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WO2020261669A1 - Dispositif d'entraînement de véhicule - Google Patents

Dispositif d'entraînement de véhicule Download PDF

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Publication number
WO2020261669A1
WO2020261669A1 PCT/JP2020/011425 JP2020011425W WO2020261669A1 WO 2020261669 A1 WO2020261669 A1 WO 2020261669A1 JP 2020011425 W JP2020011425 W JP 2020011425W WO 2020261669 A1 WO2020261669 A1 WO 2020261669A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
electric machine
rotary electric
axial direction
rotor
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/JP2020/011425
Other languages
English (en)
Japanese (ja)
Inventor
伊藤達也
前田拓洋
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.)
Aisin AW Co Ltd
Original Assignee
Aisin AW 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 Aisin AW Co Ltd filed Critical Aisin AW Co Ltd
Publication of WO2020261669A1 publication Critical patent/WO2020261669A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/44—Series-parallel type
    • B60K6/445—Differential gearing distribution type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L15/00—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles
    • B60L15/20—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles for control of the vehicle or its driving motor to achieve a desired performance, e.g. speed, torque, programmed variation of speed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L50/00—Electric propulsion with power supplied within the vehicle
    • B60L50/10—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines
    • B60L50/16—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with provision for separate direct mechanical propulsion
    • 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
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/72—Electric energy management in electromobility

Definitions

  • the first rotary electric machine and the second rotary electric machine an input member that is driven and connected to the internal combustion engine, a pair of output members that are driven and connected to the wheels, and a driving force of the internal combustion engine that is transmitted to the input member.
  • the present invention relates to a vehicle drive device including a distribution differential gear mechanism for distributing the input rotation and an output differential gear mechanism for distributing the input rotation to a pair of output members.
  • Patent Document 1 An example of such a vehicle drive device is disclosed in Patent Document 1 below.
  • the reference numerals in Patent Document 1 are quoted in parentheses.
  • the distribution differential gear mechanism (22) is driven and connected to the rotor of the first rotary electric machine (MG1) with the first rotary element (S1) and the input member (
  • the second rotating element (CA1) driven and connected to 20) is driven and connected to the second rotating electric machine (MG2) via the speed reducer (24), and the output difference is driven via the counter gear mechanism (36).
  • the first rotary electric machine (MG1), the second rotary electric machine (MG2), the differential gear mechanism for distribution (22), and the reduction gear (24) are arranged coaxially with the input member (20).
  • the output differential gear mechanism (40) and the pair of output members (38) are arranged on a shaft different from the input member (20).
  • the first rotary electric machine (MG1) is arranged coaxially with the input member (20). Therefore, the distance between the rotation axis of the first rotary electric machine (MG1) and the rotation axis of the pair of output members (38) depends on the positional relationship between the input member (20) and the output differential gear mechanism (40). It will be decided. Therefore, it is difficult to increase the radial dimension of the first rotary electric machine (MG1) while avoiding interference between the first rotary electric machine (MG1) and the pair of output members (38), and the first rotary electric machine (MG1) It was difficult to increase the torque of MG1) and improve the cooling performance.
  • the first rotary electric machine (MG1) and the distribution differential gear mechanism (22) are arranged coaxially with the input member (20). Therefore, while there are restrictions on the axial dimensions of the vehicle drive device (10), the planetary gear mechanism or the like shifts in the power transmission path from the distribution differential gear mechanism (22) to the first rotary electric machine (MG1). It was difficult to provide a mechanism, and the degree of freedom in setting the gear ratio of the power transmission path was low.
  • the characteristic configuration of the vehicle drive device is An input member arranged on the first side in the axial direction, which is one side in the axial direction with respect to the internal combustion engine, and driven and connected to the internal combustion engine. A pair of output members that are driven and connected to the wheels, respectively.
  • An output differential gear mechanism that distributes the input rotation to the pair of output members,
  • the second gear that meshes with the first gear and A first rotating element that is driven and connected to the second gear, a second rotating element that is driven and connected to the input member, and a third that is driven and connected to both the second rotor and the output differential gear mechanism.
  • a differential gear mechanism for distribution equipped with a rotating element
  • the input member, the distribution differential gear mechanism, and the second gear are coaxially arranged.
  • the output differential gear mechanism is arranged on a shaft separate from the input member. The point is that the first rotary electric machine is arranged on a shaft different from the input member.
  • each of the output differential gear mechanism and the first rotary electric machine is arranged on a shaft separate from the input member. Therefore, the degree of freedom in the positional relationship between the rotation axis of the output differential gear mechanism and the rotation axis of the first rotary electric machine is high, and it is easy to secure a large distance between them. As a result, it becomes easy to secure a large radial dimension of the first rotary electric machine while avoiding interference between the first rotary electric machine and the pair of output members.
  • the distribution differential gear mechanism is arranged coaxially with the input member, and the first rotary electric machine is arranged on a shaft different from the input member.
  • the first rotary electric machine and the distribution differential gear mechanism are arranged on different shafts. Then, the first gear and the second gear that mesh with each other are arranged in the power transmission path from the differential gear mechanism for distribution to the first rotary electric machine.
  • the gear ratio of the power transmission path from the differential gear mechanism for distribution to the first rotary electric machine can be easily set to an appropriate value by setting the gear ratio between the first gear and the second gear. it can.
  • the degree of freedom in setting the gear ratio of the power transmission path from the differential gear mechanism for distribution to the first rotary electric machine can be increased.
  • the vehicle drive device 100 includes a first rotary electric machine 1A and a second rotary electric machine 1B, a first rotor gear 2A, an input member 3, a distribution differential gear mechanism 4, and the like. It includes an input gear 5, an output differential gear mechanism 8, and a pair of output members 9.
  • the vehicle drive device 100 further includes a second rotor gear 2B, an idler gear 6, and a counter gear mechanism 7. Further, in the present embodiment, these are housed in the case CS. A part of the input member 3 and a part of the pair of output members 9 are exposed to the outside of the case CS.
  • Each of the input member 3, the distribution differential gear mechanism 4, and the input gear 5 is arranged on the first axis X1 as its rotation axis. That is, the input member 3, the distribution differential gear mechanism 4, and the input gear 5 are coaxially arranged.
  • the idler gear 6 is also arranged on the first axis X1.
