b is parallel to the output shaft 3a of the drive motor 3 and rotatably supported on a vehicle body (not shown).
  • the intermediate gear 4c has more teeth than the driving gear 4a, and is supported and fixed to the intermediate shaft 4b.
  • the final gear 4d has fewer teeth than the intermediate gear 4c, and is supported and fixed to the intermediate shaft 4b.
  • the power transmission mechanism 4 is an automatic transmission (AT), a belt type or toroidal type continuously variable transmission (CVT), an automated manual transmission (AMT), a dual clutch transmission (DCT), or a manual transmission (MT). It is also possible to provide a transmission such as a transmission and a propeller shaft.
  • the power transmission mechanism 4 is replaced with a gear-type speed reducer, or in addition to a gear-type speed reducer, for example, a belt-type or chain-type power transmission mechanism and/or a friction roller speed reducer. Can also be configured.
  • the differential device 1 of this example includes a housing 7, an input member 8, a case member 9, a one-way clutch 10, a pinion gear 11, a pair of side gears 12, and a clutch device 13.
  • the axial direction, the circumferential direction, and the radial direction refer to the axial direction, the circumferential direction, and the radial direction of the input member 8 unless otherwise specified.
  • the axial direction, circumferential direction, and radial direction of the input member 8 coincide with the axial direction, circumferential direction, and radial direction of the case member 9, and the axial direction, circumferential direction, and radial direction of the pair of side gears 12. match.
  • One side in the axial direction means the right side in FIGS. 2 to 5, and the other side in the axial direction means the left side in FIGS.
  • the housing 7 is supported and fixed to the vehicle body and does not rotate during use.
  • the input member 8 has a ring gear 14 that constitutes a torque input portion.
  • a ring gear 14 is provided on the outer peripheral surface of the input member 8 and meshes with the final gear 4 d of the power transmission mechanism 4 .
  • the input member 8 has a stepped cylindrical shape, and is arranged in order from one side in the axial direction: a small-diameter tubular portion 15a, a connecting portion 16a, a large-diameter tubular portion 17, a connecting portion 16b, and a small-diameter tubular portion. and a portion 15b.
  • the small-diameter tubular portion 15a on one side in the axial direction has a cylindrical shape, and has an input-side engaging uneven portion 18 in which concave portions and convex portions are alternately arranged in the circumferential direction on the end face on one side in the axial direction.
  • the connecting portion 16a on one axial side has a substantially conical cylindrical shape inclined in a direction in which the inner diameter and outer diameter increase from one axial side to the other side, and the axial direction of the small-diameter cylindrical portion 15a on one axial side.
  • the end on the other side and the end on one side in the axial direction of the large-diameter cylindrical portion 17 are connected. That is, one end in the axial direction of the connecting portion 16 a is connected to the other end in the axial direction of the small-diameter cylindrical portion 15 a , and the other end in the axial direction of the connecting portion 16 a is connected to the large-diameter cylindrical portion 17 . is connected to one end in the axial direction of the
  • the large-diameter cylindrical portion 17 has a cylindrical shape.
  • a ring gear 14 is provided on the outer peripheral surface of the large-diameter cylindrical portion 17 .
  • the ring gear 14 is composed of a helical gear.
  • the ring gear 14 can also be composed of spur gears or bevel gears.
  • the torque input portion to which the torque from the power transmission mechanism 4 is input may be configured by a pulley for running a belt or a sprocket for running a chain.
  • the connecting portion 16b on the other axial side has a substantially hollow circular plate shape, and is connected to the other axial end of the large-diameter tubular portion 17 and one axial end of the small-diameter tubular portion 15b on the other axial side. connect with the That is, the radially outer end of the connecting portion 16b is connected to the other axial end of the large-diameter cylindrical portion 17, and the radially inner end of the connecting portion 16b is connected to the small-diameter cylindrical portion 15b. It is connected to one end in the axial direction.
  • the small-diameter cylindrical portion 15b on the other side in the axial direction has a cylindrical shape.
  • the input member 8 is rotatably supported with respect to the housing 7 by a pair of tapered roller bearings 19a and 19b provided with a face-to-face (DF) contact angle.