  • the first rotary electric machine 1A is arranged on the second axis X2 as its rotation axis. That is, the first rotary electric machine 1A is arranged on a shaft different from the input member 3.
  • the second rotary electric machine 1B, the first rotor gear 2A, and the second rotor gear 2B are also arranged on the second shaft X2.
  • the first rotary electric machine 1A, the second rotary electric machine 1B, the first rotor gear 2A, and the second rotor gear 2B are coaxially arranged.
  • the counter gear mechanism 7 is arranged on the third axis X3 as its rotation axis.
  • Each of the output differential gear mechanism 8 and the pair of output members 9 is arranged on the fourth axis X4 as its rotation axis. That is, the output differential gear mechanism 8 is arranged on a shaft different from the input member 3.
  • These axes X1 to X4 are virtual axes that are different from each other and are arranged in parallel with each other.
  • the direction parallel to the above axes X1 to X4 is referred to as the "axial direction L" of the vehicle drive device 100.
  • the side where the input member 3 is arranged with respect to the internal combustion engine EG is referred to as "axial first side L1”
  • the opposite side is referred to as "axial second side L2”.
  • the direction orthogonal to each of the above axes X1 to X4 is defined as “diameter direction R" with respect to each axis.
  • the first space A1 and the second space A2 are formed inside the case CS.
  • the first space A1 is a space for accommodating the first rotary electric machine 1A and the second rotary electric machine 1B.
  • the second space A2 includes a first rotor gear 2A and a second rotor gear 2B, an input member 3, a distribution differential gear mechanism 4, an input gear 5, an idler gear 6, a counter gear mechanism 7, and an output differential.
  • This is a space for accommodating the gear mechanism 8 and the pair of output members 9.
  • the first space A1 is arranged adjacent to the first side L1 in the axial direction with respect to the second space A2.
  • the case CS has a first peripheral wall portion CSa1 and a second peripheral wall portion CSa2, a partition wall portion CSb, a first side wall portion CSc1, a second side wall portion CSc2, and a third side wall portion CSc3. There is.
  • the first peripheral wall portion CSa1 is formed in a tubular shape that surrounds the outside of the first rotary electric machine 1A and the second rotary electric machine 1B in the radial direction R.
  • the second peripheral wall portion CSa2 includes a first rotor gear 2A and a second rotor gear 2B, an input member 3, a distribution differential gear mechanism 4, an input gear 5, an idler gear 6, a counter gear mechanism 7, and an output difference.
  • the dynamic gear mechanism 8 and the pair of output members 9 are formed in a tubular shape that surrounds the outside in the radial direction R.
  • the partition wall portion CSb is formed so as to partition the first space A1 and the second space A2.
  • the first side wall portion CSc1 is formed so as to close the opening of the first peripheral wall portion CSa1 on the first side L1 in the axial direction.
  • the second side wall portion CSc2 is formed so as to close the opening of the second peripheral wall portion CSa2 on the first side L1 in the axial direction.
  • the third side wall portion CSc3 is formed so as to close the opening of the second peripheral wall portion CSa2 on the second side L2 in the axial direction.
  • the first space A1 is formed by the first peripheral wall portion CSa1, the first side wall portion CSc1, and the partition wall portion CSb. Further, the second space A2 is formed by the second peripheral wall portion CSa2, the partition wall portion CSb, the second side wall portion CSc2, and the third side wall portion CSc3.
  • the first rotary electric machine 1A has a function as a motor (electric motor) that receives power supply and generates power, and a function as a generator (generator) that receives power supply and generates power. .. Therefore, the first rotary electric machine 1A is electrically connected to a power storage device (not shown). As this power storage device, various known power storage devices such as batteries and capacitors can be used. In the present embodiment, the first rotary electric machine 1A functions as a generator that generates electric power by the torque of the internal combustion engine EG, charges the power storage device, or supplies electric power for driving the second rotary electric machine 1B.
  • the first rotary electric machine 1A may function as a motor that powers and generates a driving force (synonymous with "torque") when the vehicle is traveling at high speed or when the internal combustion engine EG is started.
  • the internal combustion engine EG is a prime mover (gasoline engine, diesel engine, etc.) that is driven by combustion of fuel to extract power.
  • the first rotary electric machine 1A includes a first stator 11A and a first rotor 12A.
  • the first stator 11A has a first stator core 111A fixed to a non-rotating member (here, case CS).
  • the first rotor 12A has a first rotor core 121A that is rotatable with respect to the first stator 11A.
  • the first rotary electric machine 1A is an inner rotor type rotary electric machine, the first rotor core 121A is arranged inside the radial direction R of the first stator core 111A.
  • the first rotary electric machine 1A is a rotating field type rotary electric machine. Therefore, as shown in FIG. 3, the first stator core 111A has coil end portions protruding from the first stator core 111A on both sides in the axial direction L (the first side L1 in the axial direction and the second side L2 in the axial direction), respectively.
  • the first stator coil 112A is wound so as to be formed.
  • a first permanent magnet 122A is provided on the first rotor core 121A.
  • the first terminal portion 113A which is the terminal portion of the first stator coil 112A, protrudes to the side of the second rotary electric machine 1B in the axial direction L (the second side L2 in the axial direction).
  • the first terminal portion 113A is included in the coil end portion of the first stator coil 112A on the second side L2 in the axial direction, and protrudes toward the second side L2 in the axial direction with respect to other portions in the coil end portion.
  • the first terminal portion 113A is arranged in a part of the circumferential direction of the first rotary electric machine 1A.
  • the second rotary electric machine 1B has a function as a motor (electric motor) that receives power supply and generates power, and a function as a generator (generator) that receives power supply and generates power. .. Therefore, the second rotary electric machine 1B is also electrically connected to the above-mentioned power storage device in the same manner as the first rotary electric machine 1A.
  • the second rotary electric machine 1B mainly functions as a motor that generates a driving force for traveling the vehicle.
  • the second rotary electric machine 1B may function as a generator that regenerates the inertial force of the vehicle as electric energy.
  • the second rotary electric machine 1B includes a second stator 11B and a second rotor 12B.
  • the second stator 11B has a second stator core 111B fixed to a non-rotating member (here, case CS).
  • the second rotor 12B has a second rotor core 121B that is rotatable with respect to the second stator 11B.