  • the tapered roller bearing 19a on one axial side is arranged between the outer peripheral surface of the small-diameter tubular portion 15a on one axial side and the inner peripheral surface of the housing 7, and the small-diameter tubular portion on the other axial side is arranged.
  • the input member 8 is rotatably supported inside the housing 7 by arranging a tapered roller bearing 19b on the other side in the axial direction between the outer peripheral surface of 15b and the inner peripheral surface of the housing 7 .
  • the input member 8 includes a first element 20 having a small-diameter cylindrical portion 15a on one axial side, a connecting portion 16a on one axial side, and a large-diameter cylindrical portion 17, a connecting portion 16b on the other axial side, and a A second element 21 having a small-diameter cylindrical portion 15 b on the other side is coupled and fixed with a bolt 22 . That is, bolts 22 inserted through through holes provided at a plurality of locations in the circumferential direction of the connection portion 16b of the second element 21 are screwed into screw holes that open to the other axial side surface of the large-diameter cylindrical portion 17 of the first element 20.
  • the input member 8 is configured by joining the first element 20 and the second element 21 together.
  • the case member 9 is arranged coaxially with the input member 8 and rotatable relative to the input member 8 . That is, the central axis O8 of the input member 8 and the central axis O9 of the case member 9 coincide with each other.
  • the case member 9 is configured in a stepped cylindrical shape, and is supported radially inward of the input member 8 so as to be rotatable relative to the input member 8 .
  • the case member 9 includes, in order from one side in the axial direction, a small-diameter tubular portion 23a, a connecting portion 24a, a large-diameter tubular portion 25 constituting the case tubular portion, a connecting portion 24b, and a small-diameter tubular portion 23b.
  • the small-diameter cylindrical portion 23a on one side in the axial direction has a cylindrical shape, and has a male spline portion 26 on the outer peripheral surface of the one side portion in the axial direction.
  • the connecting portion 24a on one side in the axial direction has a substantially hollow circular plate shape, and is connected to the other end portion in the axial direction of the small-diameter cylindrical portion 23a on one side in the axial direction and the one-side end portion in the axial direction of the large-diameter cylindrical portion 25. to connect. That is, the radially inner end of the connecting portion 24a is connected to the other axial end of the small-diameter cylindrical portion 23a, and the radially outer end of the connecting portion 24a is connected to the large-diameter cylindrical portion 25. It is connected to one end in the axial direction.
  • the large-diameter cylindrical portion 25 has a substantially cylindrical shape, and has a circular hole 27 that opens to the inner peripheral surface at at least one position in the circumferential direction.
  • the circular holes 27 are provided at two locations on the opposite sides in the diameter direction of the large-diameter tubular portion 25 .
  • a base end portion of a support shaft 28 for supporting the pinion gear 11 is fitted and fixed in each circular hole 27 .
  • the large-diameter tubular portion 25 has opening windows at at least one position in the circumferential direction, for example, two positions on the opposite side in the radial direction.
  • the connecting portion 24b on the other axial side has a substantially hollow circular plate shape, and is connected to the other axial end of the large-diameter tubular portion 25 and one axial end of the small-diameter tubular portion 23b on the other axial side. connect with the That is, the radially outer end of the connecting portion 24b is connected to the other axial end of the large-diameter cylindrical portion 25, and the radially inner end of the connecting portion 24b is connected to the small-diameter cylindrical portion 23b. It is connected to one end in the axial direction.
  • the small-diameter cylindrical portion 23b on the other side in the axial direction has a cylindrical shape.
  • the case member 9 is rotatably supported radially inward of the input member 8 by a plurality of rolling bearings 29a, 29b, 29c, and 29d.
  • the differential gear 1 of this example includes four rolling bearings 29 a, 29 b, 29 c, and 29 d that rotatably support the case member 9 with respect to the input member 8 .
  • a rolling bearing 29a which is a radial needle bearing, is arranged between the inner peripheral surface of the small-diameter cylindrical portion 15a of the input member 8 and the outer peripheral surface of the small-diameter cylindrical portion 23a of the case member 9, and the input member
  • a rolling bearing 29b which is a radial needle bearing, is arranged between the inner peripheral surface of the small diameter tubular portion 15b of the case member 9 and the outer peripheral surface of the small diameter tubular portion 23b of the case member 9.
  • a rolling bearing 29c which is a thrust needle bearing, is arranged between the other axial side surface of the connecting portion 16a of the input member 8 and one axial side surface of the connecting portion 24a of the case member 9.
  • a rolling bearing 29d which is a thrust needle bearing, is arranged between one axial side surface of the connecting portion 16b and the other axial side surface of the connecting portion 24b of the case member 9. As shown in FIG. Thereby, the case member 9 is rotatably supported inside the input member 8 .
  • the one-way clutch 10 is arranged between the input member 8 and the case member 9.
  • the one-way clutch 10 transmits torque from the input member 8 to the case member 9 only when the input member 8 attempts to rotate relative to the case member 9 in the normal direction.
  • the forward rotation direction refers to the relative rotation direction of the input member 8 with respect to the case member 9 when torque is transmitted from the drive motor 3 to the drive wheels 6 in order to move the vehicle forward.
  • the one-way clutch 10 is arranged between the large-diameter tubular portion 17 of the input member 8 and the large-diameter tubular portion 25 of the case member 9 .
  • the one-way clutch 10 includes an inner race 30, a plurality of sprags 31 each corresponding to an engaging element, a retainer 32, and an urging spring 33.
  • the inner race 30 is externally fitted and fixed to the large-diameter tubular portion 25 of the case member 9 .
  • the sprag 31 is a cylinder between an outer diameter side engaging surface 64 provided on the inner peripheral surface of the large diameter cylindrical portion 17 of the input member 8 and an inner diameter side engaging surface 65 provided on the outer peripheral surface of the inner race 30 . are arranged in a state of being held by retainers 32 at a plurality of locations in the circumferential direction of the shaped space.
  • the urging spring 33 urges each sprag 31 in a direction in which each sprag 31 meshes with the outer diameter side engaging surface 64 and the inner diameter side engaging surface 65 .
  • the one-way clutch 10 when the input member 8 attempts to rotate relative to the case member 9 in the normal direction, the sprags 31 swing in a predetermined direction, causing the outer diameter side engaging surface 64 and the inner diameter side engaging surface 65 to swing. bite against. As a result, the one-way clutch 10 is switched to the locked state, and torque transmission from the input member 8 to the case member 9 becomes possible. That is, the case member 9 rotates integrally with the input member 8 .
  • the pinion gear 11 is supported on the case member 9 so as to be rotatable about an axis perpendicular to the central axis O9 of the case member 9 .
  • two pinion gears 11 are provided, and each pinion gear 11 is configured by a bevel gear. That is, the pinion gear 11 has a substantially truncated cone shape and has a plurality of teeth 34 on the outer peripheral surface. Furthermore, the pinion gear 11 has a central hole 35 that penetrates the pinion gear 11 in the axial direction.
  • the pinion gear 11 is rotatably supported around the tip of a support shaft 28 fitted and fixed to the large-diameter cylindrical portion 25 of the case member 9 via a radial needle bearing 36 .
  • a pair of side gears 12 are supported coaxially with the central axis O 8 of the input member 8 so as to be rotatable relative to the input member 8 and the case member 9 , and mesh with the pinion gear 11 .
  • the side gears 12 forming the pair of side gears 12 are configured by bevel gears. That is, the side gear 12 has a substantially truncated cone shape, and has a plurality of teeth 37 meshing with the teeth 34 of the pinion gear 11 on its outer peripheral surface. Further, the side gear 12 has a spline hole 38 extending axially through the center.
  • the side gear 12 is arranged inside the large-diameter tubular portion 25 of the case member 9 and is coupled and fixed to the base end portion of the drive shaft 5 so as to transmit torque. That is, the spline shaft portion provided at the base end portion of the drive shaft 5 is spline-engaged with the spline hole 38 .
  • the clutch device 13 is arranged between the input member 8 and the case member 9 .
  • the clutch device 13 has an actuator 39 , and the connection/disconnection state is switched based on the operation of the actuator 39 .
  • the clutch device 13 includes an actuator 39 , a sleeve 40 , a pressing member 41 and an elastic member 42 .
  • the actuator 39 includes an electric motor 43 and a feed screw mechanism 44 that is a direct acting mechanism.
  • the electric motor 43 has an output shaft 45 , a rotor 46 and a stator 47 .