  • the second rotary electric machine 1B is an inner rotor type rotary electric machine
  • the second rotor core 121B is arranged inside the second stator core 111B in the radial direction R.
  • the second rotary electric machine 1B is a rotating field type rotary electric machine. Therefore, the second stator core 111B is formed with coil end portions protruding from the second stator core 111B on both sides in the axial direction L (the first side L1 in the axial direction and the second side L2 in the axial direction). The stator coil 112B is wound around it. A second permanent magnet 122B is provided on the second rotor core 121B.
  • the second terminal portion 113B which is the terminal portion of the second stator coil 112B, protrudes to the side of the first rotary electric machine 1A in the axial direction L (the first side L1 in the axial direction).
  • the second terminal portion 113B is included in the coil end portion of the second stator coil 112B on the first side L1 in the axial direction, and protrudes toward the first side L1 in the axial direction with respect to other portions in the coil end portion.
  • the second terminal portion 113B is arranged in a part of the circumferential direction of the second rotary electric machine 1B.
  • the coil end portion of the first stator coil 112A and the coil end portion of the second stator coil 112B are arranged so as to face each other in the axial direction L.
  • the first terminal portion 113A and the second terminal portion 113B are arranged at different positions in the circumferential direction with respect to the second axis X2, and the arrangement region of the first terminal portion 113A in the axial direction L and the first terminal portion 113A are arranged.
  • the two terminal portions 113B overlap with the arrangement region in the axial direction L.
  • the portion of the coil end portion of the first stator coil 112A excluding the first terminal portion 113A and the portion of the coil end portion of the second stator coil 112B excluding the second terminal portion 113B are in axial L directions with each other. It is separated.
  • the first rotor gear 2A corresponds to the "first gear” that rotates integrally with the first rotor 12A.
  • the first rotor gear 2A is integrally connected to the first rotor 12A via the first rotor shaft 21A.
  • the first rotor shaft 21A is formed in a tubular shape extending along the axial direction L.
  • the first rotor gear 2A is formed on the outer peripheral surface of the end portion of the second side L2 in the axial direction of the first rotor shaft 21A.
  • the first rotor shaft 21A is arranged so as to penetrate the partition wall portion CSb in the axial direction L.
  • the first rotor shaft 21A is rotatably supported with respect to the partition wall portion CSb via the first rotor shaft support bearing B1.
  • the first rotor shaft 21A is connected so as to rotate integrally with the first rotor support member 13A that supports the first rotor 12A.
  • the first rotor support member 13A has a first support portion 131A and a first connecting portion 132A.
  • the first support portion 131A is formed in a tubular shape extending along the axial direction L.
  • the first support portion 131A supports the first rotor 12A from the inside in the radial direction R.
  • the first connecting portion 132A is formed in a tubular shape extending along the axial direction L.
  • the first connecting portion 132A has a smaller diameter than the first supporting portion 131A and is formed to have a larger diameter than the first rotor shaft 21A.
  • the first connecting portion 132A is connected to the first supporting portion 131A so as to rotate integrally with the first supporting portion 131A in a state of being arranged inside the radial direction R. Further, the first connecting portion 132A is connected so as to rotate integrally with the first rotor shaft 21A in a state of being arranged outside the radial direction R with respect to the first rotor shaft 21A.
  • the first connecting portion 132A is integrally connected to the first rotor shaft 21A by spline engagement.
  • the first connecting portion 132A is rotatably supported with respect to the case CS by a pair of first rotor bearings B2.
  • the pair of first rotor bearings B2 are arranged on both sides in the axial direction L with the connecting portion between the first connecting portion 132A and the first supporting portion 131A interposed therebetween.
  • the first rotor bearing B2 on the second side L2 in the axial direction is supported by the partition wall portion CSb.
  • the first rotor bearing B2 on the first side L1 in the axial direction is supported by the first support wall portion CSd1.
  • the first support wall portion CSd1 is integrally connected to the second support wall portion CSd2 fixed to the first peripheral wall portion CSa1.
  • the first support wall portion CSd1 is adjacent to the second support wall portion CSd2 in the axial direction and is integrally connected to the second support wall portion CSd2 by bolt fastening.
  • the first support wall portion CSd1 and the second support wall portion CSd2 extend along the radial direction R with respect to the second axis X2.
  • the first support wall portion CSd1 and the second support wall portion CSd2 are arranged between the first rotor 12A and the second rotor 12B in the axial direction L.
  • the first support wall portion CSd1 is arranged inside the coil end portion of the first stator coil 112A and the coil end portion of the second stator coil 112B in the radial direction R.
  • the second support wall portion CSd2 has a diameter larger than that of the coil end portion through a portion in which the coil end portions of the first stator coil 112A and the second stator coil 112B are separated from each other in the axial direction L. It extends from the inside to the outside of the direction R. Then, the first stator core 111A and the second stator core 111B are connected to the outer portion of the second support wall portion CSd2 in the radial direction R from the coil end portion by bolt fastening.
  • the second rotor gear 2B corresponds to a "fourth gear” that rotates integrally with the second rotor 12B.
  • the second rotor gear 2B is integrally connected to the second rotor 12B via the second rotor shaft 21B. Further, in the present embodiment, the second rotor gear 2B has a smaller diameter than the first rotor gear 2A.
  • the second rotor shaft 21B is formed so as to extend along the axial direction L.
  • the second rotor shaft 21B is arranged so as to penetrate the inside of the first rotor shaft 21A in the radial direction R in the axial direction L.
  • the second rotor gear 2B is formed on the outer peripheral surface of the portion of the second rotor shaft 21B located on the second side L2 in the axial direction with respect to the first rotor shaft 21A.
  • the second rotor shaft 21B is rotatably supported with respect to the case CS by a pair of second rotor shaft support bearings B3 arranged at different positions in the axial direction L.
  • the second rotor shaft 21B extends from the first side wall portion CSc1 to the third side wall portion CSc3.
  • the second rotor shaft 21B is rotatably supported with respect to the first side wall portion CSc1 via the second rotor shaft support bearing B3 on the first side L1 in the axial direction.
  • the second rotor shaft 21B is rotatably supported with respect to the third side wall portion CSc3 via the second rotor shaft support bearing B3 on the second side L2 in the axial direction.