  • the output shaft 45 has a hollow cylindrical shape and is rotatably supported by a pair of rolling bearings 48 a and 48 b with respect to the housing 7 coaxially with the central axis O 8 of the input member 8 .
  • the drive shaft 5 on one side in the axial direction is inserted through the radially inner side of the output shaft 45 .
  • the output shaft 45 is supported around the drive shaft 5 on one side in the axial direction so as to be coaxial with the drive shaft 5 and rotatable relative to the drive shaft 5 .
  • the output shaft 45 has an outward flange portion 49 protruding radially outward at the other end portion in the axial direction, and has a male thread portion 50 on the outer peripheral surface of the outward flange portion 49 .
  • the rotor 46 is externally fitted and fixed around the intermediate portion of the output shaft 45 in the axial direction so as to rotate integrally with the output shaft 45 .
  • the stator 47 is arranged coaxially around the rotor 46 and supported inside the housing 7 .
  • the feed screw mechanism 44 is configured by screwing a female threaded portion 52 provided on the inner peripheral surface of a nut 51 into a male threaded portion 50 of the output shaft 45 .
  • a male spline portion 53 provided on the outer peripheral surface of the nut 51 is spline-engaged with a female spline portion 54 provided on the inner peripheral surface of the housing 7 , so that the nut 51 is supported so as to be displaceable only in the axial direction with respect to the housing 7 . ing. That is, when the electric motor 43 is energized and the output shaft 45 is driven to rotate, the rotation of the output shaft 45 is caused by the screw engagement between the male threaded portion 50 of the output shaft 45 and the female threaded portion 52 of the nut 51. converted to axial motion.
  • the nut 51 has an inward flange 55 protruding radially inward at the other end in the axial direction.
  • the sleeve 40 has, on the end face on the other side in the axial direction, case-side engaging uneven portions 56 in which concave portions and convex portions are alternately arranged in the circumferential direction, and is supported by the case member 9 so as to be displaceable in the axial direction. ing.
  • the sleeve 40 includes a cylindrical portion 58 having a female spline portion 57 on its inner peripheral surface, and an outward flange portion 59 projecting radially outward from the other axial end of the cylindrical portion 58 . and a retaining ring 60 engaged with the outer peripheral surface of one end of the cylindrical portion 58 in the axial direction.
  • the case-side engaging concave-convex portion 56 is provided on the radially outer portion of the end face on the other axial side of the cylindrical portion 58 and on the other axial side surface of the outward flange portion 59 .
  • the sleeve 40 spline-engages the female spline portion 57 provided on the inner peripheral surface of the tubular portion 58 with the male spline portion 26 provided on the outer peripheral surface of the small-diameter tubular portion 23a of the case member 9, thereby forming a case. It is supported with respect to the member 9 so that it can only be displaced in the axial direction.
  • the retaining ring 60 abuts the radially outer portion of the other axial side surface against one axial side surface of the inward flange portion 55 of the nut 51 .
  • the pressing member 41 has an inward flange 61 protruding radially inward at one end in the axial direction. It hits one side in the direction.
  • the elastic member 42 is sandwiched between the nut 51 and the pressing member 41 in an elastically compressed state.
  • the elastic member 42 can be composed of, for example, a torsion coil spring, a leaf spring, or the like.
  • the clutch device 13 switches between a state in which torque is transmitted between the input member 8 and the case member 9 and a state in which torque is not transmitted based on the energization of the electric motor 43 that constitutes the actuator 39 .
  • the sleeve 40 constitutes the first clutch member, and the end surface of the sleeve 40 on the other side in the axial direction constitutes the first side surface. 56 constitutes a first engaging uneven portion.
  • the input member 8 constitutes a second clutch member, and the end surface of the small-diameter cylindrical portion 15a provided on the input member 8 constitutes a second side surface on one side in the axial direction.
  • the input-side engaging uneven portion 18 constitutes a second engaging uneven portion.
  • the first clutch member is supported so as to be axially displaceable with respect to the input member based on the operation of the actuator, and the second clutch member is integrally formed with the case member. Alternatively, it can be supported and fixed to the case member.
  • the elastic member 42 elastically biases the pressing member 41 toward the other side in the axial direction. can be engaged. That is, when the sleeve 40 is pressed toward the other side in the axial direction based on the energization of the electric motor 43 in order to connect the clutch device 13, the tip surface of the convex portion constituting the case-side engaging concave-convex portion 56 and the The tip end surface of the convex portion forming the input-side engaging concave-convex portion 18 may come into contact. From this state, when the sleeve 40 is further pressed toward the other side in the axial direction, the elastic member 42 is elastically compressed between the nut 51 and the pressing member 41 .
  • the differential device 1 of this embodiment switches the connection/disengagement state of the clutch device 13 based on the energization of the electric motor 43, and the one-way clutch 10 based on the relative rotation direction between the input member 8 and the case member 9. By switching the connection/disconnection state, the power transmission path is switched.
  • the torque output from the drive motor 3 is increased by the power transmission mechanism 4 and then transmitted to the input member 8 .
  • the one-way clutch 10 is switched to the locked state, and the input member 8 and the case member 9 rotate together.
  • the two pinion gears 11 rotate, i.e., revolve around the central axis O9 of the case member 9. Further, based on the meshing of the teeth 34 of the pinion gear 11 and the teeth 37 of the side gear 12, a pair of pinion gears 11 rotates.
  • side gear 12 rotates around its own central axis arranged coaxially with the central axis O8 of the input member 8 .
  • the pair of drive shafts 5 coupled and fixed to the pair of side gears 12 are rotationally driven, and the pair of drive wheels 6 are rotationally driven in the direction of advancing the vehicle.
  • the torque output from the drive motor 3 is increased by the power transmission mechanism 4 and then transmitted to the input member 8 .
  • Rotation of the input member 8 is transmitted to the case member 9 via the clutch device 13 . That is, it is transmitted to the sleeve 40 via the engagement portion between the input-side engaging uneven portion 18 and the case-side engaging uneven portion 56 , and further to the female spline portion 57 of the sleeve 40 and the male spline portion 26 of the case member 9 . is transmitted to the case member 9 via the spline engaging portion of the . As a result, the input member 8 and the case member 9 rotate together.
  • the pair of drive wheels 6 can be disconnected from the power transmission mechanism 4 and the drive motor 3 during coasting in the forward direction. Therefore, it is possible to lengthen the distance traveled by inertia travel. In other words, it is possible to slow down the speed reduction during inertia running. As a result, it is possible to improve the power consumption performance of an electric vehicle equipped with the differential gear 1 .
  • the one-way clutch 10 is arranged between the input member 8 having the ring gear 14 to which torque is input from the final gear 4d and the case member 9 supporting the pinion gear 11.
  • the differential case 62 is configured by combining the input member 8 having the ring gear 14 and the case member 9 supporting the pinion gear 11 via the one-way clutch 10 .
  • the one-way clutch 10 is switched between the disengagement and connection states based on the relative rotation direction between the input member 8 and the case member 9 when the vehicle is traveling forward.
  • the drive motor 3 outputs a torque in the direction to move the vehicle forward, and the input member 8 is about to rotate relative to the case member 9 in the normal direction.
  • the one-way clutch 10 is engaged, the one-way clutch 10 is switched to the locked state, and torque from the drive motor 3 is transmitted to the pair of drive wheels 6 via the power transmission mechanism 4 and the differential gear 1 .
  • the accelerator is turned off and torque input from the drive motor 3 to the input member 8 ceases and the input member 8 rotates in the reverse direction relative to the case member 9, the one-way clutch 10 switches to the overrun state. , the torque from the pair of drive wheels 6 is no longer transmitted to the power transmission mechanism 4 and the drive motor 3 .
  • the relative rotation direction of the input member 8 with respect to the case member 9 is switched according to changes in the input torque from the drive motor 3 .
  • the connection/disengagement state of the one-way clutch 10 is switched according to a change in the direction of relative rotation of the input member 8 with respect to the case member 9 , thereby connecting the pair of drive wheels 6 with the power transmission mechanism 4 and the drive motor 3 .
  • the propriety of torque transmission between them is switched. Therefore, it is not necessary to strictly adjust the timing of engaging the clutch device, unlike the differential device described in Japanese Patent Application Laid-Open No. 2020-46065. In short, it is possible to easily switch between the pair of drive wheels 6, the power transmission mechanism 4, and the drive motor 3 to enable or disable torque transmission.