  • the second rotor shaft 21B is connected so as to rotate integrally with the second rotor support member 13B that supports the second rotor 12B.
  • the second rotor support member 13B has a second support portion 131B and a second connecting portion 132B.
  • the second support portion 131B is formed in a tubular shape extending along the axial direction L.
  • the second support portion 131B supports the second rotor 12B from the inside in the radial direction R.
  • the second connecting portion 132B is formed in a tubular shape extending along the axial direction L.
  • the second connecting portion 132B has a smaller diameter than the second supporting portion 131B and is formed to have a larger diameter than the second rotor shaft 21B.
  • the second connecting portion 132B is connected to the second supporting portion 131B so as to rotate integrally with the second supporting portion 131B in a state of being arranged inside the radial direction R. Further, the second connecting portion 132B is connected so as to rotate integrally with the second rotor shaft 21B in a state of being arranged outside the radial direction R with respect to the second rotor shaft 21B.
  • the second connecting portion 132B is integrally connected to the second rotor shaft 21B by spline engagement.
  • the second connecting portion 132B is rotatably supported with respect to the case CS by a pair of second rotor bearings B4.
  • the pair of second rotor bearings B4 are arranged on both sides in the axial direction L with the connecting portion between the second connecting portion 132B and the second supporting portion 131B interposed therebetween.
  • the second rotor bearing B4 on the first side L1 in the axial direction is supported by the first side wall portion CSc1.
  • the second rotor bearing B4 on the second side L2 in the axial direction is supported by the second support wall portion CSd2.
  • the first rotary electric machine 1A is arranged on the first side L1 in the axial direction with respect to the distribution differential gear mechanism 4. Further, in the present embodiment, the second rotor gear 2B, the first rotor gear 2A, the first rotary electric machine 1A, and the second rotary electric machine 1B are described in the order described from the second side L2 in the axial direction to the first side L1 in the axial direction. It is arranged in.
  • the input member 3 is formed so as to extend along the axial direction L. In the present embodiment, the input member 3 penetrates the third side wall portion CSc3 in the axial direction L so as to project from the third side wall portion CSc3 toward the second side L2 in the axial direction.
  • the input member 3 is drive-connected to the internal combustion engine EG. In the present embodiment, the input member 3 is driven and connected to the output shaft (crankshaft or the like) of the internal combustion engine EG via the damper device DP.
  • the damper device DP is a device that attenuates fluctuations in the transmitted torque. In the present embodiment, in order to limit the excessive load from acting on the power transmission path from the output member 9 to the internal combustion engine EG when an excessive torque is input to the damper device DP from the output side. Torque limiter is provided.
  • the “driving connection” refers to a state in which two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, or the said. It includes a state in which two rotating elements are mutably connected so that a driving force can be transmitted via one or more transmission members.
  • Such transmission members include various members that transmit rotation at the same speed or at different speeds, such as shafts, gear mechanisms, belts, chains, and the like.
  • the transmission member may include an engaging device that selectively transmits rotation and driving force, for example, a friction engaging device, a meshing type engaging device, and the like.
  • each rotating element of the distribution differential gear mechanism 4 and the output differential gear mechanism 8 is referred to as "drive connection"
  • the distribution differential gear mechanism 4 and the output differential gear mechanism 8 are respectively used. It refers to a state in which at least three rotating elements provided in the above are driven and connected to each other without interposing other rotating elements.
  • the distribution differential gear mechanism 4 distributes the driving force of the internal combustion engine EG transmitted to the input member 3 to the first rotary electric machine 1A, the second rotary electric machine 1B, and the output differential gear mechanism 8. It is configured. In the present embodiment, the distribution differential gear mechanism 4 distributes to the input gear 5 and the idler gear 6. As described above, the vehicle drive device 100 according to the present embodiment is configured as a so-called split type hybrid vehicle drive device.
  • the distribution differential gear mechanism 4 is a single pinion type planetary gear mechanism. Specifically, the distribution differential gear mechanism 4 includes a carrier C4 that supports the pinion gear P4, a sun gear S4 that meshes with the pinion gear P4, and a ring gear that is arranged outside the sun gear S4 in the radial direction R and meshes with the pinion gear P4. It is equipped with R4.
  • the carrier C4 is an input element of the distribution differential gear mechanism 4, and is connected to the input member 3 so as to rotate integrally. That is, in the present embodiment, the carrier C4 corresponds to the "second rotating element” that is driven and connected to the input member 3.
  • the pinion gear P4 is rotatably supported by the carrier C4.
  • the pinion gear P4 rotates (rotates) around its axis and rotates (revolves) around the sun gear S4.
  • a plurality of pinion gears P4 are provided along the revolution trajectory.
  • the sun gear S4 is one of the rotating elements after distribution of the driving force in the distribution differential gear mechanism 4, and is connected so as to rotate integrally with the input gear 5. That is, in the present embodiment, the sun gear S4 corresponds to the "first rotating element” that is driven and connected to the second gear (input gear 5).
  • the ring gear R4 is the other of the rotating elements after the distribution of the driving force in the distribution differential gear mechanism 4.
  • the ring gear R4 corresponds to a "third rotating element" that is driven and connected to both the second rotor 12B of the second rotating electric machine 1B and the output differential gear mechanism 8.
  • the ring gear R4 is connected so as to rotate integrally with the cylindrical gear forming member 41 extending along the axial direction L.
  • the ring gear R4 is formed on the inner peripheral surface of the region of the gear forming member 41 on the first side L1 in the axial direction with respect to the idler gear 6.
  • the input gear 5 meshes with the first rotor gear 2A. That is, the input gear 5 corresponds to a "second gear” that meshes with the first gear (first rotor gear 2A).
  • the gear ratio between the first rotor gear 2A and the input gear 5 is such that the rotation of the first rotating element (here, the sun gear S4) of the differential gear mechanism 4 for distribution is accelerated and the first rotating electric machine is used. It is set to be transmitted to 1A.
  • the input gear 5 is rotatably supported from the inside in the radial direction R by the input bearing B5 supported by the partition wall portion CSb.