  • the differential gear 1 of this example has a clutch device 13 arranged between the input member 8 and the case member 9 .
  • the clutch device 13 is switched between the disengagement and connection states based on the operation of the actuator 39 , specifically, the energization of the electric motor 43 in this example. That is, when the clutch device 13 is connected, torque can be transmitted between the pair of drive wheels 6, the power transmission mechanism 4, and the drive motor 3 regardless of the direction of relative rotation of the input member 8 with respect to the case member 9. becomes. Therefore, by connecting the clutch device 13 , the torque output from the drive motor 3 and transmitted to the input member 8 via the power transmission mechanism 4 in the direction to move the vehicle backward is transmitted via the differential device 1 to the input member 8 . It can be transmitted to a pair of drive wheels 6 .
  • the clutch device 13 is basically disengaged when the shift lever is switched to the forward travel range. However, when decelerating the vehicle while traveling forward, the torque from the case member 9 can be transmitted to the input member 8 by connecting the clutch device 13 . The torque transmitted to the input member 8 is transmitted to the output shaft 3 a of the drive motor 3 via the power transmission mechanism 4 . When the output shaft 3a rotates, the drive motor 3 functions as a generator and regenerative braking is performed.
  • the outer diameter side engaging surface 64 that engages with the sprag 31 is directly provided on the inner peripheral surface of the large diameter cylindrical portion 17 of the input member 8.
  • the outer diameter side engaging surface 64 is provided directly.
  • the engagement surface can also be provided on the inner peripheral surface of the input member via another member.
  • the inner diameter side engaging surface 65 that engages with the sprag 31 is provided on the outer peripheral surface of the large diameter cylindrical portion 25 of the case member 9 via the inner race 30, but in the case of carrying out the present invention, , the inner diameter side engaging surface may be provided on the outer peripheral surface of the case member via another member.
  • the one-way clutch 10 is configured by a sprag clutch having a plurality of sprags 31, but when implementing the present invention, the one-way clutch may be configured by a roller clutch, a ratchet type clutch, or the like. can.
  • the linear motion mechanism for converting the rotation of the output shaft 45 of the electric motor 43 into axial motion is composed of the sliding feed screw mechanism 44.
  • the linear motion mechanism can also be configured by a ball screw type feed screw mechanism, a cam device, or the like.
  • the actuator 39 for switching the connection/disengagement state of the clutch device 13 is configured by an electric actuator having the electric motor 43. It can also be configured by an actuator of formula.
  • the differential gear of the present invention is not limited to a drive device for an electric vehicle (EV) using a drive motor as a drive source, but may be a drive device for a fossil fuel vehicle using an engine as a drive source, or a drive motor and an engine as drive sources. It can also be applied to a driving device of a hybrid vehicle (HV).
  • EV electric vehicle
  • HV hybrid vehicle
  • FIGSecond example 6 and 7 show a second example of an embodiment of the invention.
  • an oil hole 63 for supplying lubricant to the one-way clutch 10 is provided in the input member 8a.
  • the oil hole 63 is provided so as to axially penetrate one or more locations in the circumferential direction of the connecting portion 16b on the other axial side corresponding to the side plate portion.
  • the oil holes 63 are provided at eight equally spaced locations in the connecting portion 16b in the circumferential direction.
  • the end portion of the oil hole 63 on the side closer to the one-way clutch 10 is located further than the inner diameter side engaging surface 65 provided on the outer peripheral surface of the large-diameter tubular portion 25 of the case member 9 . It is open radially inward.
  • the entire opening of the oil hole 63 on the other side in the axial direction need not be located radially inward of the inner diameter engaging surface 65, and at least part of the opening on the other side in the axial direction of the oil hole 63, That is, the radially inner end portion of the opening on the other side in the axial direction may be positioned radially inwardly of the inner diameter engaging surface 65 .
  • the differential gear 1a of this embodiment a sufficient amount of oil is supplied to the one-way clutch 10 arranged between the large-diameter tubular portion 17 of the input member 8a and the large-diameter tubular portion 25 of the case member 9 through the oil hole 63. Lubricating oil can be supplied. Therefore, the one-way clutch 10 can be kept well lubricated for a long period of time, and the durability of the differential gear 1a can be sufficiently ensured.