  • the idler gear 6 meshes with the second rotor gear 2B. Further, the idler gear 6 is driven and connected to the output differential gear mechanism 8. In the present embodiment, the idler gear 6 is driven and connected to the output differential gear mechanism 8 via the counter gear mechanism 7. Further, in the present embodiment, the idler gear 6 is connected via the gear forming member 41 so as to rotate integrally with the ring gear R4 of the distribution differential gear mechanism 4. That is, the idler gear 6 corresponds to a "third gear” that rotates integrally with the third rotating element (ring gear R4). In the illustrated example, the idler gear 6 is formed on the outer peripheral surface of the region of the gear forming member 41 on the second side L2 in the axial direction with respect to the ring gear R4.
  • the idler gear 6 is arranged coaxially with the input member 3, the second gear, and the distribution differential gear mechanism.
  • the idler gear 6 is rotatably supported from the inside of the radial direction R by the idler bearing B6 supported by the cylindrical cylindrical wall portion CSe extending along the axial direction L. That is, the idler bearing B6 is interposed between the inner peripheral surface of the idler gear 6 and the outer peripheral surface of the cylinder wall portion CSe.
  • the tubular wall portion CSe is formed so as to project from the third side wall portion CSc3 toward the first side L1 in the axial direction.
  • the counter gear mechanism 7 has a counter shaft 71, a first counter gear 72, and a second counter gear 73.
  • the counter shaft 71 is formed so as to extend along the axial direction L.
  • the counter shaft 71 is rotatably supported with respect to the case CS by a pair of counter bearings B7 arranged at different positions in the axial direction L.
  • the counter shaft 71 extends from the partition wall portion CSb to the third side wall portion CSc3.
  • the counter shaft 71 is rotatably supported with respect to the partition wall portion CSb via the counter bearing B7 on the first side L1 in the axial direction.
  • the counter shaft 71 is rotatably supported with respect to the third side wall portion CSc3 via the counter bearing B7 on the second side L2 in the axial direction.
  • the first counter gear 72 is an input element of the counter gear mechanism 7.
  • the first counter gear 72 meshes with the idler gear 6 at a position different from that of the second rotor gear 2B in the circumferential direction of the idler gear 6. That is, the first counter gear 72 corresponds to the "fifth gear” that meshes with the third gear (idler gear 6).
  • the first counter gear 72 is connected to the counter shaft 71 by spline engagement.
  • the second counter gear 73 is an output element of the counter gear mechanism 7.
  • the second counter gear 73 rotates integrally with the first counter gear 72 via the counter shaft 71. That is, the second counter gear 73 corresponds to the "sixth gear” that rotates integrally with the fifth gear (first counter gear 72).
  • the second counter gear 73 is arranged on the first side L1 in the axial direction with respect to the first counter gear 72. Further, in the present embodiment, the second counter gear 73 is formed to have a smaller diameter than the first counter gear 72.
  • the output differential gear mechanism 8 includes a differential input gear 81 which is an input element of the output differential gear mechanism 8.
  • the output differential gear mechanism 8 is configured to distribute the rotation input to the output differential gear mechanism 8, that is, the rotation of the differential input gear 81, to the pair of output members 9.
  • the differential input gear 81 meshes with the second counter gear 73 of the counter gear mechanism 7. That is, the differential input gear 81 corresponds to the "seventh gear” that meshes with the sixth gear (second counter gear 73).
  • the differential input gear 81 and the second counter gear 73 are arranged so that their axial L arrangement areas overlap with the axial L arrangement areas of the distribution differential gear mechanism 4. ..
  • the output differential gear mechanism 8 includes a differential case 82, a pair of differential pinion gears 83, and a pair of side gears 84, in addition to the above-mentioned differential input gear 81.
  • the pair of differential pinion gears 83 and the pair of side gears 84 are both bevel gears.
  • the differential case 82 is connected so as to rotate integrally with the differential input gear 81.
  • the differential case 82 is rotatably supported with respect to the case CS by a pair of differential bearings B8 arranged at different positions in the axial direction L.
  • the differential case 82 is arranged from the second side wall portion CSc2 to the third side wall portion CSc3.
  • the differential case 82 is rotatably supported with respect to the second side wall portion CSc2 via the differential bearing B8 on the first side L1 in the axial direction.
  • the differential case 82 is rotatably supported with respect to the third side wall portion CSc3 via the differential bearing B8 on the second side L2 in the axial direction.
  • the differential case 82 is a hollow member.
  • a pair of differential pinion gears 83 and a pair of side gears 84 are housed inside the differential case 82.
  • the pair of differential pinion gears 83 are arranged so as to face each other at intervals along the radial direction R with respect to the fourth axis X4.
  • Each of the pair of differential pinion gears 83 is attached to a differential pinion shaft 83a supported so as to rotate integrally with the differential case 82.
  • Each of the pair of differential pinion gears 83 is configured to be rotatable (rotated) about the differential pinion shaft 83a and rotatable (revolved) about the fourth axis X4.
  • the pair of side gears 84 are rotating elements after distribution of the driving force in the output differential gear mechanism 8.
  • the pair of side gears 84 are arranged so as to face each other with the pair of differential pinion shafts 83a interposed therebetween at intervals in the axial direction L.
  • the pair of side gears 84 mesh with the pair of differential pinion gears 83.
  • Each of the pair of side gears 84 is connected so as to rotate integrally with the output member 9.
  • Each of the pair of output members 9 is drive-connected to the wheel W.
  • the pair of output members 9 are formed so as to project from the output differential gear mechanism 8 on both sides in the axial direction L.
  • each of the pair of output members 9 is connected so as to rotate integrally with the side gear 84.
  • the output member 9 on the first side L1 in the axial direction is integrally connected to the side gear 84 so as to project from the side gear 84 on the first side L1 in the axial direction to L1 on the first side in the axial direction. ..
  • each of the pair of output members 9 is formed in a cylindrical shape in which the end faces on both sides in the axial direction L are open.
  • the output member 9 on the first side L1 in the axial direction is exposed to the outside of the case CS so that the end portion of the first side L1 in the axial direction penetrates the second side wall portion CSc2 in the axial direction L.
  • the output member 9 on the second side L2 in the axial direction is arranged so that the end portion of the second side L2 in the axial direction penetrates the third side wall portion CSc3 in the axial direction L and is exposed to the outside of the case CS.
  • drive shafts (not shown) that are drive-connected to the wheels W are arranged inside the radial direction R of each output member 9, and they are connected so as to rotate integrally. ..
  • corresponding splines are formed on the inner peripheral surface of the output member 9 and the outer peripheral surface of the drive shaft, and the splines are engaged with each other to integrally integrate the output member 9 and the drive shaft. It is connected so as to rotate.
  • the vehicle drive device 100 further includes a hydraulic pump OP that discharges oil.
  • the hydraulic pump OP includes a pump drive gear OPa for driving the hydraulic pump OP.
  • the pump drive gear OPa meshes with the first rotor gear 2A at a position different from the input gear 5 in the circumferential direction of the first rotor gear 2A.
  • the vehicle drive device 100 includes a first rotation sensor Se1 that detects the rotation of the first rotor 12A and a second rotation sensor that detects the rotation of the second rotor 12B. It also has Se2.
  • the first rotation sensor Se1 and the second rotation sensor Se2 are arranged between the first rotor 12A and the second rotor 12B in the axial direction L.
  • each of the first rotation sensor Se1 and the second rotation sensor Se2 is a resolver.
  • the stator of the first rotation sensor Se1 is supported by the first support wall portion CSd1
  • the rotor of the first rotation sensor Se1 is supported by the first connecting portion 132A of the first rotor support member 13A.
  • the stator of the second rotation sensor Se2 is supported by the second support wall portion CSd2
  • the rotor of the second rotation sensor Se2 is supported by the second connecting portion 132B of the second rotor support member 13B.
  • FIG. 5 shows the first rotary electric machine 1A and the second rotary electric machine 1B, the first rotor gear 2A and the second rotor gear 2B, the differential gear mechanism for distribution 4, the input gear 5, the idler gear 6, the first counter gear 72 and the second.
  • the outer shapes of the counter gear 73, the differential input gear 81, and the pump drive gear OPa are shown.
  • the outer diameter of the first rotary electric machine 1A (first stator 11A) and the outer diameter of the second rotary electric machine 1B (second stator 11B) are the same.
  • the rotation axis (second axis X2) of the first rotary electric machine 1A is the rotation axis (first axis) of the input member 3 in the axial view along the axial direction L. It is arranged on the side opposite to the side of the rotation axis (fourth axis X4) of the output differential gear mechanism 8 with respect to X1).
  • the second virtual plane IP1 including the first axis X1 and the fourth axis X4 is orthogonal to the first virtual plane IP1 including the first axis X1.
  • the second axis X2 is arranged on the side opposite to the fourth axis X4.
  • the rotation axis (third axis X3) of the counter gear mechanism 7 is the rotation axis (third axis X3) of the first rotary electric machine 1A with respect to the rotation axis (first axis X1) of the input member 3. It is arranged on the side opposite to the side of the second axis X2).
  • the third axis X3 is arranged between the first axis X1 and the fourth axis X4 in the direction along the first virtual plane IP1.
  • the counter gear mechanism 7 is arranged so as to overlap with the first rotary electric machine 1A in the axial direction along the axial direction L.
  • a part of the counter gear mechanism 7 (specifically, a part of the first counter gear 72 and a part of the second counter gear 73) is an axial view of the first rotary electric machine 1A and It overlaps with both of the second rotary electric machines 1B.
  • "overlapping in a specific direction” means that the virtual straight line is 2 when the virtual straight line parallel to the line-of-sight direction is moved in each direction orthogonal to the virtual straight line. It means that there is at least a part of the area where both of the two elements intersect.
  • the distribution differential gear mechanism 4 is also arranged so as to overlap with the first rotary electric machine 1A in the axial direction along the axial direction L.
  • the entire distribution differential gear mechanism 4 overlaps with both the first rotary electric machine 1A and the second rotary electric machine 1B in the axial direction.
  • the input gear 5, the idler gear 6, and the hydraulic pump OP are also arranged so as to overlap with the first rotary electric machine 1A in the axial direction along the axial direction L.
  • the input gear 5, the idler gear 6, and the hydraulic pump OP as a whole overlap with both the first rotary electric machine 1A and the second rotary electric machine 1B in the axial direction.
  • the configuration in which the second counter gear 73 is arranged on the first side L1 in the axial direction with respect to the first counter gear 72 has been described as an example, but the configuration is not limited to such a configuration.
  • the second counter gear 73 may be arranged on the second side L2 in the axial direction with respect to the first counter gear 72.
  • the ring gear R4 and the idler gear 6 are arranged so as to overlap each other in a radial direction along the radial direction R with respect to the first axis X1.
  • the arrangement area of the first counter gear 72 in the axial direction L overlaps with the arrangement area of the distribution differential gear mechanism 4 in the axial direction L.
  • the rotation axis (second axis X2) of the first rotary electric machine 1A becomes the rotation axis (first axis X1) of the input member 3 in the axial view along the axial direction L.
  • the rotation axis (second axis X2) of the first rotary electric machine 1A is the first virtual center with respect to the rotation axis (first axis X1) of the input member 3. It may be arranged on the same side as the rotation axis (fourth axis X4) side of the output differential gear mechanism 8 in the direction along the plane IP1.
  • the gear ratio between the first rotor gear 2A and the input gear 5 is increased by increasing the rotation of the first rotating element (sun gear S4) of the distribution differential gear mechanism 4 to make the first rotation.
  • the gear ratio of the first rotor gear 2A and the input gear 5 may be appropriately changed without being limited to such a configuration. Therefore, the gear ratio between the first rotor gear 2A and the input gear 5 is transmitted to the first rotating electric machine 1A while the rotation of the first rotating element remains at the same speed, or the rotation of the first rotating element is decelerated. It may be set to be transmitted to the first rotary electric machine 1A.
  • first rotary electric machine 1A and the second rotary electric machine 1B are arranged coaxially
  • first rotary electric machine 1A and the second rotary electric machine 1B may be arranged on different axes.
  • the configuration in which the idler gear 6 is arranged coaxially with the input member 3, the distribution differential gear mechanism 4, and the input gear 5 has been described as an example.
  • the idler gear 6 may be arranged on a shaft different from the input member 3, the distribution differential gear mechanism 4, and the input gear 5.
  • the second rotor gear 2B, the first rotor gear 2A, the first rotary electric machine 1A, and the second rotary electric machine 1B are described from the second side L2 in the axial direction to the first side L1 in the axial direction.
  • the configuration arranged in the order of is described as an example.