  • Reference Signs List 1 1a differential gear 2 electric vehicle drive device 3 drive motor 3a output shaft 4 power transmission mechanism 4a drive gear 4b intermediate shaft 4c intermediate gear 4d final gear 5 drive shaft 6 drive wheel 7 housing 8, 8a input member 9 case member REFERENCE SIGNS LIST 10 one-way clutch 11 pinion gear 12 side gear 13 clutch device 14 ring gear 15a, 15b small-diameter tubular portion 16a, 16b connection portion 17 large-diameter tubular portion 18 input-side engaging uneven portion 19a, 19b tapered roller bearing 20 first element 21 second element 22 Bolts 23a, 23b Small-diameter tubular portions 24a, 24b Connection portion 25 Large-diameter tubular portion 26 Male spline portion 27 Circular hole 28 Support shafts 29a, 29b, 29c, 29d Rolling bearing 30 Inner race 31 Sprag 32 Cage 33 Biasing spring 34 Teeth 35 Center hole 36 Radial needle bearing 37 Teeth 38 Spline hole 39 Actuator 40 Sleeve 41 Pressing member 42 Elastic member 43 Electric motor 44 Feed

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)
  • Mechanical Operated Clutches (AREA)
  • General Details Of Gearings (AREA)
PCT/JP2022/011343 2021-04-05 2022-03-14 差動装置 Ceased WO2022215449A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US18/027,276 US11852228B2 (en) 2021-04-05 2022-03-14 Differential device
EP22784434.7A EP4321773A4 (en) 2021-04-05 2022-03-14 DIFFERENTIAL DEVICE
CN202280025979.0A CN117157477A (zh) 2021-04-05 2022-03-14 差动装置
KR1020237033984A KR102873965B1 (ko) 2021-04-05 2022-03-14 차동 장치
JP2022560888A JP7211572B1 (ja) 2021-04-05 2022-03-14 差動装置

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JP2021-064315 2021-04-05
JP2021064315 2021-04-05

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EP (1) EP4321773A4 (https=)
JP (1) JP7211572B1 (https=)
KR (1) KR102873965B1 (https=)
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US11892065B2 (en) * 2021-08-17 2024-02-06 Means Industries, Inc. Drivetrain component
US12103381B1 (en) * 2023-07-10 2024-10-01 Ford Global Technologies, Llc Differential with disconnect

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JP2020046065A (ja) 2018-09-14 2020-03-26 Ｇｋｎドライブラインジャパン株式会社 デファレンシャル装置

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JPH1178587A (ja) * 1997-09-11 1999-03-23 Tochigi Fuji Ind Co Ltd 四輪駆動車における切換同期方法およびその装置
JP2005059791A (ja) * 2003-08-19 2005-03-10 Tochigi Fuji Ind Co Ltd 減速駆動装置
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JP5002142B2 (ja) * 2005-09-20 2012-08-15 Ｇｋｎドライブラインジャパン株式会社 減速駆動装置
JP5612435B2 (ja) * 2009-11-25 2014-10-22 Ｎｓｋワーナー株式会社 差動制御式２方向クラッチ
JP6699313B2 (ja) * 2016-04-14 2020-05-27 株式会社ジェイテクト 駆動力伝達装置及び四輪駆動車
JP6780332B2 (ja) * 2016-07-11 2020-11-04 株式会社ジェイテクト 差動装置
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CN112189100B (zh) * 2018-05-07 2022-09-13 日本精工株式会社 逆向输入断开离合器以及促动器

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JP2001287550A (ja) * 2000-04-07 2001-10-16 Tochigi Fuji Ind Co Ltd 動力伝達装置及びその操作方法
JP2020046065A (ja) 2018-09-14 2020-03-26 Ｇｋｎドライブラインジャパン株式会社 デファレンシャル装置

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See also references of EP4321773A4

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CN117157477A (zh) 2023-12-01
KR20230154247A (ko) 2023-11-07
JPWO2022215449A1 (https=) 2022-10-13
EP4321773A4 (en) 2025-04-09
EP4321773A1 (en) 2024-02-14
US20230272846A1 (en) 2023-08-31
KR102873965B1 (ko) 2025-10-20
US11852228B2 (en) 2023-12-26
JP7211572B1 (ja) 2023-01-24

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