  • the first rotary electric machine 1A may be arranged on the first side L1 in the axial direction with respect to the second rotary electric machine 1B.
  • the first rotor gear 2A may be arranged on the second side L2 in the axial direction with respect to the second rotor gear 2B.
  • the arrangement area of both the second counter gear 73 and the differential input gear 81 in the axial direction L overlaps with the arrangement area of the distribution differential gear mechanism 4 in the axial direction L.
  • the arrangement area of both the second counter gear 73 and the differential input gear 81 in the axial direction L is the arrangement area of the distribution differential gear mechanism 4 in the axial direction L. It does not have to overlap.
  • the vehicle drive device (100) An input member (3) arranged on the first side (L1) in the axial direction, which is one side in the axial direction (L) with respect to the internal combustion engine (EG), and driven and connected to the internal combustion engine (EG).
  • a pair of output members (9) that are driven and connected to the wheels (W), respectively.
  • An output differential gear mechanism (8) that distributes the input rotation to the pair of output members (9).
  • a distribution differential gear mechanism (4) having a third rotating element (R4) driven and connected to both of the differential gear mechanism (8) is provided.
  • the input member (3), the distribution differential gear mechanism (4), and the second gear (5) are coaxially arranged.
  • the output differential gear mechanism (8) is arranged on a shaft separate from the input member (3).
  • the first rotary electric machine (1A) is arranged on a shaft different from the input member (3).
  • the output differential gear mechanism (8) and the first rotary electric machine (1A) are arranged on separate axes from the input member (3). Therefore, the degree of freedom in the positional relationship between the rotary axis (X4) of the output differential gear mechanism (8) and the rotary axis (X2) of the first rotary electric machine (1A) is high, and the distance between them is increased. , It is easy to secure a large size. As a result, it becomes easy to secure a large radial dimension (R) of the first rotary electric machine (1A) while avoiding interference between the first rotary electric machine (1A) and the pair of output members (9). ..
  • the distribution differential gear mechanism (4) is arranged coaxially with the input member (3), and the first rotary electric machine (1A) is on a different axis from the input member (3). Have been placed. That is, the first rotary electric machine (1A) and the distribution differential gear mechanism (4) are arranged on different axes.
  • the first gear (2A) and the second gear (5) that mesh with each other are arranged in the power transmission path from the distribution differential gear mechanism (4) to the first rotary electric machine (1A).
  • the gear ratio of the power transmission path from the differential gear mechanism for distribution (4) to the first rotary electric machine (1A) can be set by setting the gear ratio between the first gear (2A) and the second gear (5). Can be easily set to an appropriate value.
  • the degree of freedom in setting the gear ratio of the power transmission path from the distribution differential gear mechanism (4) to the first rotary electric machine (1A) can be increased.
  • the first rotary electric machine (1A) is arranged on the first side (L1) in the axial direction with respect to the distribution differential gear mechanism (4).
  • the first rotary electric machine (1A) is arranged at a position separated from the internal combustion engine (EG) in the axial direction (L).
  • the diameter of the connecting portion with the internal combustion engine (EG) is larger than that in which the first rotary electric machine (1A) is arranged on the internal combustion engine (EG) side with respect to the distribution differential gear mechanism (4). It becomes easy to secure a large radial dimension (R) of the first rotary electric machine (1A) without affecting the dimension in the direction (R).
  • the distribution differential gear mechanism (4) can be easily arranged close to the internal combustion engine (EG), and the output differential gear mechanism (8) can be easily arranged close to the internal combustion engine (EG).
  • the dimensional difference in the axial direction (L) of the pair of output members (9) arranged on both sides in the axial direction (L) with respect to the output differential gear mechanism (8) can be suppressed to be small. Therefore, when the vehicle drive device (100) is mounted on the vehicle, deterioration of the steerability of the vehicle due to the dimensional difference in the axial direction (L) of the pair of output members (9) can be suppressed.
  • the rotation axis (X2) of the first rotary electric machine (1A) is the rotation axis (X1) of the input member (3). It is preferable that the output differential gear mechanism (8) is arranged on the side opposite to the side of the rotation axis (X4).
  • the gear ratio between the first gear (2A) and the second gear (5) is transmitted to the first rotating electric machine (1A) by accelerating the rotation of the first rotating element (S4). It is preferable that it is set to be.
  • the first rotor (1A) since the rotation of the first rotating element (S4) is accelerated and transmitted to the first rotating electric machine (1A), the first rotor (1A) has a rotation speed higher than that of the internal combustion engine (EG). 12A) can be rotated. As a result, the torque of the first rotary electric machine (1A) required to generate the same electric power is reduced, so that the first rotary electric machine (1A) can be easily miniaturized. Therefore, it is easy to miniaturize the vehicle drive device (100).
  • a third gear (6) that rotates integrally with the third rotating element (R4) and A fourth gear (2B) that meshes with the third gear (6) and rotates integrally with the second rotor (12B) is further provided.
  • the first rotary electric machine (1A) and the second rotary electric machine (1B) are coaxially arranged.
  • the third gear (6) is arranged coaxially with the input member (3), the second gear (5), and the distribution differential gear mechanism (4), and the output differential gear mechanism (8). ) Is driven and connected.
  • the first rotary electric machine (1A) and the second rotary electric machine (1B) are coaxially arranged, and the input member (3), the differential gear mechanism for distribution (4), and the second The gear (5) and the third gear (6) are arranged coaxially.
  • the first rotary electric machine (1A), the second rotary electric machine (1B), the first gear (2A), and the fourth gear (2B) are coaxially arranged.
  • the side opposite to the axial first side (L1) in the axial direction (L) is defined as the axial second side (L2). From the axial second side (L2) to the axial first side (L1), the fourth gear (2B), the first gear (2A), the first rotary electric machine (1A), the first It is preferable that the two-rotating electric machine (1B) is arranged in this order.
  • the first rotary electric machine (1A) and the second rotary electric machine (1B) can be arranged away from the internal combustion engine (EG) in the axial direction (L). As a result, it becomes easy to secure a large radial dimension (R) of the first rotary electric machine (1A) and the second rotary electric machine (1B).
  • a counter gear mechanism (7) having a fifth gear (72) that meshes with the third gear (6) and a sixth gear (73) that rotates integrally with the fifth gear (72) is further provided.
  • the output differential gear mechanism (8) includes a seventh gear (81) that meshes with the sixth gear (73), and distributes the rotation of the seventh gear (81) to the pair of output members (9).
  • Configured to The axial direction (L) arrangement area of both the sixth gear (73) and the seventh gear (81) is the axial direction (L) arrangement area of the distribution differential gear mechanism (4). It is preferable that they overlap.
  • the arrangement area of both the sixth gear (73) and the seventh gear (81) in the axial direction (L) is the arrangement area of the differential gear mechanism (4) for distribution in the axial direction (L).
  • the size of the vehicle drive device (100) in the axial direction (L) can be easily reduced.
  • the counter gear mechanism (7) is arranged so as to overlap with the first rotary electric machine (1A) in the axial direction along the axial direction (L).
  • the counter gear mechanism (7) is arranged by utilizing the space overlapping with the first rotary electric machine (1A) in the axial direction. As a result, it is possible to suppress an increase in the radial dimension (R) of the vehicle drive device (100) due to the arrangement of the counter gear mechanism (7).
  • the distribution differential gear mechanism (4) is arranged so as to overlap with the first rotary electric machine (1A) in the axial direction along the axial direction (L).
  • the distribution differential gear mechanism (4) is arranged by utilizing the space overlapping with the first rotary electric machine (1A) in the axial direction. As a result, it is possible to suppress an increase in the radial dimension (R) of the vehicle drive device (100) due to the arrangement of the distribution differential gear mechanism (4).
  • a third gear (6) that rotates integrally with the third rotating element (R4) and A fourth gear (2B) that meshes with the third gear (6) and rotates integrally with the second rotor (12B) is further provided.
  • the first rotor (12A) and the first gear (2A) are connected by a first rotor shaft (21A).
  • the second rotor (12B) and the fourth gear (2B) are connected by a second rotor shaft (21B). It is preferable that the second rotor shaft (21B) is arranged so as to penetrate the inside of the first rotor shaft (21A) in the radial direction (R) in the axial direction (L).
  • the second rotor shaft (21B) is connected to the second rotor shaft (21B) as compared with the configuration in which the second rotor shaft (21B) is arranged outside the radial direction (R) of the first rotor shaft (21A). It becomes easy to reduce the outer diameter of the fourth gear (2B). Therefore, the gear ratio of the power transmission path from the second rotary electric machine (1B) to the output differential gear mechanism (8) can be freely set while keeping the radial (R) dimension of the vehicle drive device (100) small. It becomes easy to increase the degree.
  • a third gear (6) that rotates integrally with the third rotating element (R4) and A fourth gear (2B) that meshes with the third gear (6) and rotates integrally with the second rotor (12B) is further provided. It is preferable that the fourth gear (2B) has a smaller diameter than the first gear (2A).
  • the technology according to the present disclosure includes a first rotary electric machine, a second rotary electric machine, an input member that is driven and connected to an internal combustion engine, a pair of output members that are driven and connected to wheels, and an internal combustion engine that is transmitted to the input member. It can be used in a vehicle drive device including a distribution differential gear mechanism that distributes the driving force of the above and an output differential gear mechanism that distributes the input rotation to a pair of output members.
  • Vehicle drive device 1A 1st rotary electric machine 12A: 1st rotor 1B: 2nd rotary electric machine 12B: 2nd rotor 2A: 1st rotor gear (1st gear) 3: Input member 4: Differential gear mechanism for distribution S4: Sun gear (first rotating element) C4: Carrier (second rotating element) R4: Ring gear (third rotating element) 5: Input gear (second gear) 8: Differential gear mechanism for output 9: Output member EG: Internal combustion engine W: Wheel L: Axial direction L1: Axial direction first side L2: Axial direction second side

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  • Electric Propulsion And Braking For Vehicles (AREA)

Abstract

L'invention concerne un dispositif d'entraînement de véhicule (100) pourvu : d'un élément d'entrée (3) ; d'une paire d'éléments de sortie (9) ; d'un mécanisme d'engrenage différentiel de sortie (8) ; d'une première machine électrique rotative (1A) ; d'une seconde machine électrique rotative (1B) ; d'un premier engrenage (2A) qui tourne d'un seul tenant avec un premier rotor (12A) de la première machine électrique rotative (1A) ; d'un second engrenage (5) qui s'engrène avec le premier engrenage (2A) ; et d'un mécanisme d'engrenage différentiel de distribution (4) pourvu d'un premier élément rotatif (S4) relié au second engrenage (5) de manière à être entraîné, d'un deuxième élément rotatif (C4) relié à l'élément d'entrée (3) de manière à être entraîné et d'un troisième élément rotatif (R4) relié à la fois à un second rotor (12B) et au mécanisme d'engrenage différentiel de sortie (8) de manière à être entraîné, l'élément d'entrée (3), le mécanisme d'engrenage différentiel de distribution (4) et le second engrenage (5) étant disposés coaxialement, le mécanisme d'engrenage différentiel de sortie (8) et l'élément d'entrée (3) étant disposés de manière non coaxiale et la première machine électrique rotative (1A) et l'élément d'entrée (3) étant disposés de manière non coaxiale.
PCT/JP2020/011425 2019-06-25 2020-03-16 Dispositif d'entraînement de véhicule Ceased WO2020261669A1 (fr)

Applications Claiming Priority (2)

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JP2019117440 2019-06-25
JP2019-117440 2019-06-25

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WO2020261669A1 true WO2020261669A1 (fr) 2020-12-30

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009011328A1 (fr) * 2007-07-18 2009-01-22 Aisin Aw Co., Ltd. Dispositif d'entraînement pour véhicule hybride
JP2013159212A (ja) * 2012-02-03 2013-08-19 Toyota Motor Corp 動力伝達装置
JP2017154736A (ja) * 2017-03-29 2017-09-07 三菱自動車工業株式会社 車両のトランスアクスル装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009011328A1 (fr) * 2007-07-18 2009-01-22 Aisin Aw Co., Ltd. Dispositif d'entraînement pour véhicule hybride
JP2013159212A (ja) * 2012-02-03 2013-08-19 Toyota Motor Corp 動力伝達装置
JP2017154736A (ja) * 2017-03-29 2017-09-07 三菱自動車工業株式会社 車両のトランスアクスル装置

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